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VOLUME 15, NO. 7 JULY 1983

THE SHOCK AND VIBRATION DIGEST

A PUBLICATION OF THE SHOCK AND VIBRATION INFORMATION CENTER NAVAL RESEARCH LABORATORY WASHINGTON. O.C. DTIC

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OFFICE OF THE UNDER SECRETARY OF DEFENSE

FOR RESEARCH AND

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THE SHOCK AND VIBRATION DIGEST

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A publication of

THE SHOCK AND VIBRATION INFORMATION CENTFR

Code 5804. Naval Reeaerch Laboratory Washington. D.C. 20375

(202) 767-2220

Dr. J. Gordan Showaltar Acting Director

Rudolph H. Volln

Jessica P. Hileman

Elizabeth A. McLaughlin

Mary K. Gobbett

Vohjma16.No.7

July 19B3

STAFF SHOCK AND VIBRATION INFORMATION CENTER

EDITORIAL ADVISOR: Henry C. Fusey

VIBRATION INSTITUTE

TECHNICAL EDITOR: Ronald L. Ejhlaman

EDITOR: Judith Nagle-Eshleman

RESEARCH EDITOR: Mild» Z. Tamultonls

PRODUCTION: Deborah K. Howard GwanWaasllak

BOARD OF EDITORS

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R Belshelm R.L. Bort J.D.C. Crltp D.J. Johns B.N. Lais K.E. McKee C.T. Morrow

W.D. Pilkey E. Sevin J.G. Showalter R.A Skop R.H. Volln H.E. von Gierke

The Shock and Vibration Digest is a monthly publication of the Shock and Vibration Information Canter. The goal of the Digest is to provide efficient transfer of suund. shock, and vibration technology among researchers and practicing engineers. Subjective and objective analyses of the literaturo are provided along with news and editorial material. News items and articles to be consider»*! for publication should be submitted to:

Dr. R.L. Eshlemen Vibration Institute

Suite 206. 101 West 55th Street Clarendon Hills, Illinois60514

(312) 654-2254

Copies of articles abstracted are not available from the Shock and Vibration Information Center (except for those generated by SVIC). Inquiries should be directed to library rusouroes. authors, or the original publishers.

This periodical is for sale on suoscripticn at «n annual rate of $140 00. For foreign subscribers, there Is an additional 25 percent charge for overseasdeliv- ery on both regular subscriptions and back issues. Subscriptior.s are accepted for the calendar year, beginning with the January issue. Back issues are available - Volumes 9 through 14 - for $20.00. Orders may be forwarded at any time to SVIC, Code 5804, Naval Research Laboratory, Washington, D.C. 20375. Issuance of this periodical is approved in accordance with the Depart- ment of the Navy Publications and Printing Regulations, NAVEX0S P 35.

SVIC NOTES

INSTITUTE OF ENVIRONMENTAL SCIENCES

ELECTS HENRY C. PUSEY FELLOW

Henry C. Pusey, Director, NavalResearch Laboratory, Shock andVibration Information Center,was elected to the membershipgrade of FELLOW in the Insti-tute of Environmental Sciences. ,

Mr. Pusey was honored "for in-valuable sustained leadership inthe development, coordinationand dissemination of an inter-national shock and vibrationinformation base, in particularthrough his role as Director ofShock and Vibration Informa- Hevy C. Puse.

tion Center."

Mr. Pusey has served the Institute as Region II Vice President,Manager Shock and Vibration Technical Committee, GeneralChairman, 1980 Annual Technical Meeting. He was the recipientof the IES Irwin Vigness Award for Shock and Vibration in 1974.

The presentation of the Fellow Award was made to Mr. Puseyat the Institute's 29th Annual Technical Meeting Awards Ban-quet, at the Marriott Hotel, Los Angeles, California, April 20,1983.

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EDITORS RATTLE SPACE

THE IMPACT OF MICROPROCESSORSON VIBRATION ENGINEERING

The advent of the inexpensive microprocessor has revolutionized the way we dovibration calculations today. Because of the complex mathematical nature ofvibration theory, it is a natural application area for computers. The computingpower of the microprocessor can be used to analyze many vibration problemsthereby eliminating the need to resort to mainframe computers. The accessibilityand convenience of microprocessors as opposed to mainframe computers meansthat large and very difficult problems can now be solved on site within minutes.

I believe that the microprocessor and programmable calculator have had a goodinfluence on the engineer. Solution of an ever increasing number of problems onthe computer has fostered a better understanding by the engineer of theory and thephysical mechanisms that are described by theory. The strengths and limitationsof the numerical processes used in computation can be better understood byengineers who apply them in small computers. The reason is that the average !77engineer now does some or all of his own programming.

The "black box" syndrome is no longer in effect. When engineers were solely ""'t;dependent on mainframe computers and canned software there was more tendency

to attempt to solve problems with a "black box" approach and less inclination oropportunity for innovation.

Computing is probably done less efficiently by engineers than by professionalprogrammers, but the engineer is gaining a better physical understanding of mecha-nisms as he develops programs, and this is the essence of engineering.

R. L.E.

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INDUSTRIAL NOISE CONTROL: THE PAST THREE YEARS

RJ. Peppr"

Absract, This paper surveys literature concerning Thus, for example, refineries have diesel generators,industrial noise control over the past three yws. furnaces, vents, pumps, and electric motors, mostBroad cetegories ar presented because of the en- of which are also found in a can-manufacturing plant.compassing nature of the area& Yet the latter type of plant can have noise sources

caused by material handling systems that are oftenmissing in refineries. To complicate matters, each

Industrial noise control is one of the subfields in major noise source is often composed of one orthe area of noise control. Others include building mjrniesuc sotncmoe foeo ..

more interacting smaller sources, so that the noiseacoustics, community noise, mechanical equipment produced by a machine such as a ball mill can con-(HVAC, plumbing) noise, and, sometimes, archi- sist of ball-to-ball impacts, ball-to-material impacts,tectural acoustics. One way to identify industrialnoise is to determine if it affects workers: if noise ,wellas the acoustical characteristics of the structure-affects workers it can be defined as industrial. How- bever, such a general definition encompasses a broad'-: ~~source of noise is the ball mill, the sum of many"-'-area because workers can be anywhere; even noise sorefnieisteblmlthsu ofaysmaller sources combine to produce the noise thoughtproduced in the community or in buildings canaffect workers. In the following discussion, therefore, tener heiit is assumed that industrial noise is noise affecting Engineers and research workers involved in noiseworkers traditionally considered employed in such control do not usually specialize in a generic area--'~~industrial areas as fatres, refineries, and mills•. oto ontuulyseiaiei eei ra<-:factorie, such as source noise control. Rather, they oftenTruck drivers, cooling tower maintenance workers, work in an industry- or process-specifi area such asoffice workers, and pilots are not included in this centrifugal fans, metal forming processes, refineries,classif icat ion. cnrfglfnmtlfrigpoess eieis

or furnaces. Because the number of these areas isThe field of industrial noise control includes methods legion, the literature review that follows is partiallyof prediction (analysis and modeling), methods of based on a noise source categorization. One corn-quantification (metrics, instrumentation, and mea- plexity of determining bounds in this literature tsurement), and methods of abatement (usually in review is the close relationship between sound andthe form of case histories) that involve either source vibration. Because vibration reduction often resultsnoise control, path noise control, or receiver control, in a drop in noise level, papers on vibration controlSource noise control is usually the redesign or new could also be considered part of noise control. Todesign of equipment, processes, and materials. Path limit this review, therefore, I have attempted when-noise control consists of reverberation control of ever possible to exclude vibration unless it is dis-space, the judicious use of barriers and enclosures, cussed as a part of noise control.and damping. Treatment of the receiver, such as theuse of earmuffs or personnel enclosures, although The field of industrial noise control gained momen-traditionally considered a means of noise control, tum during the development and enforcement ofis actually a method of employee protection that is the noise control requirement of the Occupationalnot truly noise control. Safety and Health Act (Title 29 of the Code of

Federal Regulations, 1910.95); such noise controlEvery industry has numerous major noise sources, is possibly on the decline at this writing (early 1983).each of which can be common to many industries. Industrial noise control is based on empirical and .-

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*'-eoretical science and engineering related facts the Noise [6]. The proceedings usually contain manyeffects of noise on people and the criteria associated (usually more than 100) brief (approximately fourwith these effects are based on another branch of pages each) papers that provide the most currentscience or strongly political and economic motives, reports of research in print. Sound and Vibrationor both. As a result, it is difficult to state where [1] publishes a proceedings of its yearly conference,noise control will be ten years hence. It is clear that Noisexpo. The Journal of the Acoustical Society ofwork will be done in measurement techniques, instru- America [7] also publishes recent research as ab-mentation, and some theoretical noise control of stracts in programs for semiannual meetings. Avarious equipment, especially in critical areas or in journal published by the American Society of Me-progressive facilities. However, it is not clear that chanical Engineers [8] is the Journal of Vibration,the strong force that has driven research and engi- Acoustics, Stress, and Reliability in Design. It con-neering will continue, tains articles either of the type previously carried

by other ASME-sponsored journals or published asThis review is the first dealing with industrial noise ASME preprints from sessions held at ASME con-control in the Digest and thus covers a relatively ferences. Relevant preprints will not be eliminatedlarge area. Even so, only 'the predominant literature by publication of the Journal but will probably beof the last three years is included. Readers desiring incorporated into more specialized publications.historical literature should consult references andreview citations to earlier works. Future reviews Journal of the Acoustical Society of America [7]will be essentially noise-source specific. Literature occasionally contains papers on noise control engi-in industrial noise control appears in refereed jour- reering, but they are usually theoretical treatmentsnals, trade magazines, magazines for the lay person, of rather esoteric problems. Two other journals,and conference proceedings, usually found only in academic or research libraries

in the United States, [9, 10] contain readable articlesLIT ERATURE ON INDUSTRIAL NOISE that deal with noise control. The articles usually

LONI STRcontain reports of results of theoretical work, experi-mental work, or both.

One popular source of articles on industrial noisecontrol is S/V, Sound and Vibration [11. This con- The Sck and Vibration Digest [11], issued month-trolled-circulation magazine contains a variety of ly, contains abstracts of articles from most of the

articles on noise, many of which deal with industrial literature in the field. Approximately 130 publica-noise control. Most of the articles are written for tions are scanned; the relevant papers are of varyingindividuals who deal with noise in their daily work; levels of sophistication. Applied Mechanics Reviews

as a result, the articles can usually be read and under- [12] contains critical reviews of articles, some re-stood by persons with some technical or academic lated to noise control, usually at a basic mechanics

training. The articles often include examples of level -- e.g., contact stresses, sound generation.

solutions to noise control problems. Other magazines O b ni S d[2, 31 have occasional articles that are general in Other publications in the United States and abroad

nature and do not provide generic fixes for noise also contain relevant articles on noise control andcontrol, range from sophisticated foreign language journals

to trade magazines. They will be incorporated in a

A popular journal in the United States is Noise future review.Control :ngineering Journal [4], originally calledNoise Control Engineering. Published by the Institute Other sources of product literature, handbooks, andof Noise Control Engineering [5] it is refereed and technical reviews include manufacturers of materials,is meant for engineers. Relatively sophisticated systems, and instruments. At the least these sources

analytical and experimental approaches are used in provide step-by-step approaches to noise reductionthe many articles on industrial noise control. [13, 14] or sophisticated treatises on relevant topics

[15]. One excellent how-to-book on noise controlPopular proceedings include those from two con- was published by the Department of Labor [16].ferences sponsored by INCE, Noise-Con and Inter Although the present administration has decided to

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not distribute this book, it can be found in an almost topic of research [74, 76] as was an associatedientical format [17] as part of a manufacturer's nvoise control technique, lagging [77]. In the area

l iterature offering. of mechanical components of noise, especially con-tact stresses and impact, several articles have treated

In the following paragraphs the diverse field of transmission and gears [29, 78-82] and bearings andindustrial noise control is categorized in discrete rollers [83,84].groups. The citations to the literature are not comn-plete, but they are representative of the areas. Pneumatic and hydraulic noise. Pneumatic- and

hydraulic-induced noise can be considered a distinctgroup because the noise is often not produced by

SURVEY OF PUBLICATIONS structural vibration but by fluid turbulence. Turbu-ON INDUSTRIAL NOISE CONTROL lence usually sets the containing structure into mo-

tion and causes the structure to be a secondarydAnalytical and experimental approache& Industrial source. Most of the articles in the area of pneumatic

noise control is most efficiently accomplished during noise have dealt with heavy fans [85-891, mufflersthe design stages. When equipment in operation and silencers [90-98, 175], valves [99-102], andproduces noise, measurement and analysis are usually combinations of components [98, 103-108]. Papers -necessary to develop an effective control. on hydraulic and other fluid-borne noise emphasized

cavitation [109], pumps [1 10-1 12], and silencersArticles on analytical and experimental approaches [113]. Some papers discussed fluid power abatementrange from general tutorials [18] and analyses [19, in general [114-116].20] to f inite elements (21-25] and other methods forphysical and analytical modeling and basic design Specific noise sources, Emphasis in the practice of[26-30]. Published work also includes methods of noise control concerns the specific tools or processespredicting the noise produced by machine elements necessary to solve a particular problem. Conceptsin vibration [31, 32] and the close relationship beof valve noise control can often be used in generictween noise and vibration [33-38]. solutions for products and processes with valves;

techniques to control saw noise, however, are limitedSome experimental work has been performed in the to the class of equipment to which a technique isrelatively new areas of time-series, cepstra, and applicable. Similarly, the technology resulting fromcoherence techniques (39, 40]. A potentially impor- developing methods to solve systems noise -- fortant analytical tool, the statistical energy analysis example, from a specific metal, chain driven, con-method, has been the subject of several publications veyor belt - cannot usually be applied either to other[41-47]. The number of experiments in acoustic types of systems or to other systems of similarintensity and surface intensity techniques has in- construction. In the first case no technology trans-creased in the last couple of years as indicated by the fers are applicable; in the second case site and instal-increase in commercial instrumentation available lation peculiarities tend to make solutions for oneand the many articles published [48-60]. One of the system niot applicable to another.mnore recent works in noise control deals with therenewed concept of active noise control; i.e., cancel- The general f ield of material handling has beenlation of existing sound fields by generating similar treated (84, 117, 118], as have several industry-

fields (61, 62] . specific areas. For example, the textile process wasI*1,* well-represented [24, 119 - 124] as were printing

Maerials and components A number of publications processes (125]. Publication topics in the heavieron noise control have dealt with specific areas of industries included mining [126, 127] and powermaterials investigation and applications and tech- plants [40, 128-130].niques to control noise of specific components.Topics include insulation (63, 64] and barriers One common tool that has been studied in the past[65, 661, as well as general issues in the areas of few years in an attempt to control noise is saws,materials (67-73] and their properties, including both circular saws and chain saws [131 -137). Other -transmission loss [74, 75]. Pipe noise control was a tools that have been studied are rock drills and

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other percussive tools [108, 127, 138-140], engines 10. Applied Acoustics, Applied Science Publishers,[141-144], and transmissions (80, 81, 145]. Other Ltd., Ripple Road, Barking, Essex, UK.industry-specific equipment, such as furnaces andburners [146-150], metal working and impact pro- 11. Shock end Vibration Digest, Shock and Vibra-cesses [23, 28, 117, 151-163], and hammer mills tion Information Center, Code 5804, Navalused for material reduction [164], have been studied. Research Laboratory, Washington, D.C. 20375.Several articles had to do with general concepts ofnoise control programs [26, 128, 165-173). 12. Published by the ASME (See Reference 8).

General noib control technique& Some of the more 13. Owens Corning Fiberglas, Fiberglas Tower, 'specific methods of noise control have been dis- Toledo, OH 43657.cussed in articles dealing with damping (67,174,1761and noise enclosures [157, 177-180] including pipe 14. Industrial Acoustics Co., Inc., 1160 Commercelagging [771. A yearly compendium was published Ave., Bronx, NY 10462.for potential buyers of noise control systems [181-1831, and a published search [1841 contains general 15. Technical Review, Bruel & Kjaer Instruments, ,. -

information on noise control. Inc., 185 Forest Street, Marlborough, MA01752.

ITERATURE REVIEWED 16. Noise Control: A Guide for Workers and

Employees, U.S. Department of Labor, Wash-

1. Sound and Vibration, Acoustical Publications, ington, D.C. (1980).Inc., 27101 E. Oviatt Road, Bay Village, OH44140. 17. Noise Control Bruel & Kjaer Instruments, Inc.,

185 Forest St., Marlborough, MA 01752 (1982)2. Plant Engineering, 1301 S. Grove Avenue,

Chicago, IL 60010. 18. Makarewicz, R., "Theoretical Foundations ofSome Problems in Environmental Acoustics,"

3. Mechanical Engineering, 345 E. 47th Street, J. Sound Vib., 81 (2), pp 271-286 (Mar 1982).New York, NY 10017.

19. Akay, A., "Vibration, Damping, and Acoustic4. Noise Control Engineering Journal, P.O. Box Radiation due to Transient Excitation of Struc-

3206, Arlington Branch, Poughkeepsie, NY tures," ASME Paper 81-WA/NCA-9.12603.

20. Rothschild, R.S., "Techniques of Identifying5. Institute of Noise Control Engineering, P.O. Sources of Noise and Vibration," Des. News,

Box 3206, Arlington Branch, Poughkeepsie, pp 51-54 (Apr 1982).NY 12603. pp 5 ( 1

21. Thompson, B.S., "Variational Formulations for6no Counation , P.O Box P3469, ngto the Finite Element Analysis of Noise RadiationCoantrl Foundatesi, PNO. Box 3from High-speed Machinery," J. Engrg. Indus.,Branch, Poughkeepsie, NY 10017. Trans. ASME, 103 (4), pp 385-391 (Nov 1981).

7. Journal of the Acoustical Society of America,American Institute of Physics, 335 E. 45th 22. Camel, M.N. and Wolf, J. (eds.), Finite Element

Street, New York, NY 10017. Applications in Acoustics, ASME (1981).

8. American Society of Mechanical Engineers, 23. Vasconcelos, H.F. and Taylor, S., "A Theoreti-345 E. 47th Street, New York, NY 10017. cal Method of Minimizing Vibration and Noise

Generation of High Energy Rate Forming -

9. Journal of Sound and Vibration, Academic Machine Structures," I Mech E Proc., 196, ppPress, 111 Fifth Avenue, New York, NY 10019. 183-190 (June 1982).

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24. Stewart, N.D. and Bailey, J.R., "Finite Element 35. Richards, E.J., "Energy Input, VibrationalAnalysis as a Diagnostic and Design Tool for Level and Machinery Noise; Some SimpleTextile Spindle Noise Control," ASME Paper Relationships," ASME Paper 81-DET-96.79-WA/DSC-4.

36. Petersson, B. and Plunt, J., "On Effective

25. Sung, S.H., "A Finite Element Procedure for Mobility in the Prediction of Sound Trans-

Studying the Acoustic Radiation of a Vibrating mission Between a Source Structure and a

Plate," ASME Paper 82-WA/NCA-3. Receiving Structure; Part 1: Theoretical Back-ground and Basic Experimental Studies," J.

4 26. Shield, B.M., "A Computer Model for the Pre- Sound Vib., 82 (4), pp 517-529 (June 1982).

diction of Factory Noise," AppI. Acoust.,13 (6), pp 471-486 (Nov-Dec 1980). 37. Petersson, B. and Plunt, J., "On Effective

Mobility in the Prediction of Sound Trans-:. mission Between a Source Structure and a "!

27. Jeyapalan, R.K. and Halliwell, N.A., "Ma- m iinB Structure ant achineryReceiving Structure; Part 2: Procedures for the

Estimation of Mobilities," J. Sound Vib., 82Using Acoustic Modeling," Appl. Acoust.,14 (5), pp 361-376 (Sept-Oct 1981).

"nutil 38. Okubo, N., "The Effect of Non-intensity on1' 28. Hansen, C.H. and Kuglar, B.A., "Industrial ''"'

2.ae CHa KgrB.Transfer Function Measurement," S/V, SoundMachinery Noise Impact Modeling," Vol. 1, Vib., pp 34-37 (Nov 1982).Vol. 2, and Appendices, U.S. Environmentalt,'; Protection Agency Rept. EPA-550/9-1/315Peo g y p E 5 9 339. Lyon, R.H. and Ordubadi, A., "Use of Cepstra

%, (July 1981).(Juy 98).in Acoustical Signal Analysis," ASME Paper

"-1! 29. Ishida, K. and Matsuda, T., "Study on Pitch 81-DET-138.Circle Impulse Noise of Gear by Simulated 4a icGear Tooth Contact," ASME Pae BO-C2/ 40. Ying, S.P. and Dennison, E.E., "ApplicationDET-69. of Coherence Technique for Noise in Power

Plants," Noise Control Engrg., 15 (2), pp 81-87(Sept-Oct 1980).

30. O'Keefe, E., "Modelling Directionally Radiating (.ct90Acoustical Enclosures to Determine Noise .",

Levels," SAE Paper 810699. 41. Clarkson, B.L. and Pope, R.J., "ExperimentalDetermination of Vibration Parameters Re-

~~~quired in the Statistical Energy Analysis Meth- .,i.31. Dubowsky, S. and Morris, T.L., "An Analytical qure in the tiaEnergy AayiMth

and Experimental Study of the Acoustical o"S Pe8.-Noise Produced by Machine Links," ASME 42. Miller, V.R. and Faulkner, L.L., "Prediction ofSPaper 81 -DET-93. Aircraft Interior Noise Using the Statistical

. MEnergy Analysis Method," ASME Paper 81-

,32. Marsh, K.J., "Determination of Sound Power DET-102.Levels for Industrial Purposes," Appl. Acoust.,14 (2), pp 135-146 (Mar-Apr 1981). 43. Maidanik, G., "Principle of Supplementarity

of Damping and Isolation in Noise Control,"33. Yokoi, M. and Nakai, M., "A Fundamental J. Sound Vib.,7ZZ (2), pp 245-250 (July 1981).

Study on Frictional Noise," Bull. JSME, 23(186), pp 2118-2124 (Dec 1980). 44. Wohle, W., et al, "Coupling Loss Factors for

Statistical Energy Analysis of Sound Trans-

34. Kojima, N., "Estimation of Noise Emitted by mission at Regular Structural Slab Joints;Vibration of a Plate," Bull. JSME,.24 (193), pp Part I," J. Sound Vib., 2 (3), pp 323-3341233-1238 (July 1981). (Aug 1981). •.,,

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45. Wohle, W., et al, "Coupling Loss Factors for 55. Upton, R., "Sound Intensity -. A Powerful NewStatistical Energy Analysis of Sound Trans- Measurement Tool," S/V, Sound Vib., pp

A mission at Regular Structural Slab Joints 10-19 (Oct 1982). -11.

Part II," J. Sound Vib., 77 (3), pp 335-344(Aug 1981). 56. McGary, M.C. and Crocker, M.J., "Surface

Intensity Measurements on a Diesel Engine,"46. Craik, R.J.M., "The Prediction of Sound Trans- Noise Control Engrg., 16 (1), pp 27-36 (Jan-

mission Through Buildings Using Statistical Feb 1981).Energy Analysis," J. Sound Vib., 82 (4), pp505-516 (June 1982). 57. Crocker, M.J., et al, "Measurement of Trans-

mission Loss of Panels by the Direct Determina-

47. Elmallawany, A., "Improvement of the Method tion of Transmitted Acoustic Intensity," Noise - -

of Statistical Energy Analysis for the Calcula- Control Engrg., 17 (1), pP 6-11 (July-Augtion of Sound Insulation at Low Frequencies," 1981).

App. Acoust., 15 (5), pp 341-345. 58. Thompson, J.K., "Acoustic Intensity Measure-ments for Small Engines," Noise Control

48. Reinhart, T.E. and Crocker, M.J., "Source Engrg., 19 (2), pp 56-63 (Sept-Oct 1982).Identification on a Diesel Engine Using Acous-tic Intensity Measurements," Noise Control 59. Wang, Y.S. and Crocker, M.J., "Direct Measure-Engrg., iaj (3), pp 84-92 (May-June 1982). ment of Transmission Loss of Aircraft Struc-

tures Using the Acoustic Intensity Approach,"49. Pope, J., "The Use of Acoustic Intensity Scans Noise Control Engrg. J., 19 (3), pp 80-85 (Nov-

for Sound Power Measurements and for Noise Dec 1982).Source Identification in Surface Transportation

Vehicles," SAE Paper 810401. 60. Benner, H. and Koopman, G.H., "Sound PowerPrediction Using Hemholtz-Kirchhoff Integral

50. Crocker, M.J., "The Use of Existing and Ad- Equation," ASME Paper 81 -WA/NCA-4.vanced Intensity Techniques to Identify NoiseSources on a Diesel Engine," SAE Paper 810- 61. Ross, C.F., "A Demonstration of Active Con-694. trol of Broadband Sound," J. Sound Vib.,

74 (3), pp 411-417 (Feb 1981).51. Chung, J.Y. and Blaser, D.A., "Recent Develop-

ments in the Measurement of Acoustic Inten- 62. Warnaka, G., "Active Attenuation of Noise:sity Using the Cross Spectral Method," SAE The State of the Art," Noise Control Engrg.,Paper 810396. &18 (3), pp 100-110 (May-June 1982).

63. Dear, T.A., "Introduction to Design Specifica-52. -,hy, F.J. and Elliott, S.A., "Acoustic Inten-

sity Measurements of Transient Noise Sources," tion Criteria for Acoustical Insulation," ASME

Noise Control Engrg., 1Z (3), pp 121-125 (Nov- Paper 80-WA/NC-10.

Dec1981). 64. Ingard, K.U., "Locally and Nonlocally Reacting -Flexible Porous Layers: A Comparison of

' 53. "Recent Developments in Acoustic Intensity Acoustical Properties," ASME Paper 80-WA/Measurement," Proc. Intl. Congr. Senlis, NC-12. --France, Sept 30 - Oct 2, 1981, CETIM D.P.67,

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F-60304, Senlis, France. 65. Hohman, J.J., "Plastic Strip and Sheet Bar- ":riers," Plant Engrg., 3A (16), pp 71-73 (Aug 7, i_

54. Pettersen, O.Kr.(., "Sound Intensity Measure- 1980).

ments for Describing Acoustic Power Flow,"Appl. Acoust., 14 (5), pp 387-398 (Sept-Oct 66. Narayanan, S. and Shanbhag, R.L., "Sound1981). Transmission through a Damped Sandwich

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77 7. . . . .. . .

Panel," J. Sound Vib., 80 (3), pp 315-327 Acoustical Holography," ASME Paper 80-C2/(Feb 1982). DET-44.

67. Purcell, W.E., "Materials for Noise and Vibra- 80. Drago, R.J., "Minimizing Noise in Transmis-tion Control," Sound Vib., 14 (7), pp 8-32 sions," Machine Des., 53 (1), pp 143-148 (Jan

. (July 1980). 1981).

68. Purcell, W.E., "Materials for Noise and Vibra- 81. Drago, R.J., "How to Design Quiet Trans-tion Control," Sound Vib., 15 (7), pp 4-30 missions," Machine Des., 52 (28), pp 175-181(July 1981). (Dec 1980).

69. Purcell, W.E., "Materials for Noise and Vibra- 82. Umezawa, K. and Houjoh, H., "The Soundtion Control" Sound Vib., 16 (7), pp 6-31 Radiated from Gears," Bull. JSME, 24 (195),(July 1982). pp 165-167 (Sept 1981).

70. Pizzirusso, J., "The Acoustics of Plastic Foam,"Machine Des., 53 (1), pp 135-139 (Jan 1981). 83. Ries, J.P. and Witherell, P.G., "Noise due to

Resonant Excitation of Rotating Cylinder,"

71. Prybutok, R., "Materials for Noise Control," ASME Paper 81-DET-98.

SAE Paper 810859.84. Bollinger, J.G., et al, "Support Roll Noise

72. Cummings, A., "High Amplitude Acoustic Reduction Using Elastomer Surfaces," NoisePower Losses in Perforated Materials," ASME Control Engrg., 15 (3), pp 114-119 (Nov-DecPaper 81 -WA/N CA-10. 1980).

73. Nelson, P.A., "Noise Generated by Flow over 85. Neise, W., "Review of Noise Reduction Meth-Perforated Surface," J. Sound Vib., 83 (1), pp ods of Centrifugal Fans," ASME Paper 81-WA/11-26 (July 1982). NCA-2.

74. Fagerlund, A.C. and Chou, D.C., "Sound 86. Neise, W. and Koopman, G.H., "Reduction of

Transmission through a Cylindrical Pipe Wall," Centrifugal Fan Noise by the Use of Resona-ASME Paper 80-WA/NC-3. tors," J. Sound Vib., 73 (2), pp 297-308 (Nov

1980).75. Lyon, R.H. and Slack, J.W., "A Review of

Structural Noise Transmission," Shock Vib. 87. Neise, W., "Review of Noise Reduction Meth-

Dig., 14(8), pp 3-11 (Aug 1982). ods for Centrifugal Fans," J. Engrg. Indus.,Trans. ASME, 104(2), pp 151-161 (May 1982).

76. Loh, H.T. and Reethoff, G., "On Circular PipeWall Vibratory Response Excited by Internal 88. Neise, W., "Noise and Noise Abatement inAcoustic Fields," ASME Paper 80-WA/NC-13. Fans and Blowers -- A State of the Art Re-

view," Deutsche Forschungs and Versuchsan-

77. Smith, T., et al, "Pipe Lagging -- An Effective staid F Luftund Raumfahrt e V., Goettingen,Method of Noise Control?" AppI. Acoust., West Germany, Report No. DFVLR-FB-80-16

13 (5), pp 393-404 (Sept-Oct 1980). (1981).

78. Ishida, K. and Matsuda, T., "Effect of Tooth 89. Wright, T., "A Velocity Parameter for the

Surface Roughness on Gear Noise and Gear Correlation of Axial Fan Noise," Noise Con-Noise Transmitting Path," ASME Paper 80- trol Engrg., 19 (1), pp 17-25 (July-Aug 1982).C2/D ET-70.

90. Thunder, T.D. and Shahan, J.E., "Effects of

79. Imezawa, K. and Houjoh, H., "On the Study Flu-Gas Contamination on the Acousticalof the Sound of Gear and Gear Box Using Performance of Tuned Discharge Silencers

9%-

%il

for Induced Draft Fans," ASME Paper 82-WA/ 102. Bordelon, T.R. and Etherington, J.F., "Pres-

NCA-6. sure Relief Valve Noise Attenuation," ASMEPaper 81 -PVP-38.

91. Munjal, M.J., "Evaluation and Control of theExhaust Noise of Reciprocating IC Engines," 103. Oviatt, M.D., "Energy Conservation and Noise

Shock Vib. Dig., 13 (1), pp 5-14 (Jan 1981). Control in Pneumatic Devices and Systems;Part II, Percussive Tools, Blow-offs and Air

92. Scarton, H.A., et al, "Energy Efficient Muffler Ejectors," Plant Engrg., 35 (16), pp 116-118

for Reduction of Exhaust Noise Generated by (Aug 1981).

Pneumatic Grinder," ASME Paper 80-WA/ '0NC-9. 104. Maa, D.Y. and Li, T.Z., "Pressure Dependence

of Jet Noise and Silencing of Blow-offs," Noise

93. Ferrelli, M.W., "Insertion-loss Measurements of Control Engrg., 17 (3), pp 104-112 (Nov-Decan Elliptical Cross-section Disapation Muffler," 1981).Noise Control Engrg., 16 (1), pp 22-24 (Jan- 105. Jungowiski, W.M. and Selerowicz, W.C., "The-Feb 1981). ory and Operation of a Low Noise Throttling-

Norris, T.R., "Noise Reduction in Engine Ex- Venting Device," Noise Control Engrg., 17 (2),94. ppris 86-94 ("ept-sc 1981). i Egiex

haust," U.S. Army Rept. No. AD-D007 636/4 pp 86-94 (Sept-Oct 1981

(June 16, 1980). 106. Hooker, R.J. and Rumble, R.H., "Noise Charac-

teristics of a Pulsed Jet," Noise Control Engrg.,95. Nakara, B.C., et al, "Investigations on Mufflers 17 (3), pp 113-119 (Nov-Dec 1981).

for Internal Combustion Engines," Appl.Acoust., 14 (2), pp 135-145 (Mar-Apr 1981). 107. Dahl, M.D. and McDaniel, O.H., "The Perfor-

mance of Jet Noise Suppression Devices for96. Thawani, P.T. and Noreen, R.A., "Computer Industrial Applications," ASME Paper 82-WA/

Aided Analysis of Exhaust Mufflers," ASME NCA-5.Paper 82-WA/NCA-10.

108. Patterson, W.N., "Computer Design of Pneu-97. Soderman, P.T., "Design and Performance of matic Rock Drills and Mufflers," ASME Paper

Resonant-Cavity Parallel Baffles for Duct 81-DET-99.Silencing," Noise Control Engrg., 17 (1), pp12-21 (July-Aug 1981). 109. Saito, S. and Oshima, M., "An Experiment in

Pump Pressure Fluctuation, Vibration and Air-98. Franco, L. and Ruspa, G., "Reduction of Noise borne Noise Caused by Cavitation," ASME

on Large Size Pipes by Inserting Acoustic Paper 81-DET-94.Grilles," Appl. Acoust., 14 (6), pp 417-436(Nov-Dec 1981). 110. Florjancic, D., et al, "Primary Noise Abate-

ment on Centrifugal Pumps," Sulzer Tech.

99. Chadha, J.A., et al, "Acoustic Source Prop- Rev., 62 (1), pp 24-26 (1980).erties of Governor Valves," Flow InducedVibration of Power Plant Components, (M.K. 111. Hobbs, J. and Fricke, H., "New Methods ofAu-yang, Ed.), pp 125-138, ASME PVP-41 Reducing Noise in External Gear Pumps," I(Aug 1980). SAE Paper 801005.

100. Chow, G.C. and Reethof, G., "A Study of 112. Sharma, J.K.N. and Dutta, P.K., "Aspects ofValve Noise Generation Processes for Com- Noise in Rotary Vacuum Pumps," AppI.pressible Fluids," ASME Paper 80-WA/NC-15. Acoust., 13 (6), pp 425-432 (Nov-Dec 1980).

101. Ng, K.W., "Aerodynamic Noise Generation and 113. Narui, H. and Inagaki, S., "Attenuation Char-Control Valves," ASME Paper 80-WA/NC-8. acteristics of Mufflers with Gas Reservoir in

10 7

--.

Liquid Pipe System," Bull. JSME, 23 (182), Cutting," J. Engrg. Indus., Trans. ASME,pp 1374-1379 (Aug 1980). 03 (3), pP 257-269 (Aug 1981).

114. Maroney, G.E., "Fluid Power System Noise 127. Bender, E.K., et al, "Noise Control of Jumbo

Abatement - 1980," SAE Paper 801007. Mounted Percussive Drills," Noise ControlEngrg., 15 (3), pp 128-136 (Nov-Dec 1980).

115. "Beating Noise in Fluid Systems," Engrg. 1oi b, all.Des, 24(8) PP 4-50(Set 190).128. "Noise Control in Industry," Noise Vib. Con- i .Matl. Des., 24 (8). pp 44-50 (Sept 1980).(9,p34-7(NvDc18)

16"B itrol, 11 (9), pp 343-347 (Nov-Dec 1980).116. "Beating Noise in Fluid Systems," Engrg. 129. Nuspl, S.P. and VanHandle, H.R., "Power 0

Matl. Des., 24 (9), PP 28-32 (Oct 1980). Plant Noise Control," ASME Paper 81-JPGC/o',' PWR-15."•

117. Vajpayee, S., et al, "Noise Reduction in Mate- WR.rial Handling Machines," Appl. Acoust., 14 (6), 130. Bannister, R.L., "Power Plant Monitoring andpp 471-476 (Nov-Dec 1981). Diagnostics," Sound Vib., pp 16-20 (Sept

118. Rivin, E.I., "Noise Abatement of Vibration- 1982).

-' Simulated Material Handling Equipment," 131. Mote, C.D. and Leu, M.C., "Whistling Insta-Noise Control Engrg., 14 (3), pp 132-142 (May- bility of Idling Circular Saws," ASME PaperJune 1980). 79-WA/DSC-18.

119. Satter, M.A., "Noise Reduction of a Draw 132. Yap, K.T., "Analysis of Vibratory Noise inRoll Assembly by Design," Noise Control Sawing of Aluminum Extrusions," Ph.D. thesis,Engrg., L15 (3), pp 120-125 (1980). University of Wisconsin, Madison (1981).

120. Satter, M.A., "Noise Reduction of a Tack 133. Toenshoff, H.K., et al, "Noise Reduction Pro-Driving Assembly by Design," Noise Control cess in Cutting with High Speed Tools," NoiseEngrg., 16 (1), pp 15-19 (Jan-Feb 1981). Control Engrg., 17 (3), pp 126-130 (Nov-Dec

1981).

121. Kaliskan, M., et al, "Analysis of Fly ShuttleLoom Noise by Multi-channel Digital Signal 134. Ulsoy, A.G. and Mote, C.D., Jr., "VibrationProcessing Techniques," ASME Paper 81-DET- of Wide Band Saw Blades," J. Engrg. Indus.,100. Trans. ASME, 104 (1), pp 71-78 (Feb 1982).

122. Stewart, N.D., "Analysis and Control of the 135. Mote, C.D., et al, "Bandsaw and Circular SawNoise of Textile Ring Spinning Frames," Ph.D. Vibration Stability," Shock Vib. Dig., 14 (2),Thesis, North Carolina State University (1981). pp 19-25 (Feb 1982).

123. "Noise Pollution in Textile Mills," 1975 to Nov 136. Kristiansen, V.R., "A Coincidence Criterion for1981. NTIS, Springfield, VA (Nov 1981). Effective Sound Radiation from a Resonant

Free Running Circular Saw Blade," Appl.

124. Mandl, G., "Noise Control in Ring Spinning Acoust., 14 (4), pp 267-280 (July-Aug 1981).Rooms," Noise Control Engrg., J8 (3), pp 93-99 (May-June 1982). 137. Leu, M.C. and Mote, C.D., Jr., "Vortex Shed-

ding: The Source of Noise and Vibration in125. Lundin, K., "Printing Press Automation and Idling Circular Saws," ASME Paper 82-WA/

Noise Control," Noise Control Engrg., 15 (2), NCA-2.pp 65-69 (Sept-Oct 1980).

138. Scarton, H.A., et al, "Sources of Noise Pro-126. Becker, R.S., et al, "An Investigation of the duced During Pneumatic Chipping Hammer

-' Mechanics and Noise Associated with Coal Operations," ASME Paper 80-WA/NC-1i1.

- ......

llA

. -' - .. " .' • .

'47-

139. George, D.L. and Matteo, N.J., "Development 151. Kennedy, W.C., et al, "Experimental Investi-of Noise Control Technology for Pneumatic gation into the Physics of Arc-Air Metal Goug-Jumbo Drills," I.R. Research Inc., Princeton, ing Noise Generation," ASME Paper 80-WA/NJ, Rept. BUMINES-OFR-100-81 (Nov 1980). NC-12.

140. Vajpayee, S. and Sadek, M.M., "Effects of Pro- 152. Vajpayee, S., et al, "Acoustic Diagnosis of acess Parameters on Hammer Noise," ASME Hydraulic Hammer," ASME Paper 81-WA/Paper 81-DET-95. NCA-8.

141. Slabber, N.J.J., "Review of Diesel Engine 153. Vajpayee, S., et al, "Influence of Machine --Noise," Presented at Intl. Symp. Transp. Noise, Suspension and Process Parameters on NoiseCSIR Conf. Center, Pretoria (Oct 21-23, 1981). Emitted from Drop Hammers," ASME Paper81 -WA/NCA-7..i.

142. DeJong, R.G. and Parsons, N.E., "Diesel NoiseReduction: A Study," Auto. Engrg. (SAE), 154. Vajpayee, S., et al, "Prediction of Linear90 (6), pp 70-74 (June 1982). Noise Load Relationship for Impact Forming

Machines," Intl. J. Machine Tool Des. Res.,

143. Schultz, N. and Summerson, W.N., "Noise 22 (1), pp 1-6 (1982).Control for Diesel Engine Generator Sets,"Sound Vib., pp 30-33 (May 1980). 155. Koss, L.L. and Moffatt, J.A., "Vibration and

Acoustic Data for a Punch Press," J. Sound144. Kojima, N., et al, "Impulse Response and Vib., 80 (4), pp 543-544 (Feb 1982).

Radiated Noise in an Air Cooled Small Engine,"Bull. JSME, 25 (200), pp 234-240 (Feb 1982). 156. Thornhill, R.H. and Smith, C.C., "Impact Force

Prediction Using Measured Frequency Re-

145. Kagotani, M., et al, "Some Methods to Reduce sponse Functions," ASME Paper 81-WA/DSC-Noise in Toothed Belt Drives," Bull. JSME, 24 17.(190), pp 723-728 (Apr 1981). "--

157. Stormont, J.W. and Pelton, H.K., "Partial En-

146. McQueen, D.H., "Electric Arc Furnace as a closures -- Effective Control of Punch PressNoise Source," Noise Control Engrg., 15 (2), Noise," Sound Vib., pp 10-17 (Oct 1980).pp 89-95 (Sept-Oct 1980).

158. Atkinson, K. and Lamb, P., "Time History147. Bitterlich, G., "Burner Noise and Its Suppres- Analysis of Multi-impact Noise," Noise Con-

sion," Noise Control Engrg., 14 (1), pp 6-11 trol Engrg., 15 (1), pp 6-10 (July-Aug 1980).(Jan-Feb 1980).

159. Richards, E.J., "On the Prediction of Impact148. Anglesio, P. and Cirillo, E., "Noise Generation Noise; Ill, Energy Accountancy in Industrial .'

by Oil-Burner Heads with Pressure Jet Atomi- Machines," J. Sound Vib., 76 (2), pp 187-232zation," Noise Control Engrg., j(2), pp 62-67 (May 1981).(Mar-Apr 1982).

160. Francis, D.T.I., et al, "Prediction of Acoustic149. Rodman, CW., "Monitoring Combustion Emission of Impact Forming Machines from

Chamber Oscillations with Anechoic Pressure Design Drawings," ASME Paper 81-WA/NCA-5.Probes," INTECH (Apr 1982).

161. "Drop Forge: Noise Reduction and Automatic150. Summers, I.R., "Combustion Noise - Measure- Control Equipment," Jan 1973 - Oct 1981.

ments on Single Oil Drops and Other Diffusion (Citations from Information Services in Me-Flames," AppI. Acoust., 13 (6), pp 441-448 chanical Engineering Data Base), NTIS, Spring-(Nov-Dec 1980). field, VA (Oct 1981).

12

%-- -. -

162. Taylor, D.L. and Sedek, M.N., "Squeeze Film 173. Gibson, D.C. and Norton, N.P., "The Eco-Die Support as a Means of Noise Reduction in nomics of Industrial Noise Control in Austra-Forging Machines," ASME Paper 81-DET-97. lia," Noise Control Engrg., 16 (3), pp 126-134

(May-June 1981).

163. Trethewey, M.W. and Evansen, H.A., "Identifi-cation of Noise Sources of Forge Hammers 174. Albrecht, H., "Vibration Absorbers for Damp-

During Production: An Application of Residual ing of Solid-State Noise," Messerschmitt -

Spectrum Techniques to Transients," J. Sound Boelkow-Blohm GmbH, Munich, Germany,

Vib., 77 (3), pp 357-374 (Aug 1981). Rept. No. BMFT-FB-HA-79-03 (May 1979).

164. lanniello, C., "Hammermill Noise Reduction," 175. VandenBrulle, P.J., "Development of an Ex-111-113 (Nov. haust Noise Suppressor with Negligible Back

Nose Coo EPressure," -Messerschmitt -- Boelkow-BlohmGmbH, Munich, Germany, Rept. No. BMFT-

165. Elmaraghy, R.L. and Baronet, C.N., "An Effec- FB-HA-79-02 (May 1979)., ~tive Noise Diagnosis Scheme for Industrial ;

tgf176. Bahar, A. and May, D.N., "Vibration DampingPlants," SN, Sound Vib., 14 (9), pp 14-18 Material as a Means to Reduce Steel Noise -: (Sept 1980). Barrier Cost," SN, Sound Vib., 71 (1), pp 55-,'.

58 (July 1980). ..

166. Steel, C.M., "Reverberation Time Measure-ments in Industrial Noise Control," ASME 177. O'Keefe, E.J. and Stewart, D.R., "Insertion,Paper 79-WA/SAF-2. Loss Measurements of Small Rectangular En-

closures," Noise Control Engrg., 15 (1), pp167. Liebich, R.E., "Industrial Noise Pollution; 20-27 (July-Aug 1980).

Part I: The Nature and Extent of the Problem,"Mech. Engrg., 103 (7), pp 34-43 (July 1981). 178. Maidanik, G., et al, "The Use of Decoupling

to Reduce the Radiated Noise Generated by168. Bannister, R.L., "Industrial Noise Pollution; Panels," J. Sound Vib., B1 (2), pp 165-185

Pprt II: Identifying and Controlling Industrial (Mar 1982).Noise Sources," Mech. Engrg., 103 (8), pp24-29 (Aug 1981). 179. Toothman, E.I., "Tumbler Noise Reduction: -.-

The Close Fitting Acoustical Enclosure," Noise169. Lyon, R.H., et al, "Industrial Noise Pollution; Control Engrg., 14 (3), pp 143-144 (May-June

Part II: Practical Function of Acoustical 1980).Engineering," Mech. Engrg., 103 (9), pp 42-47(Sept 1980). 180. Umezawa, U., "Sound Radiation from a Hous-

ing Containing an Acoustic Source," Bull.170. Glasburn, L.E., "Industrial Noise: Properties, JSME, 25 (202), pp 638-645 (Apr 1982).

Sources and Solutions," Hydrocarbon Pro-cessing, 60 (8), pp 127-130 (Aug 1982). 181. Purcell, W.E., "Systems for Noise and Vibration

Control," S/V, Sound Vib., 14 (6), pp 10-36171. Moulder, R., "Understanding Noise Control; (Aug 1980).

Part 1: Principles and Methods for ReducingIn-Plant Noise," Plant Engrg., 36 (17), pp 182. Purcell, W.E., "Systems for Noise and Vibration75-77 (Aug 1982). Control," S/V, Sound Vib., 15 (6), pp 4-28

(Aug 1981).172. Moulder, R., "Understanding Noise Control,

Part 2: Principles and Procedures for Reducing 183. Purcell, W.E., "Systems for Noise and VibrationExterior Noise," Plant Engrg., 36 (16), pp Control," S/V, Sound Vib., 16 (6), pp 8-2057-58 (Sept 1982). (Aug 1982).

.2. . .. . ... ° o•. ••, - - . . • . . . . . . . . . . . . . . .

184. "Industrial Noise Control: Architectural and9

Environmental Aspects (1975 - July 1982),(Citations from the Inspec. Data Base), NTIS,Springfield, VA.

14

- - .

survey and analysisILRATUoRE REVIEW:the Sh kandL Vibration literature

The monthly Literature Review, a subjective critique and summary of the litera-ture, consists of two to four review articles each month, 3,000 to 4,000 words inlength. The purpose of this section is to present a "digest" of literature over aperiod of three years. Planned by the Technical Editor, this section provides theDIGEST reader with up-to-date insights into current technology in more than150 topic areas. Review articles include technical information from articles, reports,and unpublished proceedings. Each article also contains a minor tutorial of thetechnical area under discussion, a survey and evaluation of the new literature, andrecommendations. Review articles are written by experts in the shock and vibrationfield.

This issue of the DIGEST contains articles about instability of circular cylinderarrays in cross flow and nonstationary resonance oscillations.

Dr. S.S. Chen of Argonne National Laboratory, Argonne, Illinois has written anarticle on the developments in dynamc instability of circular cylinder arrayssubjected to cross flow. The review presents a summary of progress since 1980.Mathematical models, experimental data, stability criteria, design guidelines, andfuture research needs are discussed.

Dr. B.N. Agrawal of INTELSAT, Washington, D.C. and Dr. R.M. Evan-lwanowskiof Syracuse University, Syracuse, New York have written an article describing non- -

stationary oscillations in combination resonances, factors affecting nonstationaryresponses, and applications and unsolved problems of nonstationary responses.

4-1""°:"::"°""::° ' "" .......":""." ° . . " " . i; i::: i

,I a -A -o--.*

INSTABILITYOF CIRCULAR CYLINDER ARRAYS IN CROSS FLOW

s.s. Che,

Abstract. Developments in dynamic instability of f, and damping ratio . For a cylinder array vibratingcircular cylinder arrays subjected to cross flow has in flow, the definitions of these three parametersbeen exciting in the post several years. This review vary widely. These parameters can be defined underpresents a summary of progress since 1980; mathe, the following four conditions:matical models, experimental data, stability criteria,design guidelines, and future research needs are dis- 0 In vacuum: system parameters are measuredcussed in vacuum (practically, in air); the effect of the 7

surrounding fluid is ignored.Developments in dynamic instability of circular 0 In quiescent fluid - uncoupled vibration: sys-cylinder arrays subjected to cross flow have been tem parameters are measured for an elasticconcerned in recent years with heat exchanger tube cylinder vibrating in a fluid; the surroundingfailures due to dynamic instability. Considerable cylinders are rigid. The coupling effect ofliterature has been developed to document service fluid is not taken into account.failures [1-3]; analytical and experimental studies 0 In quiescent fluid - coupled vibration: systemare being made to explain complicated instability parameters are measured for an array of cylin-phenomena. Progress in this area up to 1979 has ders vibrating in a fluid; the coupling amongbeen presented in a previous review [4]. The present different cylinders due to fluid is included.review describes mathematical models, experimental 0 In flow: system parameters are measured indata, stability criteria, design guidelines, and future flow; in general, they are dependent on theresearch needs; the period between 1980 and 1983 flow velocity.is covered.

These parameters are summarized in Table 1,MATHEMATICAL MODELS AND STABILITY

CRITERIA A summary of mathematical models is presented inTable 2 (5-151. With the exception of the original

The three important parameters used in the stability model developed by Connors [5] and analyzed bycriteria are mass per unit length m, natural frequency Blevins [6, 7], all of the models were published

Table 1.'Effective Mass, Natural Frequency, and Modal Damping Ratioin Different Conditions

In oeinent Fluidparametws In Vacuum Uncoupled Vibration Coupled Vibration In Flow

Effective imv mu mc mf-. Mass (m)

Natural fv fu fc ffFrequency (f)

Modal Damping ru fRatio (S)

Ornmponents Technology Divlaon, Arlionne Abtionel Laboratory, Argonne, IllInos

17

% % ° . .. . . . . ° . . . • , .. .. - ... . . ...

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.

.4

I4 1- t2i ~04 .0 01a

~

uILJib ~ ~ lan

I o4

is ~ ~

..

in the last few years. Table 2 shows that these models Equations of motion. Among the approaches usedare not in agreement in several respects: instability to solve the equations of motion are a single equa-mechanisms, stability criteria and system parameters, tion of motion [5, 15], multiple equations of motionand equations of motion. with assumed modes [61, and general solution of

multiple equations [8-14].

Instability mnchinus Two basic instability mecha- The merits and deficiencies of each model can be

nisms have been discussed by Chen [11, 12] : velocity summarized as follows:

mechanism and displacement mechanism. With thevelocity mechanism, or fluid-damping-controlled 0 Quasi-static models (Connors, Blevins, and

nstedominant fluid force is proportional Price and Paidoussis). These models are appli- - .instability, the cablean flnly frc isudeproc-spffrsioonoalto the velocity of the cylinders. The fluid-damping cable only for fluidelastic-stiffness-controlled

force depends on the reduced flow velocity and can instability. Although flow-velocity-dependent

act as an energy-dissipation mechanism or an excita- forces have been considered partially in sometion mechanism for cy!inder oscillations. When the modens, they are not applicable to fluid-damp-fluid-damping force acts as an excitation mechanism, inT-eontletal ity.system damping is reduced. After the modal dampingof a mode becomes negative, the tubes are no longer quires only three empirical constants but isstable. based on the velocity mechanism only. The

model has been used to demonstrate the exis-

With displacement mechanisms, or fluidelastic-stiff- tence of the jump phenomenon in critical flowness-controlled instability, the dominant fluid force velocity at a certain value of the mass-damp-is proportional to the displacements of the cylinders. ing parameter and the observed characteristicsThe fluidelastic-stiffness force can affect both natural of cylinder arrays in heavy fluids. The model

frequencies and modal damping. As flow velocity does not include the coupling effect of the ..-

increases, the fluidelastic-stiffness force can reduce fluidelastic-stiffness force. For light fluid, it.' modal damping. When the modal damping of a mode predicts that the critical flow velocity U/fD

becomes negative, the cylinders become unstable. is proportional to the first power of the mass-damping parameter; this is not in agreement

Before 1980 the displacement mechanism was used with published experimental data.

exclusively; therefore, instability was attributed to 0 The general semi-analytical model (Chen and

the fluidelastic-stiffness force. When instability is Tanaka) requires a significant amoung of mea-

attributed to the displacement mechanism, coupling surement or computation to determine fluid-

of the fludelastic-stiffness force and the neighboring force coefficients but predicts very well all the

cylinders is a requirement for instability. Before observed characteristics of instability for both

1980 it was assumed that a single elastic cylinder light and heavy fluids, including the jump

among an array of rigid cylinders would not become phenomenon and multiple stable and unstableunstable even though experimental results showed regions [11-13].the contrary; no plausible explanation was given. At this point in time, the general semi-analyticalChen [11, 121 used Tanaka's fluid-force data [8-10] model provides the most insight into instability phe-to show that both the displacement mechanism and meloithe velocity mechanism are important. Discrepancies nomena.among different models can be resolved reasonably Models not listed in Table 2 include a quasi-staticwell using the two mechanisms. model [16] that is basically an extension of Blevins'

model.Stability critia and system prrameterm Table 2shows that different investigators have developeddifferent stability criteria and used different param- EXPERIMENTAL STUDIESeters. In some cases the system parameters are not jdefined in sufficient detail or are used without Because of the difficulty in predicting critical flowjustification, velocity under different conditions, experimental

* 19

7- -- .. -

studies have been conducted in various countries Other investigators emphasize different aspects of theand can be grouped in several areas: stability con- problems; e.g., equation (2) has been used to establishstants, direct comparison with analytical results, the following constants for square arrays [9, 10]:and effects of different system parameters.

for pitch-to-diameter ratio of 1.33, .-. 9Stability conatantm In addition to the analyticaland semi-empirical stability criteria given in Table 2 U 2wm" 0.5

are various stability criteria that have been proposed o a= - , low density fluid

based on experimental data. Most of these criteria fDp 2

can be grouped into two classes:

, The critical flow velocity U/fD is a function U 0*/ 3= aI (2ir/) 0 •2 , high density fluid

of the mass-damping parameter fD C \pD2J

':J U / 2irm 2e ,.

f - \ D2~ / (1) and for pitch-to-diameter ratio of 2.0fD \t pD.4•.

- The critical flow velocity is a function of masskU 3 0 (2fm 07.ratio (m/pD ) and damping (2ir') fD

U /m 2 0 Results of triangular and square arrays for different- = P1(21t) (2) pitch-to-diameter ratios in water and air-water two-fD (D phase flows have been reported [21]. Equation (1)

was used to correlate the data.These equations have been adopted by variousinvestigators [9, 10, 13, 17-21]. Direct comparison with analytical results. The semi-

Extensive tspanalytical models (see Table 2) of Chen [12] andsexensivetstprograms e been conducted by Tanaka [8-10] can provide detailed instability char-

several investigators. Heilker and Vincent (17] have acteristics, such as oscillation frequency and mode ,•:presented the results of tube arrays in water and -"'p n h s o b a n rat instability, as well as critical flow velocity. Experi-simulated two-phase flow for various layouts. Thestability criterion equation (1) with a2 = 0.5 is used; czyk [13, 22] anducted Tanaka [8-1] td ver e

in their tests the tightly packed triangular pitch c al solutions Thoeia results a eri -analytical solutions. Theoretical results and experi-arrays are the most susceptible when the instability mental data are in good agreement. Experimentalcosatia .. data of Chen and Jendrzejczyk have verified the

Soper [181 has described a systematic study of the following conclusions:

effect of tube layout on the instability constant for

16 tube bundles based on equation (1) with % = 0.5. * Two distinct instability mechanisms exist:

Results show that the instability varies by a factor flu id-damping-controlled instability and fluid-

of three over the range of tube layouts tested. elastic-stiffness-controlled instability.0 Multiple stable and unstable regions exist

Chen and Jendrzejczyk [191 presented experimental in tube rows, and a jump occurs in the criticaldata for 12 different arrays of varying spacing, geom- flow velocity at a certain value of the mass-etries, mass ratio, damping, and detuning in water damping parameter.flow. The empirical constants based on their test 0 The effect of detuning depends on instabilitydata and published results are a, = 4.51 and a2 = mechanisms and the amount of detuning.0.52. Based on equation (1) the instability constant Detuning is important for fluidelastic-stiffness-

* of tests on nine tube layouts with both metallic and controlled instability.plastic tubes does not vary much from a = 2.5 with 0 Different stability criteria should be used for

a2 0.5 [20). large and small mass ratios.

20

i - . . . ...

":'" . . . . . . . . . . . ....22""i':. i, .i2 i 21. . . .. ,. .. .2.. .....--. _,_.-...... :... ::......... ., .-. ,....•- .. , ,. ;..

Tanaka's data also agree with his analytical results turbulence causes initiation of fluidelastic instability[8-101. to shift to higher flow velocities. Gorman [27]

carried out tests in water for typical heat-exchanger ,Effects of different system parameteri The critical tubes. He found that the existence of upstream gridsflow velocity is affected by many parameters, includ- and screens had no appreciable effect on the criticaling detuning, upstream turbulence, nonuniform flowdistribution, cylinder layout, mass ratio and damping, tunnel experiments [28] have shown that turbulenceand support clearance. Some of these effects are tends to reduce critical flow velocity. A water-tunnelqualitatively known; however, most of them are still test has been used to resolve the discrepancy (191;difficult to evaluate quantitatively, turbulence can stabilize or destabilize the tube array

depending on the characteristics of the turbulence.The frequency variation of a cylinder array in a This conclusion was verified by Soper in wind-tunnelvacuum is called detuning. When a cylinder array al situations turbulence charac-ary tests [29]. In practicsiutosurueechr-" .:is submerged in a fluid, all of the cylinders are cou- teristics are not known and are difficult to accountpled by the fluid. The natural frequency of each for. a--

cylinder in a vacuum must be known in order to for.

define detuning. In general, the detuning of a cylin- In general, flow velocity is not uniform either in theder array increases the critical flow velocity. In a axial direction along the cylinder or perpendicularwater-loop test, Chen and Jendrzejczyk [23] demon- to the cylinder. Most experiments are conductedstrated the effect of detuning on fluid-damping-con- for uniform flow. In practice, however, nonuniform "':

trolled-instability. They showed that an elastic tube flow distribution must be considered. Connors [30]surrounded by rigid tubes in water flow can lose has shown that the skimming flows created in thestability; the motion is predominantly in the lift vicinity of inlet-nozzle impingement plates can causedirection. This agrees with the theory that a single instability; the critical flow velocity depends onelastic tube in a rigid square array can lose stability cylinder pattern and spacing and on the clearanceby a fluid-damping force in the lift direction [11, between the cylinder array and the wall. In a large12]. Other experimental data [20, 22] and analyt- cylinder array, the cylinders do not become unstableical results (9, 131 are basically in agreement with at the same time; this phenomenon has been attrib-those of Chen and Jendrzejczyk [23]. uted to nonuniform flow distribution and other

effects.Tests with differences in streamwise and transversefrequencies ranging from 6.3 and 57% for a rotated Empirical correlations have been developed for thetriangular array with a pitch ratio of 1.375 were case in which an entire cylinder length is subjectedconducted by Weaver and Koroyannakis [24]. They to the same flow velocity. In many structural compo-found that the critical reduced flow velocity based nents or experiments, however, the flows are noton the lower frequency increased only slightly above uniform. A general practice has been to reduce thethat of the symmetric case; it was about 20% higher general case of nonuniform flow to the ideal case ofthan the velocity for tubes with identical stiffness in uniform flow. An equivalent uniform flow velocity -.

the transverse and streamwise directions. The effect is defined bywas essentially independent of the difference infrequency and direction of the lower frequency f U2 (z) 1(Z)dz.

relative to flow. Note that the results apply only Ue = (3)to a particular tube arrangement. Effects are not f m (z)dzthe same for different tube arrays. For example,for a tube row in water flow the lowest critical flow where oIm(z) is the mth orthonormal function ofvelocity is associated with the out-of-phase mode in the cylinders. Equation (3) has been used frequentlythe lift direction [22]. In this case an increase in [19, 28, 30]. It is applicable for high reduced flowthe natural frequency in the drag direction will have velocity [12, 13] but is not strictly applicable at lowlittle effect on critical flow velocity, reduced flow velocity.

Upstream turbulence can affect critical flow velocity. The critical flow velocity depends on cylinder layout. .

Wind-tunnel experiments [25, 26] have shown that Systematic studies have been conducted for different

S21- . - •

. - .1.. ..

9 . -. . . . . . . . .. .

- t~b~...t. k. ~ .'-..-

cylinder arrays [17-211. Available experimental the clearance does not significantly affect the naturaldata published up to 1981 have been compiled [34] frequencies for modes in which support plates corre-for five different cylinder arrays: cylinder rows, spond to nodal points, it has the effect of increasingsquare arrays, rotated square arrays, triangular arrays, the critical flow velocity [40]. The interaction ofand rotated triangular arrays, For practical pitch-to- cylinders with support plates in cross flow is fairlydiameter ratios, the effect of pitch-to-diameter ratio complex and is currently being studied.for square and rotated triangular arrays is not asimportant as other patterns. Fluid force. Fluid forces acting on rigid and moving

cylinders are measured using pressure transducersWater tunnel experiments have been conducted on a [20, 41], strain gauges [8-10], and fluid-force trans-triangular array of tubes with a pitch ratio of 1.5 ducers [421. The pressure for rigid and moving cylin-[35]. The critical flow velocity for the triangular ders has also been measured [20]. The pressurearray was about twice that of the rotated triangular obtained for a rigid cylinder has been analyzedarray. However, the critical flow velocity for tri- to obtain frequency spectra, correlation length,angular array was very sensitive to incident flow and rms force coefficient. The pressure for a movingdirection. cylinder is similar to that of a rigid cylinder but

also contains a pure tone spike at the frequencyThe mass ratio of a cylinder to the displaced mass of cylinder vibration. This pure tone spike corre-

-, of fluid and cylinder damping are two important sponds to the motion-dependent fluid force that-, parameters in determining critical flow velocity is important for stability. Similar measurements

Experiments have been conducted to study the have also been made by other workers [41].effects of these two parameters. One of the follow-ing methods has been used: (1) placing the samecylinder array in air and water flow [9, 36] and in Data from pressure transducers must be integratedwater and air-water two-phase flows [17], (2) using to obtain the resultant fluid force. Direct measure-a different set of cylinder mass for the same array ments of fluid forces have been made [8-10, 42]. In(9, 13, 38], and (3) varying cylinder damping for one case [8-10] the cylinder strain was measured andthe some array [13, 19, 22]. Experimental data are the fluid force based on cylinder motion was calcu-in agreement with results based on the semi-analytical lated. In the other case [42] the resultant fluid forcetheory. In air flow, according to the semi-analytical was measured directly using a force transducer.theory [13] and experimental data, the mass ratioand damping can be combined as a single parameter Fluid-force data associated with a moving cylinderand the stability criterion expressed in equation (1) [8-10] has been used to calculate fluid-damping andis applicable. However, in liquid flow mass ratio and fluidelastic-stiffness coefficients as functions of thedamping must be treated as two independent param- reduced flow velocity. [12]. These coefficients caneters; in this case the stability criterion expressed be used to calculate the critical flow velocity.in equation (2) is more appropriate.

Cylinder response characteristics vary significantly DESIGN CONSIDERATIONSwith cylinder-to-support clearance. In turn, theeffective clearance is a function of the initial me- Various design guidelines have been proposed to eval-chanical fit up, tolerances, thermal expansion, and uate heat transfer equipment [33,34,43,44]. In moststeady fluid forces. In the past cylinders supported cases a single criterion has been used for both lightby baffle plates have been treated as beams on knife- and heavy fluids and for all cylinder layouts. Chenedge supports. This assumption is reasonable so long [34] used his semi-analytical model to compile avail-as the clearance between cylinder and support plate able experimental data for different cylinder patternsis small. When the support clearance is relatively and different criteria for light and heavy fluids. Inlarge, the cylinder rattles around in whatever space general, the experimental data obtained for light fluidis available. The supports cannot act as nodal point agree well. The significant scattering of data that oc-until they are impacted and significant response in curs in heavy fluid has been attributed to varioustheoretically restrained modes occurs [39]. Although causes: using different system parameters (see Ta-

22

%'=•,'~~~~.. .%'*'% "**% .=-" .... %%... ". ".. .... .. "• -•-

N.

ble 1), difficulty in defining the critical flow velocity, * Experimental and analytical techniques havedifferent mass ratio and damping, and differences in been developed to characterize and predictinterpretation of data. instability phenomena; theory and experi-

mental data are in agreement.Design guidelines are useful in the assessment of apreliminary design. In many cases a scaled model Dynamic instability of cylinders in cross flow hasor full scale of a sector are needed for design verifi- been an area of recent progress. Future studies arecation to assure that dynamic instability will not expected to focus in the following areas:occur. For example, a test has been conducted on a -,

half-scale sector model of a steam generator helicalcoil tube bank [45]. In addition, certain features 0 Mathematical models and stability criteria:

are difficult to account for in the general stability the analytical model [15] is useful for exam-criteria and must be considered [39, 40]. There are ining instability phenomena qualitatively; it is

very few cases in which complete fluid force data doubtful that such a model can be improved

are available and detailed analyses can be made [46]. to predict details of instability characteristics.The quasi-static model [5, 6, 14] is useful in

Most data for simple test sections are obtained under certain parameter ranges but is not alwayslaboratory conditions; questions are raised as to applicable. The semi-analytical method [8-10,

whether these data are applicable to real heat ex- 11-13] appears promising for predicting de-changers. To evaluate and improve prediction meth- tailed characteristics; if numerical techniques

ods and design criteria a specifically built and in- can be developed to calculate fluid-damping

strumented, industrial-type, shell-and-tube heat ex- and fluidelastic stiffness coefficients, this

changer has been tested to obtain tube vibration method could become very powerful.[47]. Fluid forces: fluid-force components are key$7 ~~data under controlled conditions 47. Data gener-fatrinhepdcioofrtclfowvo-

ated from tests are being made available to research- factors in the prediction of critical flow veloc-

ers and engineers for use in evaluating and improving ity. Both experimental measurements andpredictive methods and design guides. numerical calculations of fluid forces areneeded to improve prediction techniques.

0 Flow field: understanding the flow field around

CONCLUDING REMARKS cylinder arrays oscillating in flow is important.Flow visualization and measurements of local

Significant progress has been made in the past few pressure and flow velocity will allow identifica-years on the subject of instability of circular cylinder tion and quantification of important system

arrays in cross flow. The three major accomplish- parameters.

ments are as follows: 0 Effects of different system parameters: sta-bility under some special conditions, such as

0 Two instability mechanisms have been recog- nonuniform flow and support clearance, arenized: fluid-damping-controlled and fluidelas- also important and are expected to receive

tic-stiffness-controlled instability. Although dif- more attention.

ferent investigators are still not in agreementon the mechanisms, it is clear that the fluid In the past decade the original work by Connors [5]force associated with the quasi-static displace- has given impetus to numerous studies of cylindersment mechanism proposed in 1970 is not the in cross flow. The dynamic instability of cylindersonly one that contributes to instability, in cross flow has been confusing, but the develop-

* In light fluid mass ratio and damping can be ment of various models and experimental data, incombined as a single parameter; the exponent particular the semi-analytical model, has shed lightof the mass-damping term is 0.5. In heavy on the problem. Although our understanding offluid the two parameters must be treated the problem remains incomplete, there is a soundindependently. Stability criteria in light and basis and direction for future development towardheavy fluids also differ, quantifying critical flow velocity.

23

ty .- ,,,,-=, -. = *,*-. -w° - .. .. .... .... .. . .. .....

REFERENCES 11. Chen, S.S., "Instability Mechanisms and StabilityCriteria of a Group of Circular Cylinders Sub-

1. Tatone, O.S. and Pathanta, R.S., "Steam-Genera- jected to Cross Flow; Part I: Theory," J. Vib.,tor Tube Failures: World Experience in Water- Acoust., Stress, Reliability Des., 105, pp 51-58Cooled Nuclear Power Reactors in 1976," Nucl. (1983).Safety, 12(6), pp 748-760 (1978).

12. Chen, S.S., "Instability Mechanisms and Stability

2. Paidoussis, M.P., "Flow-Induced Vibrations in Criteria of a Group of Circular Cylinders Sub- - -'

Nuclear Reactors and Heat Exchangers, Practical jected to Cross Flow; Part I1: Numerical ResultsExperiences and State of Knowledge," in Prac- and Discussions," ASME Paper 81-DET-22; to .tical Experiences with Flow-induced Vibrations appear in J. Vib., Acoust., Stress, Reliability Des.(eds. Naudascher, E. and Rockwell, D.), Springer-Verlag, Berlin, pp 1-81 (1980). 13. Chen, S.S. and Jendrzejczyk, J.A., "Stability of

Tube Arrays in Crossflow," to be published

3. Halle, H., Chenoweth, J.M., and Wambsganss, (1983).

M.W., "DOE/ANL/HTRI Heat Exchanger Tube 14 'MVibration Data Bank," Argonne Natl. Lab., 14. Price, S.J. and Paidoussis, M.P., "Fluidelastic .....

4 Tech. Memo. ANL-CT-80-3 (1980). Instability of an Infinite Double Row of CircularCylinders Subjected to a Uniform Crossflow,"

S4 e S "r- -u IaiJ. Vib., Acoust., Stress, Reliability Des., 105,":4. Chen, S.S•, "Cross-Flow-Induced Instabilities of p 59-6 (1983).

Circular Cylinders," Shock Vib. Dig., 12 (5), pp p - 121-34(1980). 15. Lever, J.H. and Weaver, D.S., "A Theoretical

Model for Fluidelastic Instability in Heat Ex-5. Connors, H.J., "Fluidelastic Vibration of Tube changer Tube Bundles," J. Pressure Vessel Tech.,

Arrays Excited by Cross Flow," in Flow-Induced Trans. ASME, 104, pp 147-158 (1982).Vibration of Heat Exchangers, ASME, pp 42-56(Dec 1970). 16. Whiston, G.S. and Thomas, G.D., "Whirling In-

stabilities in Heat Exchanger Tube Arrays," J.6. Blevins, R.D., "Fluid Elastic Whirling of a Tube Sound Vib., 81 (3), pp 1-31 (1982).

Row," J. Pressure Vessel Tech., Trans. ASME,pp 263-267 (1974). 17. Heilker, W.J. and Vincent, R.Q., "Vibration in

Nuclear Heat Exchangers due to Liquid and Two-7. Blevins, R.D., "Fluid Damping and Whirling In- Phase Flow," J. Engrg. Power, Trans. ASME,

stability of Tube Arrays," in Flow Induced 103, pp358-366(1981).Vibrations, ASME, pp 35-39 (1979).

18. Soper, B.M., "The Effect of Tube Layout on the8. Tanaka, H., "A Study on Fluid Elastic Vibration Fluidelastic Instability of Tube Bundles in " "

of a Circular Cylinder Array (One-Row Cylinder Cross Flow," in Flow-Induced Heat ExchangerArray)," Trans. Japan Soc. Mech. Engrs., 46 Tube Vibration - 1980 (eds. Chenoweth, J.M.(408) (Section B), pp 1398-1407 (1980). and Stenner, J.R.), ASME, pp 1-9 (1980).

9. Tanaka, H. and Takahara, S., "Fluid Elastic 19. Chen, S.S. and Jendrzejczyk, J.A., "Experiments

Vibrition of Tube Array in Cross Flow," J. on Fluid Elastic Instability in Tube Banks Sub- , "

Sound Vib., 77, pp 19-37 (1981). jected to Liquid Cross Flow," J. Sound Vib.,78 (3), pp 355-381 (1981).

10. Tanaka, H., Takahara, S., and Ohta, K., "Flow-Induced Vibration of Tube Arrays with Various 20. Blevins, R.D., Gibert, R.J., and Viliard, B.,Pitch-to-Diameter Ratios," in Flow-Induced "Experiments on Vibration of Heat ExchangerVibration of Circular Cylindrical Structures, Tube Arrays in Cross Flow," 6th SMiRT, PaperASME, pp 45-56 (1982). No. B6/9 (1981).

24

" " ° ° °" % °° "" "

'.. . .. . . . . . . . . . . .".. . ". . ". . . . .° • "

". . .. . . . . . S. - ' - - . - .

. _ ... ... . . .. . . .... .. . .. .. ... -... . .. '. .°.'...,.'-ooo

21. Zukauskas, A.A., Katinas, V.J., Perednis, E.E., 31. Weaver, D.S. and EI-Kashlan, M., "On the Num-and Sobolev, V.A., "Viscous Flow Over Inclined broTueRwRqiedtSuyCos-Flow ':.' !In-Line Tube Bundles and Vibrations Induced Induced Vibrations in Tube Banks," J. Sound

in the Latter," Fluid Mechanics - Soviet Re- Vib., 75 (2), pp 265-273 (1981).search, 9 (4), pp 1-12 (1980).

32. Remy, F.N., "Flow Induced Vibration of Tube

22. Chen, S.S. and Jendrzejczyk, J.A., "Experiment Bundles in Two Phase Cross Flow," Third

and Analysis of Instability of Tube Rows Subject Keswick Intl. Conf. Vib. Nucl. Plants, English

to Liquid Crossflow," J. AppI. Mech., Trans. Lakes, U.K., Paper Log No. 68 (May 1982).

ASME, 48, pp 704-709 (1982). 33. Pettigrew, M.J. and Gorman, D.J., "Experimental 7*.

23. Chen, S.S. and Jendrzejczyk, J.A., "Flow Veloc- Studies on Flow Induced Vibration to Support

ity Dependence of Damping in Tube Arrays Steam Generator Design, Part III - Vibration of

Subjected to Liquid Crossflow," J. Pressure a Small Tube Bundle in Liquid and Two-PhaseVessel Tech., Trans. ASME, 103, pp 130-135 Cross Flow," Proc. Intl. Symp. Vib. Problems(1981). T Indus., Keswick, U.K., Paper No. 4-24 (1973).

34. Chen, S.S., "The Instability Flow Velocity of24. Weaver, D.S. and Kcroyannakis, D., "Flow In- T aocnTube Arrays in Crossflow," Proc. Intl. Conf. .. :.

duced Vibrations of Heat Exchanger U-Tubes, Flow Induced Vib, Fluid Engrg., Reading,A Simulation to Study the Effects of Asym- Flanduce N. F2 Engrg., Reading,

metric Stiffness," J. Vib., Acoust., Stress, Reli- E a pr 2( 16 )ability Des., 105, pp 67-75 (1983). 35. Yeung, H.C. and Weaver, D.S., "The Effect of

Approach Velocity Direction on the Flow-25. Gross, H., "Investigations in Aeroelastic Vibra- Induced Vibrations of a Triangular Tube Array,"

tion Mechanisms and Their Application in De- J. Vib., Acoust., Stress, Reliability Des., 105 (1),sign of Tubular Heat Exchangers," Technical pp 76-82 (1983).University of Hanover, Ph.D. dissertation (1975).

36. Weaver, D.S. and Koroyannakis, D., "The Cross-26. Southworth, P.J. and Zdravkovich, M.M., "Effect Flow Response of a Tube Array in Water - A

of Grid-Turbulence on the Fluid-Elastic Vibra- Comparison with the Same Array in Air," J.tions of In-Line Tube Banks in Cross Flow," Pressure Vessel Tech., Trans. ASME, 104, ppJ. Sound Vib., 39 (4), pp 461-469 (1975). 139-146 (1982).

27. Gorman, D.J., "The Effects of Artificially In- 37. Zukauskas, A. and Katinas, V., "Flow-Inducedduced Up-Stream Turbulence on the Liquid Vibration in Heat-Exchanger Tube Banks," inCross-Flow Induced Vibration of Tube Bundles," Practical Experiences with Flow-Induced Vibra-ASME PVP-41, pp 33-43 (1980). tions (eds., Naudascher, E. and Rockwell, D.),

Springer-Verlag, Berlin (1980).

28. Franklin, R.E. and Soper, B.M.H., "An Investi-gation of Fluidelastic Instabilities in Tube 38. Weaver, D.S. and EI-Kashlan, M., "The EffectBanks Subjected to Fluid Cross-Flow," 4th of Damping and Mass Ratio on the StabilitySMiRT, Paper No. F6/7 (1977). of a Tube Bank," J. Sound Vib., 76 (2), pp

283-294 (1981).29. Soper, B.M.H., "The Effect of Grid Generated

Turbulence on the Fluidelastic Instability of 39. Weaver, D.S. and Schneider, W., "The EffectTube Bundle in Cross Flow," Paper No. P10.6, of Flat Bar Supports on the Cross Flow InducedDubrovnik (Sept 7-12, 1981). Response of Heat Exchanger U-Tubes," ASME

Paper No. 82-JPGC-NE-12 (1982).30. Connors, H.J., "Fluid-Elastic Vibration of Tube

Arrays Excited by a Non-Uniform Cross Flow," 40. Gorman, D.J., "The Effects of Tube-to-BaffleASME Publication PVP-41, pp 93-107 (1980). Plate Clearances on the Liquid Cross-Flow In-

25

*- - - - - - - - - -

. . -, . .

duced Vibration on Heat Exchanger Tube 44. Pettigrew, M.J. and Ko, P.L., "A ComprehensiveBundles," Presented at 33rd Ann. Tech. Mtg. Approach to Avoid Vibration on Fretting inPetroleum Soc. CIM, Calgary, Alberta, Canada Shell and Tube Heat Exchangers," ASME Publi-(June 6-9, 1982). cation PVP-41, pp 1-18 (1980).

41. Heinecke, E.P. and Mohr, K.H., "Investigations 45. Chen, S.S., Jendrzejczyk, J.A., and Wambsganss,on Fluid Borne Forces in Heat Exchangers with M.W., "Tube Vibration in a Half-Scale SectorTubes in Cross Flow," Third Keswick Intl. Conf. Model of a Helical Tube Steam Generator," toVib. Nucl. Plants, English Lakes, U.K., Paper appear in J. Sound Vib.Log No. 36 (May 1982).

46. Ohta, K., Kagawa, K., Tanaka, H., and Takahara,42. Jendrzejczyk, J.A. and Chen, S.S., "Fluid Forces S., "Study on the Fluidelastic Vibration of Tube

Acting on Circular Cylinders in Liquid Cross Arrays Using Modal Analysis Technique," ASMEFlow," ASME Publication PVP-63, pp 31-44 PVP-63, pp 57-69 (1982).(1982).

47. Halle, H., Chenoweth, J.M., and Wambsganss,43. Remy, F.W. and Bai, D., "Comparative Analysis M.W., "Flow-Induced Tube Vibration Tests of

of Cross-Flow Induced Vibrations of Tube Typical Industrial Heat Exchanger Configura-Bundles," Proc. Intl. Conf. Flow Induced Vib. tions," ASME Paper No. 81-DET-37; PresentedFluid Engrg., Reading, England, Paper No. F3 at ASME Des. Engrg. Conf., Hartford, Connecti-(Sept 14-16, 1982). cut (Sept 1981).

.W

26

...

- ~ fl * -. - -- -"-•

NONSTATIONARY RESONANCE OSCILLATIONS

B.N. Agrawal* and R.M. Evan-Iwanowdd"

7 Abstract. This article describes nonstationary oscilla- amplitude of excitation H = H(t), or both a' and H aretions in combination reonances, factors affecting functions of time.nonstationry rewonses, and applications and un-soved problems of nonstationary responses. It has been found that either linear or cyclic varia-

tions of these parameters with time are sufficient todescribe nonstationary responses. More complicated

Nonstationary resonance responses occur when time functions of the transitions do not provideexternal excitation parameters - frequency, ampli- any essentially new information.tude, or both - vary with time close to stationaryresonance frequencies. This process is also known aspassage through a resonance or sweep through a reso- NONSTATIONARY OSCILLATIONSnance. IN COMBINATION RESONANCES

The first concerted investigations of nonstationary Salient features of nonstationary responses of systemsresponses were presented in a monograph by Yu.M. exhibiting either parametric* or combinationMitropol'skii [1]. Mitropol'skii, like most of the additive resonances can be described from the be-Russian School of Mechanicians, limited his analysis havior of a cylindrical panel subjected to axial andof nonstationary responses to dynamic and para- transverse periodic loads (Figure 1) and simplymetric resonances. A more extensive treatment of supported along all edges and sides. Consider linearthis phenomenon can be found in the book by R.M. variation of the frequency P, (t) = Po + at [4] ; o andEvan-lwanowski [2]. He presents nonstationary a are constants.responses for combination resonances - additive(summation) and differential.

/" X

A stationary combination resonance is characterized .by the following relationship between the frequencya of the external harmonic excitation and the naturalfreq uencies wj, j = 1,2.. n of the system:

nko P= E Kjwi 1

j= 1where ko and kj are integers - positive, negative, or a tzero -- and n is the number of degrees of freedom 7of the system. The phenomenon that occurs whenko = 0 is called internal resonance. When all kj are Figure 1. Cylindrical Panel and Loadingpositive, an additive (summation) resonance occurs. a'1 (t) = 01 (t) = a'o + atIf some kj are negative, the result is differentialresonance [3]. Nonstationary responses occur whenthe external excitation P(t) = H(t) cos 0(t); that is, Figure 2 is a summary of nonstationary responses.when the frequency of excitation v(t) = e(t), the Three categories of the response -- denoted by C1,O~nlorAtmberof the Technial Staff, INTELSAT, 490 L'Enfant PlMaza East &W., Washlngton, D.C 20024"Profassor, Syracure University, Syracuse, NY9The parametric (nin) reonanse is, In aseanet, an additive combination resonance whereby two distinct frequencies coalesce

Into a double frequency.27

--~~~~~~~~~......-.,.:..........--:-.-:...............:.......-.... ...... .:-:-.--. -...-. .. .. ..

C2, and C3 in Figure 2 -- can be distinguished, de- lies in the ranges of values of a and possibly otherpending on the rate of transition a. Responses in the factors. The initial conditions or variations of thecategory Cl follow the stationary response, where material constants do not provide any clue.P. is assumed to be constant. In C2 the response 9tends to the initial condition. In C3 the response A remark pertaining to the analysis of systems ex-tends to static equilibrium, sometimes dropping cited by external forces with randomly varyingrapidly to the equilibrium condition, frequencies (i.e., with randomly varying a) is ap-

propriate. From the preceding paragraph, it can be

Detailed analysis of nonstationary responses leads to concluded that only statistical analyses can be carrieda startling situation. The separation between the out for some definite ranges of a. Otherwise, it iscategoreis C1, C2, and C3 is very sharp. For instance difficult to imagine how responses can jump fromthe small difference in the transition (sweep) rates relatively small values (curves C2 and C3 for somebetween a = 1.269 and a = 1.268 -- i.e., only 0.001 -- a) to the excessively large values (curves C1 forproduces a marked difference in the nonstationary other a).response. In the first case the response tends toinfinity (curve C1 of Figure 3); in the second case Laboratory experiments conducted for a discretethe response tends to a finite value (curve C2 of system consisting of three masses (three degrees ofFigure 3). This type of behavior has been observed freedom) and exhibiting an additive combinationfor other systems with various additive resonances resonance (among other resonances) P = w, + W 2

[2]. + W3 support analytical results [5]. Stationary andnonstationary responses for this experiment are

Another somewhat puzzling manifestation of non- shown in Figures 5 and 6 (WI , o2, and w 3 are thestationary responses is shown in Figure 4 (and to natural frequencies of the system). Figure 6 shows

some extent in Figure 3). For the first four or five experimental results for the decreasing excitation fre-cycles the response C1 (a = 0.06) and C2 (a = 0.04) quencies, v(t) = P o - a t. For such cases, the ampli-almost coincide. Later, however, they diverge dra- tudes of the nonstationary responses are decreasingmatically. An explanation for such behavior is still [5].being sought by the authors. The answer evidently

Stationary response "" "

a 9.0

'0.? I0B-0.7 C2

% -0.6OC3

•1.14 1.1 1.22 1.26 1.20 1.34 130P2 /2w,

Figure 2. Transition through Resonance: Effect of Sweep Rates on Resonance Response

28

'202 . . . . . .,

" ." ,. ,." . " , ",, . ,' J ,h .. , .', '....' ,'. '-., , ",, . " . .'., . ... , . . .

.17%

P2 /2(4 1 2. 16(1 a t) 1.6

K~~~o 110.269ti~C2

a I I

r V/12()

Figure 3. Transition through Resonance: Response Category Changes for Very Close Sweep Rate

00.0

C2I

Figure 4. (w - P/2) Parametric Resonance: Nonstationary Response

29

A32A32

H 111.5m minUm H1.

2.9 24

2.3- 2.3

A Statatooary

.7 47.3 47.0 #ONW 47 4?.3 47.6 Op

Figure 5. v'=cw, + W2 + W3. Combination Resonance Figure 6.Pw +CAW2 +(AW3. Combination Resonance-. (See Table.v v0 + at) (See Table.vP P0 + Ot)

Table. Parameter SpecificationsP VWl + C02 + W)3

ve a,Case POMM

1 47.6 0.025 1.5 2 a 6.0

2 47.6 0.075 1.5

3 47.6 0.25 1.5 Stationary 0

4 4 47.6 0.75 1.5 Sal.V 5 47.6 2.5 1.5 0

6 48.4 - 0.075 1.57 48.4 -0.75 1.5

8 48.4 -1.0 1.5 Ofa 1.9 48.4 -2.5 1.5

StSmiaamnfettinionantrinryrspne

statinary espose ofthe yroscpitaystem showimigre 7aniehaiits the nstachar esc s tes Fiur 7.0 obnto eoac

panel benobsred fo 49ocoi forem all cures

sytm8ujce0o n nonevtv ustn

focs- olwr ocs fo intac [.. . . . .no-ios _

stationary.........................................

in~~~~~~~~~~~ Fiur 7ehbtthsaecaatrsiaste Fge7. P l W2Cmiaio eoac

NN

Figure 8 shows nonstationary amplitudes of thesystem for cyclic variation of the excitation fre-quency for Y = 60 + 2.5 sin 0.5t (curve a) and P =60 + 2.5 sin t (curve b). Note again that these tworesponses are drastically different; they apparentlydepend on the frequency of the transition (sweep).One exhibits cyclic variation of the amplitude, and v-60+2.huatanother tends rapidly to zero.

Interesting and puzzling results have been obtainedfor variations of the amplitude H(t) of the forcing 0.,function P(t) = H(t) cos 0(t); Y(t) = 6(t), and P iskept constant in Figure 9. Simultaneous variationsof both H(t) and P(t) [21 are shown in Figure 10. StationaFigure 9 shows the nonstationary amplitude for H(t) Stable= Ho + ,tt, ' = constant for various values of a,.Figure 10 presents the results for H(t) = Ho + alt _and v = Po + at for various values of a, and a. Addi-tional background on the subject is available [9-321.

Statioary eo0 +

FACTORS AFFECTING NONSTATIONARY UatableRESPONSES 2.5 sin 0.5t

bThe factors that markedly effect nonstationary re- to

sponses are, in order of significance [21:

* geometrical nonlinearities: large deformationsand attendant longitudinal and rotatory inertias Figure 8. w, W2 - .Combination Resonance

* nonlinear restoring and dissipative forces,particularly, hysteretic dissipative forces, whichcan considerably modify the response

* nonideal external excitations* resulting in theinteraction between excitation and systemresponses

PRACTICAL APPLICATIONS 09"-

In some complex systems in which the mechanical Ston Stable

strength of the system is low, resonance frequencies

can be found experimentally by sweeping the exci-tation frequency rapidly through the wide range, o3 Stationar Unstable

thus avoiding a high buildup of resonance ampli- -- ------.-10-

tudes. Particularly convenient is a variation in thedirection of decreasing frequencies by which the o s so o to ,s us,

amplitudes are rapidly decreasing. Another possible Hpractical application of nonstationary responses iseffective stabilization of resonance oscillations byan appropriate transition rate through the resonance Figure 9. Nonstationary Amplitude(see Figure8). (H = Ho +c, t)SRe r d to as tuow with lmited power (20).

31

. 7 . ..

-' 5. Hsieh, J.S., Doctoral Dissertation, SyracuseUniversity (1974).

6. Parthasarathy, A. and Evan-lwanowski, R.M.,"Resonances in a Continuous System Subjected

to a Pulsating Follower Force," SURI (1970).

N 7. Ostiguy, G., Doctoral Dissertation, SyracuseUniversity (1970).

8. Becker, L., "Experimentelle und numerische

P9 - 0.708;=tO- 0.001; H0 - 0.02;a1l - 10- Untersuchung von Kombinationsresonanzen,"

P0 - 1.414; a -0.001; H 0 - 0.02; r1 =-10-6 Karlsruhe (1972).

Pv0 - 1.414; Ot - -0.001; H 0 - 0.02; ot, - -2.10 - s

Figure 10. Nonstationary Amplitude 9. Mettler, E., "Combination Resonances in Me-

chanical Systems under Harmonic Excitation,"

Proc. Fourth Conf. Nonlin. Oscill., PragueUNSOLVED PROBLEMS 1967, S.51, Academic Prague (1968).

It is essential to determine the parameters of system 10. Leiss, F., "Zur Berechnung von Resonanzschwin-excitation and initial conditions that are responsible gungen quasilinearer mechanischer Systeme mit 1

for a specific category of nonstationary responses; der asymptotischen Methode," Dissertation,i.e., (i) tending to infinity, (ii) tending to initial Karlsruhe (1966).conditions, or (iii) dropping to static equilibrium.This can be significant for the cyclic variation of the 11. Mettler, E., "AIlgemeine Theorie der Stabil-frequency v(t). In this case very small perturbations itaet erzwungener Schwingungen elastischercan totally (zero amplitude) stabilize the system

Koerper," Jng. Arch. 17, S 418 (1949).(see Figure 8). Another problem is the interactionof various modes. It is significant that some verydistant modes without much energy individually 12. Adams, Jr., O.E. and Evan-lwanowski, R.M.,

can transfer this energy to one mode and cause "Passage through Parametric Resonance of a

failure. Reinforced Cylindrical Shell," Proc. ThirdCanadian Cong. AppI. Mech., pp 433-434 (May17-21, 1971).

REFERENCES

13. Goodier, J.N. and Mclvor, I.K., "The Elastic

1. Mitropol'skii, Yu.A., "Problems of the Asymp- Cylindrical Shell under Nearly Uniform Radial

totic Theory of Non-stationary Vibrations," Impulse," J. AppI. Mech., Trans. ASME, pp 259-

Israel Program Sci. Transl., Jerusalem (1965). 266 (June 1964).

2. Evan-lwanowski, R.M., Resonance Oscillations 14. Cutts, S.J., "Internal Resonance of Two Degreesin Mechanical Systems, Elsevier, Amsterdam of Freedom Mechanical Systems," M.S. Thesis,(1976). Syracuse University (1968).

3. Agrawal, B.N., Doctoral Dissertation, Syracuse 15. Kononenko, V.O., "Resonance Vibrations of aUniversity (1970). Shaft with a Disc," Izv. AN SSSR, OTN, No. 7,

pp 87-90.4. Mittal, S. and Evan-lwanowski, R.M., "Reso-

nance Oscillations in a Cylindrical Panel," Con- 16. Tondl, A., "Some Problems of Rotor Dynamics,"gres de Mechanique Appliquee (1979). Publ. House of CSAV, Prague (1965).

32

" - * -' '." ' .",''." ,"",". . -- " - ." . .'" " " " ".-""- '- . ...-. - ' " ,"- . " ".

17. Ehrich, F.F., "Sum and Difference Frequencies 27. Bolotin, V.V., Nonconservative Problems of thein Vibration of High Speed Rotating Machinery," Theory of Elastic Stability (English translation),

ASME Paper No. 71 - Vibr.-103, pp 1-4 (1971). Pergamon Press (1963).

18. Messal, E.E., "Subharmonic Rotor Instability 28. Herrmann, G., "Stability of Equilibrium ofdue to Elastic Asymmetry," Ph.D. Dissertation, Elastic Systems Subjected to NonconservativeIllinois Inst. Tech., Chicago (1970). Forces," AMR, 20, pp 103-108 (1967).

19. Yamamoto, Z. and Ota, H., "On the Unstable 29. Gregory, R.W. and Paidoussis, M.P., "Unstable

Vibrations of a Shaft Carrying an Unsymmetrical Oscillation of Tubular Cantilevers ConveyingRotor," J. AppI. Mech., Trans. ASME, 86 (3) Fluid," Parts I and II, Proc. Royal Soc. (Lon-don), Ser. A., 293 pp 512-527, pp 528-542pp 515-522 (Sept 1964).%(1966). [ [

20. Kononenko, V.0., "Vibrating Systems with 3 Nemat-Nasser, S., Prasad, S.N•, and Hermann,Limited Excitation," Nauka., Moscow (1964); G., "Destabilizing Effect of Velocity-DependentAMR 19 (1966), Rev. 1483. Forces in Nonconservative Continuous Systems,"

AIAA J.,4, pp 1276-1280 (1966).

21. Subach, A.P., "Experimental Investigations ofthe Influence of Dry Friction on the Instability 31. Kiusalaas, J. and Davis, H.E., "On the StabilityRegions of Vibrating Systems with an Engine of Elastic Systems under Retarded Followerof Limited Power," Sb. Voprosy Dinamiki Forces," Intl. J. Solids Struc., 6, pp 399-409Prochnosti, 8, Riga (1962), pp 37-50; AMR 17 (1970).(1964), Rev. 3806.

32. Beal, T.R., "Dynamic Stability of a Flexible

22. Proust, L., "Transition through the Resonance Missile under Constant and Pulsating Thrusts,"Zone in Vibrating Mechanical Systems Taking AIAA J., 3, pp 486-494 (1965).into Account the Influence of Vibrator," ISNV,

.111, p 398, 1961 (R); [Lecture 161. 33. Brown, J.E., Hutt, J.M., and Salama, A.E., "Fi-nite Element Solution to Dynamic Stability of

23. Bhargava, D., "Interaction of Mechanical System Bars," AIAA J., 6, pp 1423-1425 (1968).

with a Nonideal Source of Energy (Sommerfield ".a•-IEffect)," M.S. Thesis, Syracuse University 34. Schmidt, G. and Weidenhammer, F., "Insta-(1967). bilitaeten gedaempfter rheolinearer Schwingun-

gen," Math. Nachr., 23, pp 301-318 (1961).

24. Sewell, M.J., "On Configuration-Dependent 35. Hagedorn, P.B., "On the Lateral Buckling of aLoading," Arch. RatI• Mech. Anal., 23, pp Beam Subjected to the Reaction of a Pulsating327-351 (1967). Fluid Jet," Publ. No. 5.70, Federal University,

25. Shieh, R.C. and Masur, E.F., "Some General RioeJaneiro (1970).

Principles of Dynamic Instability of Solid Bod- 36. Hagedorn, P.B., "Kombinationsresonanz undies," Z. angew Math. Phys., 1 pp 927-941 Instabilitaetsbereiche ... mit nichtlinearer(1968). Daempfung," Ing. Arch., 38, pp 80-96 (1969).

26. Herrmann, G. and Bungay, R.W., "On the 37. Tso, W.K. and Fung, D•P.K., "Dynamic Insta-Stability of Elastic Systems Subjected to Non- bility under the Combined Actions of Noncon-conservative Forces," J. AppI. Mech., Trans. servative Loading and Base Motion," J. Appl.ASME,.3j, pp 435-440 (1964). Mech., Trans. ASME, 38, pp 1074-1076 (1971).

33

" 4.

. . . . . . . . . . . .. . . . . . . . . . . . . . . . . . . . . . . .

BOOK REVIEWS

ACOUSTICS: AN INTRODUCTION An extensive subject index as well as a name indexTO ITS PHYSICAL PRINCIPLES are included. The text would be more useful, how-

AND APPLICATIONS ever, if additional example problems had been in-cluded. Another suggested improvement is the in-

A.D. Pierce clusion of answers to the exercises at the end of theMcGraw-Hill Book Co., New York, NY chapters. Overall, this book will be a welcome addi-

1981,642 pp, $29.95 tion to the library of the graduate level engineer withan interest in acoustics.

This book is one of a series of texts in mechanical V.R. Millerengineering and will be a highly useful reference in 5331 Pathview Driveacoustics. It is a carefully' written, intermediate-level Huber Heights, OH 45424survey of the physics underlying several areas ofacoustics and contains an extensive bibliography andmeasurement standards. The book can be used as aguide to the more advanced literature. NOISE CONTROL SOLUTIONS FOR THE

WOOD PRODUCTS INDUSTRY

The scope is much broader than that in TheoreticalAcoustics by Morse and Ingard. Included are suchtopics as the effects of moving media, not usually Fairmont Press, Atlanta, GAfound in textbooks, and the following chapters: 1980, 72 pp

1. The Wave Theory of Sound This book is a collection of noise control concepts2. Quantitative Measures of Sound designed for different types of machinery used in3. Reflection, Transmission, and Excitation of the wood products industry. It contains a brief sum-

Plane Waves mary of some existing literature on the subject. The4. Radiation from Vibrating Bodies book opens with a discussion on OSHA and an5. Radiation from Sources near and on Solid approach to industrial noise control. Each chapter

Surfaces contains tables and figures that provide some infor-6. Room Acoustics mation about noise control. Unfortunately, this7. Low Frequency Models of Sound Trans- book is not as good as other textbooks that present

mission excellent treatments of noise control and are not8. Ray Acoustics necessarily tailored specifically to the wood products

- 9. Scattering and Diffraction industry.

*10. Effects of Viscosity and Other DissipativeProcesses The proposed solutions are aimed at satisfying OSHA I

11. Nonlinear Effects in Sound Propagation requirements and typically involve using enclosuresto attain a desired noise level; however, the only

It is somewhat surprising that a chapter was not enclosures mentioned are made of wood, which mayincluded on acoustic measurements, even though not be allowed in production environments. Spectrathe author stated that some topics . . . such as jet are shown for various types of wood products equ ip-noise and acoustic imaging . . . were purposely ment, but no discussion on how these spectra can beomitted so that the text will not be unmanageable used is presented. Several other important details arein length, missing: no index; no discussion of community im-

34I2- '-. - . - -- - . - -4

, . = ,. = i . -, . J, = ,. . . : .. . . . :. . , . : .- , ,. - . . .. -. ,. . . ., . . . . ... .. , . . ... .. ._.. ... . ... .. .....

pact of specific equipment operation or prediction engineering scientists. Those interested in the connec-and measurement of equipment noise. tion between the theory and more traditional ap-

proaches to the same problem area are directed toThe authors did not succeed in achieving the objec- to the review article "Vibrations and Stability oftives stated at the beginning of the book. It could Mechanical Systems II" by K. Huseyin in the Shock .be used as a primer, but the more experienced reader and Vibration Digest (13 (1), Jan 1981, pp 21-29).can obtain better information on noise problems inthe wood products industry from other books on In the third article Zarka and Casier analyze thenoise control. cyclic loading of several simple elastic-plastic struc-

tures. Three parallel bars in axial loading, a thinV.R. Miller tube, and a rectangular plate are analyzed when

5331 Pathview Drive subjected to a prescribed traction or when the tem-Huber Heights, OH 45424 perature varies as a sine curve. The responses of these

structures are analyzed to answer such questions asdoes the deformation reach a periodic state, and, ifnot, how does the response of the structure proceed

MECHANICS TODAY, VOLUME 6 toward failure?

S. Nemat-Nasser, Editor The authors propose an extension of their analysesPergamon Press, New York, NY to general structures. They begin with their results,

1981, 204 pp, $50.00 which are necessarily restricted to simple structures.The generalization is achieved by obtaining boundsin parameter space.

This is the sixth volume of a series containing re-search level state-of-the-art review articles on various The addendum by F. Erdogan presents recent resultstopics in theoretical and applied mechanics. The book obtained by the author and updates material pre-contains three major articles and an addendum to a sented in Vol. 4 of Mechanics Today, 1978; pp 1-86,previously published article in another volume of the under the title "Mixed Boundary-Value Problems inseries. Mechanics." The same title is retained in the adden-

dum.In the first article McCoy treats elastic solids with amicrostructure much larger than the atomic scale L.Y. Baharbut much smaller than the characteristic size of the Department of Mechanical Engineeringentire structure. Examples include polycrystalline and Mechanicssolids and fiber-reinforced composites in which each Drexel Universityrandomly oriented crystal, fiber, or matrix region Philadelphia, PA 19104can be treated as a linearly elastic solid. Statisticalmodels are used to relate microstructural propertiesto the elastic characteristics of the entire structure.

THE CALCULUS OF VARIATIONS ANDIn the second article Sewell presents an extensive OPTIMAL CONTROL: AN INTRODUCTIONtutorial article on the subject of catastrophe theory.This subject is acquiring a great importance in me- G. Leitmannchanics; readers who want a simpler exposition of the Vol. 24 of Mathematical Concepts in Sciencesubject should read a reference that was published in and Engineeringthe Intemationl Journal of Mechanical Engineering Plenum Press, New York, NY " -*

Education and is the work of the same author. 1981, 311 pp, $35.00

Increased interest in qualitative methods in non-linear mechanics makes reasonable the current inter- This volume combines two related topics, each ofest in catastrophe theory by analytically inclined which deserves extensive treatment in its own right.

35

- A: - -.. . . . . . .

. . . . .. . . . .-. . . . . . .

However, in combining the two, the author is able principle is obtained in Chapter 11 by an elegantto show the smooth transition from the calculus of method. In Chapter 12 two important applicationsvariations to that of optimal control. The transition are given: time optimality of a constant-power jjhighlights the common features of both subjects and rocket and navigation. Chapter 13 generalizes somethus shows the continuity between the classical of the work not included in Chapter 11. Later chap-subject of variational calculus and a major area of its ters deal with such topics as singular systems, theapplication in modern engineering, optimal control, maximum range of rockets, and bang-bang controls

that are time optimal. Nonstandard material in thePart 1, on the calculus of variations, is much shorter final chapters ranges from problems in botany and -

than the second part, and seems intended as a review economics to a taste-optimal decision in choosingof the subject in order to show that optimal control the best Camembert cheese!is a natural extension. It is confined to the simplestproblem -- with fixed end points. The necessary con- The reviewer believes that the highly mathematicalditions of Euler, Weierstrass, and Jacobi are devel- choice of notation will decrease the number ofoped as are the corner conditions for problems with engineers and applied scientists who could mostdiscontinuous slopes. Topics that belong to the benefit from the text. After all, a great deal of thiscalculus of variations in the classical framework, such material has been available in the literature beforeas free end points and transversality conditions, are and has been presented in the standard notation ofdeferred to the second part and are treated within ordinary calculus. The author of the text, whothe context of optimal control. teaches in an engineering department, appears to have

written his book more for an audience composed ofThe chapter on the inverse problem of variational mathematicians than one consisting of engineerscalculus is sketchy and does not include some of the and applied scientists.more interesting and direct approaches that havebecome recently available. The inverse technique L.Y. Baharis used to develop conservation laws in a simpler Department of Mechanical Engineeringmanner than the usual set-theoretic methods. These and Mechanicsresults are also useful in stability considerations and Drexel Universitythus should have been included in this chapter. Philadelphia, PA 19104

Part 11 treats optimal control in detail. Chapter 10covers the preliminary material; the maximum

361

SHORT COURSES

AUGUST losses and equipment costs through vibration analysisand correction will be stressed. Techniques will bereviewed along with examples and case historiesto illustrate their use. Demonstrations of measure-

DESIGN AND ANALYSIS OF ENGINEERING EX ment and analysis equipment will be conductedPERIMENTS during the course. The course will include lecturesDates: August 1-12, 1983 on test equipment selection and use, vibration mea-Place: Ann Arbor, Michigan surement and analysis including the latest informa-Objective: Recent developments in the field of tion on spectral analysis, balancing, alignment, iso-testing, methods for designing experiments, interpre- lation, and damping. Plant predictive maintenance "Atation of test data, and procedures for better utiliza- programs, monitoring equipment and programs, andtion of existing data. Design of experiments with equipment evaluation are topics included. Specificsmall numbers of test pieces and runs with high dis- components and equipment covered in the lecturespersion are emphasized. Obtaining maximum infor- include gears, bearings (fluid film and antifriction),mation from limited data is stressed. shafts, couplings, motors, turbines, engines, pumps,

compressors, fluid drives, gearboxes, and slow-speedContact: Engineering Summer Conferences, 200 paper rolls.Chrysler Center, North Campus, The University ofMichigan, Ann Arbor, MI 48109 - (313) 764-8490. Contact: Dr. Ronald L. Eshleman, Vibration Insti-

tute, 101 W. 55th St., Suite 206, Clarendon Hills, IL60514 - (312) 654-2254.

SIMULATION USING GPSSDates: August 8-12, 1983Place: Ann Arbor, MichiganObjective: This course is designed for persons work- DYNAMIC BALANCING

4 ing in management science, operations research or Dates: August 17-18, 1983analysis, facilities planning, or manufacturing system September 21-22, 1983

desigrn Simulation concepts are illustrated with GPSS October 19-20, 1983* applications, using case studies. Computer workshops November 16-17, 1983

provide participants with hands-on experience in Place: Columbus, Ohio "-ci e rbuilding and using GPSS models. Objective: Balancing experts will contribute a series

of lectures on field balancing and balancing machines.","-

Contact: Engineering Summer Conferences, 200 Subjects include: field balancing methods; single,

Chrysler Center, North Campus, The University of two and multi-plane balancing techniques; balancing

Michigan, Ann Arbor, MI 48109 - (313) 764-8490. tolerances and correction methods. The latest in-placebalancing techniques will be demonstrated and usein the workshops. Balancing machines equipped withmicroprocessor instrumentation will also be demon-

MACHINERY VIBRATION ANALYSIS strated in the workshop sessions. Each student willDates: August 16-19, 1983 be involved in hands-on problem-solving using thePlace: New Orleans, Louisiana various balancing techniques.Dates: November 15-18, 1983Place: Chicago, Illinois Contact: R.E. Ellis, IRD Mechanalysis, Inc., 6150Objective: In this four-day course on practical Huntley Road, Columbus, OH 43229 - (614) 885-machinery vibration analysis, savings in production 5376.

437

:.."....''. -....-... ,..,,.. ... ,..-....,.... ... - .,,

VIBRATION AND SHOCK SURVIVABILITY, SEPTEMBERTESTING, MEASUREMENT, ANALYSIS, ANDCALIBRATIONDates: August 22-26, 1983 12TH ADVANCED NOISE AND VIBRATIONPlace: Santa Barbara, California COURSEDates: October 17-21, 1983 Dates: September 19-23, 1983Place: England Place: Southampton, EnglandDates: October 24-28, 1983 Objective: The course is aimed at researchers andPlace: Boulder, Colorado development engineers in industry and researchDates: November 21-25, 1983 establishments, and people in other spheres who arePlace: Ottawa, Ontario associated with noise and vibration problems. TheDates: November 28 - December 3, 1983 course, which is designed to refresh and cover the

*Place: Cincinnati, Ohio latest theories and techniques, initially deals withDates: December 5-9, 1983 fundamentals and common ground and then offersPlace: Santa Barbara, California a choice of specialist topics. There are over thirtyObjective: Topics to be covered are resonance and lectures, including the basic subjects of acoustics,fragility phenomena, and environmental vibration and random processes, vibration theory, subjective re-shock measurement and analysis; also vibration and sponse and aerodynamic noise, which form theshock environmental testing to prove survivability, central core of the course. In addition, several spe-This course will concentrate upon equipments and cialist applied topics are offered, including aircrafttechniques, rather than upon mathematics and noise, road traffic noise, industrial machinery noise,theory. diesel engine noise, process plant noise, environmen- -

tal noise and planning and laser techniques for non-Contact: Wayne Tustin, 22 East Los Olivos Street, contact measurements.

x Santa Barbara, CA 93105 - (805) 682-7171.Contact: Mrs. Maureen Strickland, ISVR Con-ference Secretary, The University, Southampton S095NH-, England - 0O703) 559122 ext. 231 0/532.

DYNAMICS AND CONTROL OF LARGE FLEX-IBLE STRUCTURESDates: August 22-26, 1983 MODAL TESTING COURSEPlace: Los Angeles, California Dates: September 20-22, 1983Objective: The theme of the course is the need to Place: Washington, D.C.integrate the understanding of physical system dy- Objective: Vibration testing and analysis associatednamics with the methods of modern control theory with machines and structures will be discussed into accomplish the practical control of the class of detail. Practical examples will be given to illustratelarge, flexible structures of current interest. Atten- important concepts. Theory and test philosophy oftion focuses initially on the idealization of space- modal techniques, methods for mobility measure-craft structures and the formulation of their equa- ments, methods for analyzing mobility data, mathe-tions of motion. Dynamics and control theory are matical modeling from mobility data, and applica-then developed in integrated teams, with emphasis tions of modal test results will be presented.gradually shifting to the applications of modern con-

*trol theory. The limitations of conventional optimal Contact: Dr. Ronald L. Eshleman, Vibration Insti-estimation and control theory for such applications tute, 101 W. 55th St., Suite 206, Clarendon Hills, I L

*are illustrated, and various techniques for reducing 60514 - (312) 654-2254.the sensitivity of conventional methods to modelingerrors are presented.

STRUCTURAL DYNAMICS: COMPUTER-ORIENT.Contact. Short Course Program Office, UCLA Ex- ED APPROACH WIT H APPLICATIONStension, P.O. Box 24901, Los Angeles, CA 90024 - Dates: September 26-30, 1983(213) 825-1295 or 825-3344. Place: Los Angles, California

38

Objective: The course emphasizes discrete methods, Objective: This course is des;gned to provide a

numerical methods, and structural modeling for broad, comprehensive introduction to important

computer-oriented solution of various structural topics in underwater acoustics and signal processing.

dynamic problems. Some recent developments in the The primary goal is to give participants a practical

structural dynamic analysis of parametrically excited understanding of fundamental concepts, along with

systems, rotating systems, and systems in which an appreciation of current research and development

fluid-structure dynamic interactions occur are also activities. Included among the topics offered in this

considered. course are: an introduction to acoustics and sonarconcepts, transducers and arrays, and turbulent and

Contact: Short Course Program Office, UCLA Ex- cavitation noise; an extensive overview of sound

tension, P.O. Box 24901, Los Angeles, CA 90024 - propagation modeling and measurement techniques;

(213) 825-1295 or 825-3344. a physical description of the environment factorsaffecting deep and shallow water acoustics; a practical

guide to sonar electronics; and a tutorial review of

OCTOBER analog and digital signal processing techniques and

active echo location developments.

UNDERWATER ACOUSTICS AND SIGNAL PRO- Contact: Alan D. Stuart, Course Chairman, Ap-

CESSING plied Research Laboratory, The Pennsylvania State

Dates: October 3-7, 1983 University, P.O. Box 30, State College, PA 16801 -

Place: State College, Pennsylvania (814) 865-7505.

39

-- .. ,

. .... ..

. . . . . .

77~.w-.---.--.-

ABSTRACTS FROMTHE CURRENT LITERATURE

Copies of publications abstracted are not available from SVIC or the Vibration Institute, except those generatedby either organization. Government Reports (AD-, PB-, or N-numbers) can be obtained from NTIS, Springfield,Virginia 22151; Dissertations (DA-) from University Microfilms, 313 N. Fir St., Ann Arbor, Michigan 48106;U.S. Patents from the Commissioner of Patents, Washington, DC 20231; Chinese publications (CSTA-) in Chinese

or English translation from International Information Service Ltd., P.O. Box 24683, ABD Post Office, HongKong. In all cases the appropriate code number should be cited. All other inquiries should be directed to libraries. -

The address of only the first author is listed in the citation. The list of periodicals scanned is published in issues1, 6, and 12.

ABSTRACT CONTENTS

MECHANICAL SYSTEMS . ... 41 MECHANICAL COMPONENTS. 51 MECHANICAL PROPERTIES. . 71

Rotating Machines ....... 41 Absorbers and Isolators . .. 51 Damping ............. 71Metal Working and Tires and Wheels ........ 54 Fatigue .............. 72

Forming .......... 42 Blades ............... 55 Elasticity and Plasticity . .. 72% ~Bearings .............. 55

Fasteners ............. 56 EXPERIMENTATION ....... 73

STRUCTURAL SYSTEMS .... 42 Valves ............... 56 Measurement and Anaiysis . 73

Brige..........42Dynamic Tests ......... 78 fSTRUCTURAL COMPONENTS. 57 SclnadMoeig 8Buildings ............. 42 Diagnostics ............ 80

Foundations . . . . .. 44 B lnig. . . . . . .8Harbors and Dams Cale.......... Balaonctoing ............. 80Power Plants ................. Bars and Rods .......... 58 Mntrn......8Off-shore Structures... 46 Bem .ANALYSIS AND DESIGN .... 81

Cylinders . . . . . ..59Colmn.........60 Analytical Methods ...... 81

VEHICLE SYSTEMS Frames. an4rhs...6 Modeling Techniques..84Plates ............... 61 Nonlinear Analysis ....... 85Shells ............... 63 Numerical Methods ...... 86

Ground Vehicles ........ 47 Pipes and Tubes ........ 64 PrmtrIetfcto..8Shis 4 Buldig Cmpoent .66 Optimization Techniques . 88Aircaft.. 48Design Techniques.....88

Missiles and Spacecraft. .... 50CoptrPgam...8DYNAMIC ENVIRONMENT. . 67

GENERAL TOPICS ......... 89BIOLOGICAL SYSTEMS..50 Acoustic Excitation .... 67

Shock Excitation ........ 70 Conference Proceedings . .89

Human . .. ....... 50 Vibration Excitation..71 Useful Applications ...... 89

40

--- A

:7. 7--_7

MECH NICA SYS EMSsystem is shown based on the relation between the dissipat iveMECH NICA SYS EMSenergy and the logarithmic decrement. By applying the

method to a rotor-bearing system which is subjected to afluid dynamic destabilizing force, the stability of the systemis evaluated. The effects of the axial location of disk, thestiffness of rotor and the anisotropy of bearing characteristicson the stability of the system are described and the ,mntribu-

ROTATING MACHINES tion of each element to the stability is discussed.

(Also see No. 1494)

83-1279Critical Speeds of Unbalanced Rotors Caused by 83-1281Torque Fluctuation, Bearing Anisotropy and Dead Unbalance Response of a Single Mass Rotor on Fluid

Weight (Biegakritische Drehzalden unwehtiger Ro- Film Bearings Usuug Modal AnalysisStoren ofolge Drehmaomentschwankunen, Lageraniso- R.B. Bhattrope undEigengewieht) Dept. of Mech. Engrg., Concordia Univ., Montreal,Hri and K. e schne Quebec, Canada, Intl. Modal Analysis Conf., Proc. 0-, H. Martins and K. Teschner

-, Fachhochschule Hamburg, Fed. Rep. Germany, 1st, Nov 8-10, 1982, Orlando, FL. Spons. Union30J 13 fg College, Schenectady, NY, pp 649-655, 9 figs, 1

Konstruktion, 5 (1), pp 3-10 (Jan 1983) 7 figs,f" 5 refstable, 11 refs ."5 ref s

,7, (In German)(G aKey Words: Modal analysis, Rotors, Unbalanced mass re-

,,Jm ~sponse, Critical speeds. .1

Key Words: Rotors, Critical speed

Critical speeds and unbalance response in synchronous whirlIn the article, both critical and sub-critical speeds are calcu- of a single mass rotor, supported on hydrodynamic bearingslated for Laval rotors. The subcriticals, obtained by a non- are studied, employing modal analysis. Due to the asymmetrylinear calculation, are defined only by rotor parameters in the cross coupled coefficients in a fluid film bearing, aand occur at whole number intervals of the flexural natural conventional normal mode analysis is not possible and it isfrequency of the rotor. The combination criticals are a necessary to take into account the adjoint system in thecombination of flexural natural frequency of the rotor analysis. The orthogonality relation oetween the modes ofand the torsional frequency. They occur above, as well as, the original system and those of the adjoint system is used tobelow the normal critical speeds, and should be watched; uncouple the system of equations of motion. A discussion " . .e.g., in cases where electric machines are coupled to recipro- of the application of modal analysis to study the dynamics

°" ating engines.-t"nisof rotors is included.

83.1280 83-1282Energetic Evaluation of Stability in Rotor-Bearing Rotor Dynamic Simulation and System IdentificationSystem (Contribution of Each Element to Logarith- Methods for Application to Vacuum Whirl Datamic Decrement) A. Berman, N. Giansante, and W.G. FlannellyM. Kurohashi, T. Iwatsubo, R. Kawai, and T. Fuji- Kaman Aerospace Corp., Bloomfield, CT, Rept. No.kawa R-1496, NASA-CR-159356, 188 pp (Sept 30, 1980)Mech. Engrg. Res. Lab., Kobe Steel, Ltd., 1-Chome, N83-11117Wakinohama-Cho, Chuo-Ku, Kobe, Japan, Bull.

:"" JSME, 26 (212) pp 276-282 (Feb 1983) 11 figs,.•JSM -- 2 ( ) p 6Key Words: Rotors, System identification techniques, Natu-

7 tables, 9 refs ral frequencies, Mode shapes

Key Words: Rotors, Fluid-induced excitation, Stability Methods of using rotor vacuum whirl data to improve theability to model helicopter rotors were developed. The work

A calculation method for the contribution of each element consisted of the formulation of the equations of motion of

(bearing, etc.) to the logarithmic decrement In a rotor-bearing elastic blades on a hub using a Galerkin method; the develop-

41

"S-

: 7 7% . . I . . -. - . .- - .. - . V. . . . . . ,. . . . ._ . . . -. . . . ..-. . . . . . .. . . . . ".. ~~~ .. *: .

ment of a general computer program for simulation of these obtained for the dynamic potential by using the concepts

equations; the study and implementation of a procedure of slender-body theory to define near- and far-field poten-for determining physical parameters based on measured tials which are matched to form the complete solution.data; and the application of a method for computing thenormal modes and natural frequencies based on test data.

METAL WORKING AND FORMING(See Nos. 1452, 1487)

83-1283Toriomnal Owcactions in Constant-Velocity DrivesIncorporating Two Cardan Joints the Present Stateof Knowledge and the Design of an Experanental-Research..........AeCosta STRUCTURAL SYSTEMSDept. of Mech. Engrg., Politecnico di Milano, Italy,Meccanica, 17 (4), pp 179-200 (Dec 1982) 12 figs,4 tables, 24 refs BRIDGES

Key Words: Shafts, Drive shafts, Cardan shafts, Torsionalvibration

The paper reports a survey and a comparison between thee- 83-1285retical predictions (as well as a few experimental findings Multimnore Bridge Response to Wind Excitations"already known) on dynamic stability of torsional oscillations Y.K. Lin and J.N. Yangin two-Cardan-joint constant-velocity drives. The design of Univ. of Illinois, Urbana, IL 61801, ASCE J. Engrg.a special test apparatus is described which can be used ina broad range of testing conditions and can measure and M 19record the oscillatory relative motion of the drive output 18 refsshaft.

Key Words: Bridges, Random vibration, Wind-induced excite-tion

Spectral analysis of random vibration is used to develop anew multimode linear theory for the computation of cross-

831]284 spectra of bridge response to turbulent wind excitations. NewA Nonliear Method for Predicting Unsteady Sheet interpretations are given to previous works in the literature,Cavitation on Marine Propellers and the results compared. The comparison enables a directF. Stern and W.S. Vorus utilization of previously obtained experimental results, asScience Applications, Inc., Ship Hydrodynamics well as clarification of the implication and limitation of

Div., Annapolis, MD, J. Ship Res., 27 (1), pp 56-74 previously proposed simplified procedures.

(Mar 1983) 14 figs, 2 tables, 17 refs

Key Words: Propellers, Marina propellers, Cavitation BUILDINGS

A method is presented which provides a basis for predicting (Also see No. 1364)- the nonlinear dynamic behavior of unsteady propeller sheet* cavitation. The method separates the fluid velocity potential

boundary-value problem Into two parts, static and dynamic,which are solved sequentially in a forward time stepping 83.1286procedure. The static potential problem Is for the cavity Seismic Safety: 10-Story UBC Designed Steel Build-fixed instantaneously relative to the propeller and the pro- a, -

* pallor translating through the nonuniform wake field. This Shih-Sheng Paul Lai. problem can be solved by standard methods, The dynamic National Taiwan Inst. of Tech., Taipei, Taiwan,

potential represents the Instantaneous reaction of the cavity* to the static potential field and thus predicts the cavity's R.O.C., ASCE J. Engrg. Mech., 109 (2), pp 557-575

deformation and motion relative to the blade. A solution is jApr 1983) 16 figs, 4 tables, 28 refs

42

. . ... . . . . .... . .. . . .... . . . . .

Key Words: Buildings, Steel, Multistory buildings, Seismic profiles of tall buildings in the finite strip analysis. Particu-response larly, the model fails to reflect the correct building behavior

whenever the story-shear distortion may be significant. An

In evaluating the seismic safety of a 10-story Uniform Build- attempt is made, therefore, to develop a new set of striping Code-designed steel moment-resisting building, three shape functions that is free of the above shortcoming. A 0major sources of uncertainty have been extensively exam- polynomial series is specially constructed and shown to beined: the representation of earthquake environment; the effective for all building types. Several tall building examplesstructural dynamic properties; and the method of structural are tested and the results clearly exhibit the versatility andanalysis. By combining these uncertainties, the reliability surprisingly high accuracy of the proposed finite strip model, -'.

of local inelastic response conditional on the peak ground in both static and free vibration analyses.acceleration is assessed for the frame. The overall seismicsafety is investigated by introducing the site-specific seismicrisk.

83-1289Comparative Seismic Analyses of a Framed Tube with

83-1287 Localized and General Non-LinearityVibration of Asymmetrical Building-Foundation A.A. Huckelbridge, Jr. and R.M. FerenczSystems Dept. of Civil Engrg., Case Western Reserve Univ., 0T. Balendra, Chan Went Tat, and Seng-Lip Lee Cleveland, OH, Intl. J. Earthquake Engrg. Struc.

Dept. of Civil Engrg., Natl. Univ. of Singapore, Singa- Dynam., 11 (2), pp 167-177 (Mar/Apr 1983) 11

pore, ASCE J. Engrg. Mech., 109 (2), pp 430-449 figs, 14 refs

(Apr 1983) 6 figs, 2 tables, 23 refsKey Words: Framed tube technique, Tubes, Buildings, Multi-

Key Words: Buildings, Interaction: soil-structure, Interac- story buildings, Seismic analysis

tion: structure-foundationThe seismic response of a 30-story framed tube is examined.A description is given of an analysis procedure utilizing a

The ibrtioal ffec casedby n erthqakeon n aym- linear substructure to represent the building superstructure,metrical building foundation system is determined by re-ducing the governing equations of motion to a set of coupled achieving considerable economy in computational effort.

intheg oerning equations invoigonly the nectio n Localized nonlinearity in the form of transient foundationintegro -lifferential equations invo lving o nly the interact ion u lf s i c u e s a r s o s e t r . C m a i o s odisplacements, with the degrees of freedom of the super- uplift is included as a response feature. Comparisons ofstructure being eliminated by the modal analysis technique. substructured to non-substructured analyses for the same

The formulation facilitates to discard the insignificant modes ground motion are made.of the superstructure and, as such, the effort involved in thesolution of the eigenvalue problem required for the modalanalysis is minimal, especially for a particular class of tor-sionally coupled buildings. The influence of the eccentricity,shear wave velocity, and the direction of earthquake on the 83-1290dynamic response of the system is investigated. Probability of Failure from Abnormal Load

B. Ellingwood, E.V. Leyendecker, and J.T.P. Yao"Ctr. for Building Tech., Natl. Bureau of Standards,Washington, D.C. 20234, ASCE J. Struc. Engrg.,

83-1288 109 (4), pp 875-890 (Apr 1983) 8 figs, 2 tables,A Versatile Finite Strip Model for Three-Dimensional 18 refsTall Building AnalysisW. Kanok-Nukulchai, S.-Y. Lee, and P. Karasudhi Key Words: Buildings, Shock resistant design, ExplosionsDiv. of Struc. Engrg. and Construction, Asian Inst.

of Tech., Bangkok, Thailand, Intl. J. Earthquake Abnormal loads, which usually are not considered in struc-~ Engrg. Struc. Dynam., 11 (2), pp 149-166 (Mar/Apr tural design because of their low probability of occurrence,E u1 p(may initiate a catastrophic failure if they occur. A case

1983) 14 figs, 6 tables, 12 refs study shows that the probability of structural failure due to a

gas explosion in a residential compartment may exceedKey Words: Buildings, Finite strip method probabilities associated with unfavorable combinations of

ordinary design loads. Therefore, specific provision in designThis study endeavors to show the inadequacy of thin beam standards to mitigate the effects of abnormal loads appear

elgenfunctions commonly used to represent displacement warranted.

43

............................................

83-1291 Y. Moriwaki, R, Pyke, M. Bastick, and T. UdakaThree.Dimensonl Linear Dynamic Anlysis of Civil Systems, Inc., San Leandro, CA, Rept. No.Buildings with 32-Bit Virtual-Memory Minicom- EPRI-NP-2097, 140 pp (Oct 1981)puters DE82901317 IM. Gattass and J.F. AbelDepartmentte de Engineering Civil, P.U.C., Rio de Key Words: Interaction: soil-structure, Seismic analysis,

Janeiro, R.J. 22453, Brazil, Computers Struc., 17 Computer programs

(1), pp 97-104 (1983) 4 figs, tables, 22 refs A brief assessment of some rational approaches to specifying

input motions within a nonlinear analysis framework isKey Words: Buildings, Dynamic structural analysis, Com- presented. Using a modified STEALTH ID seismic andputer-aided techniques SHAKE computer codes, some points discussed in the

assessment are illustrated.This paper focuses on computer-aided analysis of three-dimensional buildings with 32-bit, virtual-memory minicom-puters. Various floor, inertial, geometry, stiffness, and dis-placement models of three-dimensional buildings are dis- HARBORS AND DAMScussed with respect to implications for computational effi- (Also see No. 1489

ciency. From this discussion a model for three-dimensional

buildings is selected for use with virtual-memory minicom-puters. The use of symbolic manipulation, dynamic allocea- 8'-2tion of memory, and matrix storage and manipulation to 831294achieve computational efficiency are also examined. Exam- On the Possibility of Extracting Power from Reso-pies with computational statistics illustrate the ideas pre- ant Harbour Oscillationssented. V. Cossalter, G. Liberatore, and F. Toffolo

Istituto di Meccanica Applicata alle Macchine, Fa-colta di Ingegneria, Universita di Padova, Meccanica,

FOUNDATIONS 17 (4), pp 222-229 (Dec 1982) 8 figs, 15 refs(Also see Nos. 1299, 1365)

Key Words: Harbors, Water waves, Power plants (facilities)

83-1292 The possibility of extracting wave power using energy-cap-Seimic Response Arising from Traveling Waves turing devices placed inside specially shaped artificial basins,

rather than with offshore free-floating installations, is exam-J.R. Morgan, W.J. Hall, and N.M. Newmark ined. A particular type of basin - rectangular in shape withTexas A&M Univ., College Station, TX, ASCE J. convergent mouth - was selected, where optimization ofStruc. Engrg., 109 (4), pp 1010-1027 (Apr 1983) efficiency in wave energy exploitation is achieved by a

8 figs, 3 tables, 19 refs movable back-wall allowing the resonant frequency of theharbor to be tuned to the variable frequency of incidentwaves. The dynamical behavior of the proposed harbor con-

Key Words: Foundations, Seismic response figuration is first investigated by means of a mathematicalmodel, obtained by a combination of the finite element

Over the years observations of earthquake damage suggest and boundary integral techniques. Experiments are thenthat structures on large foundations respond to ground mo- conducted in a large three-dimensional wave basin in ordertion with less intensity than do smaller structures. The to verify the theoretical results. Both theoretical and experi-limited data obtained from instruments support these obser- mental analyses confirmed the potentiality of the proposedvationS. The theoretical investigation described constitutes solution for the purpose of exploiting wave power from thean attempt to establish the feasibility of employing the sea.7-averaging traveling seismic wave procedures to investigate

the effects of combined lateral motion resulting from transle-tion and rotation of a simple structure.

POWER PLANTS(Also see Nos. 1294,1386,1388)

83-1293Specifications of Input Motions for Seismic Analyses 83-1295of Soil-Structure Systems within a Nonlinear Anal. Non-Linear Rocking Response of Model Containmentyses Framework. Final Report Structures

% -.4

i. ... "" -

D.K. Vaughan and J. Isenberg Combustion Engineering, Inc., Windsor, CT, Intl.Weidlinger Associates, 3000 Sand Hill Rd., Bldg. 4, Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,Suite 245, Menlo Park, CA 94025, Intl. J. Earth- Orlando, FL. Spons. Union College, Schenectady,quake Engrg. Struc. Dynam., 11 (2), pp 275-296 NY, pp 608-613, 3 figs, 3 tables, 3 refs 0(Mar/Apr 1983) 20 figs, 21 refs

Key Words: Modal analysis, Nuclear power plants, Seismic .-..

. Key Words: Containment structures, Nuclear power plants, response

Underground explosions, Interaction: soil-structure, Finitedifference technique A method is presented to simplify the modal and seismic

response analysis of complex control panel cabinets. The

Smell (1/24- to 1/8-size) nuclear containment structures methodology presented here is valid for other types of 9were subjected to ground shaking from buried explosions cabinet assemblies that must be seismically analyzed. Also

a end to oscillating forces. The apparent natural frequency included is a discussion of the modeling techniques used,

* or resonant frequency of rocking varies inversely with ampli- with emphasis on the key modeling assumptions made.

tude of the shaking. An explicit finite difference model ofsoil-structure interaction induced by explosive loading isdescribed. The results indicate that nonlinear rocking re-sponse is primarily a result of debonding-rebonding andcompaction of soil at the soil-structure interface.

83.1298Dynamic Testing and Analysis of Magnetic Fusion

Containment Vessel StructureH.J. Weaver

83.1296 Lawrence Livermore NatI. Lab., Livermore, CA

Modal Analysis of Light Ion Beam Fusion Reactor 94550, Intl. Modal Analysis Conf., Proc. 1st, Nov 8-

Vessis 10, 1982, Orlando, FL. Spons. Union College, Schen-*' R.L. Engelstad and E.G. Lovell ectady, NY, pp 579-585, 10 figs, 2 refs

Univ. of Wisconsin, Madison, WI 53706, Intl. ModalAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orland, Key Words: Nuclear reactors, Containment structures, Modal

FL. Spons. Union College, Schenectady, NY, pp 289- tests, Modal analysis, Seismic design

, 295, 18 figs, 1 table, 2 refs Dynamic (model) testing was performed on the Magnetic

Fusion Test Facility (MFTF) containment vessel. The seismic

* Key Words: Nuclear reactors, Modal analysis, Blast response design of this vessel was heavily dependent upon the value ofstructural damping used in the analysis. The report presents

Light ion beam inertial confinement fusion reaction vessels a description of the test procedure used. It also presents an

are subjected to intense dynamic overpressure and heat flux interpretation of the damping mechanisms observed (material

from nuclear microexplosionL The conceptual design pro- and geometric) based upon the spatial characteristics of the

posed consists of a cylindrical chamber with hemispherical modal parameters (mode shapes).ends. The shell structure is supported by a gridwork of ribs

and stringers. Modal static deflections and stresses for paneland beam components are developed In parametric form.The dependence of modal dynamic load factors upon thepulse shape of the fireball blest wave are identified. Maxi-mum DLF values are determined and characterized as func- 83-12"9tions of flexural frequencies for the various structural coin- Soil-Siructure Interaction Analysis of a 5 kg HDRponents. The dynamic response is determined by coupling Exploive Testthe static results with the appropriate dynamic load factors. CMvKnC.A. Kot, M.G. Srinivasan, D.K. Vaughan, and J..-

Isenberg

Argonne National Lab., Argonne, IL, Rept. No. ANL- -°

82-53, 117 pp (Nov 1982)NUREG/CR-2918

83-1297Modal sad Seismic Reqponse Analysis of Complex Key Words: Interaction: soil-structure. Containment struc-

Control Palle Cabinets tures, Nuclear reactors, Blest response, Computer programs.

T.P. Pastor Dynamic tests

- 45

4

.- .-, .- -.- . -. ....--

This report summarizes a nonlinear 3-0 finite-element, safety monitoring techniques and systems, and survivalsoil-structure interaction analysis of dynamic response techniques and training.to a 5 kg explosive blast test performed on the containmentbuilding of the Heissdampfreaktor in Germany in 1979.The modeling of the explosive source, site, and building foruse in the TRANAL computer code was partially based onInformation obtained from previous tests. Comparison of

* analytical results with the test measurements shows that 83-1302the analysis simulates superstructure response better than True Ice Force by Deconvolutionit does the foundation response. ~M. Mittinen """

Univ. of Oulu, Oulu, Finland, Intl. Modal AnalysisConf., Proc. 1st, Nov 8-10, 1982, Orlando, FL.

Spons. Union College, Schenectady, NY, pp 586-590,7 figs, 5 refs

4.83-1300"-" 310Modal Anay and Radom Vibration Test of a Key Words: Ice, Off-shore structures, Modal tests, Transferfunctions, Finite element technique

NuckarFueA1 blyR.G. Hill and J.F. Patterson Moving ice exerts high static and dynamic loads againstExxon Nuclear Co., Intl. Modal Analysis Conf., fixed offshore structures. To justify design criteria ice force

3 Proc. 1st, Nov 8-10, 1982, Orlando, FL. Spons. in-field measurements are needed. However, it is not possibleUnion College, Schenectady, NY, pp 103-109, 5 to measure ice forces directly. With slender structures the

dynamic response interferes in the measurement signal. Thefigs, 1 ref effects of dynamic response of the structure can be removed

by deconvolution. This paper presents methods in using" Key Words: Nuclear fuel elements, Natural frequencies, transfer functions and deconvolution for analyzing ice" Mode shapes, Finite element technique, Vibration tests force measurement signals from steel lighthouses.

Full scale random vibration tests are performed on a nuclearfuel assembly to determine its vibrational properties for usein verifying analytical models that are subsequently used inearthquake and LOCA (loss-of-coolant accident) vibrationanalse. 83-1303

Feasibility of Structural Integrity Monitoring of Off-shore Platforms Using Vibration AnalysisG. WitteGKSS - Forschungszentrum Geesthacht GmbH,

OFF-SHORE STRUCTURES Geesthacht-Tesperhude, Fed. Rep. Germany, Rept.(Also see No. 1489) No. GKSS-80/E/42, CONF-8009228-1, 11 pp (1980)

(Intl. Congress on Marine Research and Marine Tech.

(Intermaritec '80), Hamburg, Fed. Rep. Germany,Sept 24, 1980)D E82902158

83-1301 (In German)

Offshore Structures. 1974 -December, 1982 (Cita-" tions from Oceanic Absracts) Key Words: Monitoring techniques, Signature analysis,

:NTIS, Springfield, VA, 212 pp (Dec 1982) Off-shore structures, Drilling platforms' "f V

PB83-855635 The feasibility of strength monitoring of offshore platformsby analyzing their vibration behavior has been investigated.

Key Words: Off-shore structures, Fatigue tests, Bibliographies This so called signature analysis is a new tool for earlyfault detection and for the near future it can be expected

This bibliography contains 264 citations concerning safety that this method will partially substitute conventional, considerations and disester prevention for offshore struc- Inspection techniques; e.g., the visual checking of structures

tures. Citations include studies of the dynamic behavior of by divers. Some fundamental aspects of structural failuresthe structures, fatigue and failure analyses, structural and and their origin are presented.

46

*J 46

- . .4 . . .. .

VEHICLE SYSTEMS 834306

The Effect of Two Point Contact on the CurvingBehavior of Railroad VehiclesJ.A. Elkins and H. WeinstockThe Analytic Sciences Corp., Reading, MA, ASMEPaper No. 82-WA/DSC- 13

GROUND VEHICLES(Also see Nos. 1339, 1412, 1418) Key Words: Interaction: rail-wheel

This paper describes recent improvements in the predictionof wheel/rail forces. These improvements are associated with

83-1304 the analytic modeling of the two point contact conditionsDigital Modal Analysis Applied to Steering Wheel that exist with the standard wheel and rail profiles in com-Vibrationt mon use in the U.S.

L. Enochson and D. GalyardtTime Series Associates, Spokane, WA, Intl. ModalAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,FL. Spons. Union College, Schenectady, NY, pp 566-572, 13 figs, 2 tables 83-1307

Modal Characterization of a 70-Ton Railroad BoxcarKey Words: Automobiles, Steering gear, Modal tests, Modal Using a Vibration Test Unitanalysis F.D. Irani and N.G. Wilson

Boeing Services International, Inc., Intl. Modal Anal- -

An automobile with high performance suspension, wheels ysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL.and tires installed experienced moderate to severe steering Spans Union College, Schenectady, NY, pp 72-81wheel shake at road speeds of 55, 65 and 90 mph. Modaltesting and structural modification analyses were performed 13 figs, 6 tables, 4 refsusing a mini-computer based spectral analyzer. The resultsof these test and analyses indicated that both the frame Key Words: Railroad cars, Box cars, Vibration tests, Testcrosamember, onto which the steering rack wAs bolted, fecilitiesand the transmission mount bracket required stiffening.Installation of stiffened components on the automobile A Vibration Test Unit (VTU) which is designed for dynamicsignificantly alleviated steering wheel shake, testing of rail vehicles is described. The facility is capable

of inputting periodic, as well as random waveforms andtrack geometry time histories, to excite a test object. Thetest unit is controlled and can operate each of its 12 actua-tors, 8 verticals, one for each wheel, and 4 laterals, one foreach axle, simultaneously. Since it is capable of indepen-

83-1305 dently controlling any of the actuators with relative timeDynamic Problems in Vehicle Transmuission Design and phase delays the VTU is able to excite a test object inD. Barbiero, A. Garro, and V. Vullo the vertical, lateral, torsional, roll, pitch and yaw modes.FIAT Auto S.p.A. - Direzione Tecnica - Sviluppo This paper presents the details of a modal test and analysis

and the results of this investigation. A 70-ton railroad boxcarProgetti, Intl. Modal Analysis Conf., Proc. 1 st, Nov 8- was tested in two different truck suspension configurations,10, 1982, Orlando, FL. Spans. Union College, Schen- with and without friction snubbers.ectady, NY, pp 278-288, 17 figs, 10 refs

Key Words: Power transmission systems, Automotive trans-missions, Drive line vibration, Flexural vibration, Modalanalysis

83-1308The dynamic problems of motion transmission from gear- Railroad Vehicle Dynamic Testing Capability andbox to wheels due to the modal shapes of vibration of the Suesssystem, when they come within ranges of excitation of the Wnengine, cardanic joints, transmission, centrifugal force, Ptc.,are examined. The analysis is carried out with discretization Boeing International Inc., Pueblo, CO, ASME Papermethods and modal analysis. No. 82-WA/RT-9

47

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Key Words: Railroad trains, Dynamic tests, Vibration tests, in terms of one-third-octave bend spectra and in terms ofTet facilities EPNL units. The 747 experimental results are compared

with previous results for a turbojet-powered T-38 airplaneThis paper describes the capability of the Rail Dynamics and with the SAE recommended empirical lateral attenuationLaboratory at the DOT Test Center, in Pueblo, Colorado prediction procedure. Theoretical predictions are comparedto perform roll dynamics and low frequency vibration test- with the 747 and T-38 results. Good agreement was founding of railroad vehicles, describes performed testing and between the predictions and measured results.its results, and describes application of laboratory capabilityto nonrailroad vehicle test articles.

83-1311SHIPSAircraft Dynamic Response to Damaged and Re-

(See No. 1334) aired Runways

AGARD, Neuilly-sur-Seine, France, Rept. No.AGARD-CP-326, 227 pp (Aug 1982)

AICR FTAD-A122 061r, AIRCRAFT --S(Also see No. 1412) Key Words: Aircraft response, Runway roughness

During 1981 and 1982 the AGARD Structures and Materials83-1309 Panel held two technical meetings on "Aircraft Dynamic

Response to Damaged and Repaired Runways." The 1981

Flight Effects of Fan Noise meeting focused on the environment of damaged airfields,D. Chestnutt while the 1982 Specialists' Meeting focused on aircraft dy-NASA Langley Res. Ctr., Hampton, VA, Rept. No. namic response. The meetings had two main goals: to review

L-15493, NASA-CP-2242, 128 pp (Sept 1982) the programs and methods within the AGARD countries(Presented at the Workshop on Res. on the Simula- for dynamic analysis and testing of taxiing aircraft, and to

encourage the exchange of information on aircraft dynamicresponse, thereby improving the interoperability of NATO

ton, VA, Jan 26-27, 1982) military aircraft. The publication consists of the papersN83-10883 presented at these meetings.

Key Words: Aircraft noise, Fan noise, Flight simulation

Simulation of inflight fan noise and flight effects was dis-cussed. The status of the overall program on the flight ef- 83.1312fects of fan noise was reviewed, and flight to static noisecomparisons with the JT1 5D engine were displayed. Investigation of Landing Gear Alternatives for High

Performance AircraftA.R. DeWispelare and R.P. StagerAir Force Inst. of Tech., Wright-Patterson AFB, OH,J. Aircraft, 20 (4), pp 319-326 (Apr 1983) 14 figs,

83-1310 6 tables, 9 refsGround Effects on Aircraft Noise for a Wide-BodyCommiercial Airplane Key Words: Aircraft, Landing gear, Runwvay roughness

W.L. Willshire, Jr.NASA Langley Res. Ctr., Hampton, VA, J. Aircraft, In an effort to improve rough field performance for a specific

high performance aircraft, the modeling of runway profiles,20 (4), pp 345-349 (Apr 1983) 9 figs, 10 refs the aircraft structure, landing gears, and aerodynamics was

accomplished. Various load alleviation schemes are modeledKey Words: Aircraft noise and then combined with the aforementioned runway and

aircraft models into a dynamic simulation which allows theA flight experiment was conducted to Investigate ground evaluation of the control schemes through numeric andeffects on noise from an airplane with a high-bypeas-ratio graphical means. These combined evaluation tools (numericengine. A Boeing 747 was flown at altitudes of 30-960 m and graphic) add efficiency to the design process along withpast a 20 microphone array. Ground effects are calculated increasing physical insight into the problem.

48

S,.........-. -. .. ,...-.-.. . . . ... ... . . . ... .v-.

-. . . . -, o ,. , . -. ...., . - . .. . . .. - _ .. . . .- .- -. ---- . -., .- .. - . ..' ? , ' . .. . ,

-..

83-1313 G.D. Carbon, D.L. Brown, and R.J. AllemangDual Input Estimation of Frequency Response Func- Boeing Commercial Airplane Co., Seattle, Washing-tions for Experimental Modal Analysis of Aircraft ton 98024, Intl. Modal Analysis Conf., Proc. 1st,Structures Nov 8-10, 1982, Orlando, FL. Spons. Union College,R.J. Allemang, R.W. Rost, and D.L. Brown Schenectady, NY, pp 559-565, 7 figs, 6 refsUniv. of Cincinnati, Cincinnati, OH 45221, Intl.Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982, Key Words: Aircraft, Modal tests, Vibration tests, Testing . -

Orlando, FL. Spons. Union College, Schenectady, techniques, Flutter

NY, pp 333-340, 9 figs, 9 refs This paper describes a new multi-exciter ground vibrationtesting system and procedure used for testing large commer-

Key Words: Aircraft, Frequency response function, Modal cial aircraft. The testing method uses uncorrelated multi-analysis input random excitation with an extensive digita! data

acquisition system to significantly reduce the testing timeThe accurate measurement of the frequency response func- and at the same time improve the quality of the modaltion is vital to the estimation of the system modal param- data base.sters, The use of the single input/output theory to formulatethe equations for the frequency response function can bereplaced by an equivalent theory involving multiple inputs.The results of this approach provide frequency responsefunctions that are comparable to the single input/output 83-1316case but with a reduction in the time required per measure- A Multiple Sine Excitation Approach to Groundment and an increase in the consistency of modal frequency '4%

and damping values estimated from different frequency re-sponse functions Examples are included for representative C.E. Brickeyaircraft structures. McDonnell Aircraft Co., P.O. Box 516, St. Louis,

MO 63166, Intl. Modal Analysis Conf., Proc. 1st,Nov 8-10, 1982, Orlando, FL. Spons. Union College,

Schenectady, NY, pp 82-87, 10 figs83-1314Getting the Most Out of Commercial Modal Systems Key Words: Aircraft, Vibration tests, Testing techniques,R.G. Smiley Sine mask technique

Entek Scientific Corp., Cincinnati, OH, Intl. Modal The ground vibration test technique utilized on full-scaleAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, aircraft for many years at McDonnell Aircraft CompanyF L. Spons. Union College, Schenectady, NY, pp 341- had been that of swept sine and dwell using multiple vibra-

347, 8 figs tion exciters. With the advent of real time analyzers, usingthe fast Fourier transform, a new testing technique needed

Key Words: Modal analysis, Measuring instruments to be developed which could take advantage of the newpotential offered by these data systems. The technique devel-oped combined the proven advantages of swept sine testing

This paper reviews some of the characteristics of "canned" ith the random data approach required by real time ena-modal analysis systems and presents some simple techniques

lyzers, The approach, described here and termed "sinethat can be used to greatly enhance the capabilities of (anid mak"ivleusnasresosneiglswchtruhincrease confidence in) their use. Examples include illustra- mask:' Involves using a series of sine signals which, through

proper combining, create a high energy narrow band signaltions of problems encountered due to the lack of rotational capable of exciting the test structure at up to six modal

degrees-of-freedom capabilities and ways to avoid these prob. feunisa n ie h irto nrdcdit hfrequencies at one time. The vibration introduced into the -..lenis; computation of Joint and boundary conditions fromsiple; expemntaon dajont, ndibng onnec tionts wrem test structure can be controlled better since multiple exciterssimple experimental dat, including connection points where are utilized.no data exists; a strategy for designing products to makethem more amenable to analysis; and some reasons for thedifficulties encountered In predictive analysis,

83-1317Digital Modal Analysis of a Full Scale Twin Engine

83-1315 AircraftApplication of Dual Input Excitation Techniques L. Enochson and R.L. Howesto the Modal Testing of Comunercial Aircraft Time Series Assoc., Spokane, WA, Intl. Modal Analy-

-- 4.

49

" , -~......... .......- . . ........ . .. , .. ,. ... .. ....•,- .•.•. .,--. ,..

* . --~. -,-. -

sis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL. modal testing were employed: normal mode testing using

Spans. Union College, Schenectady, NY, pp 95-101, multi-point swept sine wave excitation, and transfer function5 figs, 1 table, 6 refs testing using single point broad-bond random excitation.

Key Words: Aircraft, Vibration tests, Random excitation,Impact tests

A ground vibration test on a twin engine aircraft is described. 83-1320Single point random and impact excitation were used. The Dvoseto etDne tanMdlMdldatae ws acquired and analyzed using a high-speed mini-. f Development of Test-Derived Strain Modal Models

computer. Results were extracted using complex exponential for Structural Fatigue Certification of te Spaceand least squares circle fit algorithms. Shuttle Orbiter

J.W. Young and J. JoanidesStructural Dynamics Res. Corp., San Diego, CA, Intl.Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,Orlando, FL. Spons. Union College, Schenectady,

83-1318 NY, pp 479-487, 6 figs, 14 refsTrmaqort Aircraft Crad DynamicsG. Wittlin, M.A. Gamon, and D. Shycoff Key Words: Spacecraft, Space shuttles, Fatigue life, ModalLockheed-California Co., Burbank, CA, Rept. No. tests, Frequency response function

NASA-CR-1 65851, 470 pp (Mar 1982) A method of predicting strain using a modal model derived

from test data is presented. A modal test is performed, andKey Words: Crash research (aircraft), Aircraft frequency response functions are collected from accelerom-

eters and strain gages. A combined modal model is extractedA review and evaluation of transport airplane accident data in which the eigenvectors included both displacement andfor the 1964 - 1979 period is presented. Included in the strain mode shape coefficients. An example application ofresults are formulation of candidate crash scenarios, the such test-derived strain modal models to the fatigue evalue-identification of the involvement of structural systems and tion of the space shuttle orbiter is presented.

subsystems in transport airplane accidents, a review of exist-Ing design criteria and philosophy, and conclusions andrecommendations for future R&D effort.

BIOLOGICAL SYSTEMSMISSILES AND SPACECRAFT

(Also see Nos. 1347,1363,1378)

HUMAN

83-1319Exp(iiental Modal Analysis of the Titan 34D/IUS 83.1.21Payload FairingA.G. Ripple and J.R. Janczy Sleep Disturbance Before and After Traffic Noiae

Martin Marietta Corp., Denver, CO, Intl. Modal Atteuation in an Apartment Building

Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, E. Ohrstrom and M. Bjorkman

FL. Spons. Union College, Schenectady, NY, pp 410: Dept. of Environmental Hygiene, Univ. of Gothen-

416,15 figs, 10 tables burg, Box 33031, S-400 33 Gothenburg, Sweden,J. Acoust. Soc. Amer., 73 (3), pp 877-879 (Mar

Key Words: Spacecraft, Modal analysis, Modal tests, Swept 1983) 1 table, 10 refs

sine wave excitation, Transfer functions, Random excitationKey Words: Traffic noise, Human response, Noise reduction

A modal survey test of the Titan 34D/IUS Payload FairingIPLF) was conducted to characterize the PLF dynamic prop- A study on traffic noise sleep disturbance was made in anertles and to use the resuts to verfy/modify the PLF dynam- apartment building before and after the installation ofIc model to be used in payload load studies. Two methods of noise insulating windows. Three tenants completed a quet-

so- .. . ..-

- . • .- . .

". .. ;"". ", . :'., :' -' . -- . .:; -. -';:;.'- ;- :.. . -. .' ._.; .;' .' . .

-- ~~~ -. . . . .

tionnire each morning one week before and one week after Vibration absorption of bridge cranes by means of hydraulic

the insulation of windows, and body movements during sleep absorbers is investigated. Hydraulic vibration absorbers are

were recorded during these periods. The results suggest that mounted on both of the main girders of the crane symmetri-

subjectively judged sleep quality as well as recordings of bed cally to the axis of the crane. By means of this procedure

movements are useful tools for evaluating actions to reduce vibration is reduced by about 25-30%.noise.

83-1324

MECHANICAL COMPONENTS Somie Aspects of the Design of a Frictionaly DampedAbsorber

L.J. Wilkins and S.W.E. EarlesCity Univ., London, UK, Dynamic Vibration Isola-

tion and Absorption Conf., Sept 8, 1982, Univ.ABSORBERS AND ISOLATORS of Southampton. Spons. Chartered Mechanical

Engineer, Instn. of Mech. Engineers, pp 31-43, 12

figs, 10 refs

83-1322Experimental-Theoretical Study of Active Vibration Key Words: Vibration absorption (equipment), Coulomb

friction

ControlW.L. Hallauer, Jr., G.R. Skidmore, and L.C. Mesquita The principle of the undamped vibration absorber is well

Virginia Polytechnic Inst. and State Univ., Blacks- established and the theory of such an absorber has beenburg, VA 24061. Intl. Modal Analysis Conf., Proc. extended to damped systems to demonstrate the resulting

8 1benefits of reduced vibration levels over a wider frequencyrange. Damping may be achieved In an absorber by the

College, Schenectady, NY, pp 39-45, 10 figs, 20 refs introduction of interfaces at which energy may be dissipated

by small relative displacement between mating pas. It isKey Words: Active vibration control, Beams, Suspended this slip damping which forms the subject of this paper.

structures

The objectives of this research are design and execution ofexperiments in active vibration control, and quantitative

comparison of experimental measurements of control system 83-1325performance with theoretical predictions. This paper is a How to Select Isolators for a Long Service Lifereport of the initial results. The structure analyzed experi-

mentally and theoretically was a beam suspended by cables R. Raccain tension. The paper presents experimental results and Barry Controls, Barry Wright Corp., Watertown, MA,corresponding theoretical predictions. Des. News, 38 (1), pp 43-46, 48 (Jain 4, 1982) 6 figs

Key Words: Isolators, Shock isolaton, Vibration Isolators

The factors to be considered in the selection of elastomersare discussed. They are: product application; personnel and

83-1323 equipment protection; sources of vibration, shock and noise,

Vibration Absorption of Bridge Cranes During Load as well as smaller environmental effects; recommendedPick Uip (Schwhsgisnudslpfug an Briickenkraen spring rate and frequency of the support structure; type ofheins Hub mi Laifulah ) loading; type of elastomer; internal heat buildup in the

elastomer under resonant conditions; and stress and strainD.N. Spizyna and W. B. Bulanow on the mount.Hebezeuge und Fordermittel, 22 (12), pp 360-363(1982) 4figs, 7 refs(In German)

Key Words: Cranes (hoists), Vibration absorption (equip- 83-1326ment) Vibration Isolation Mounts

,:51

°.., .... . .

R.L. Marinello, editor 83,1329Plant Engrg., 37 (4), pp 36-40 (Feb 17, 1983) 8 figs Vibration Isolation of Pulverising Mills

D. Malam, J.P. Newell, and G.P. RobertsKey Words: Vibration isolation, Mountings Atkins Res. and Dev., Epsom, UK, Dynamic Vibra- .

tion Isolation and Absorption Conf., Sept 8, 1982,Some of the more common methods used to control vibra- Univ. of Southampton. Spons. Chartered Mechanicaltion in industrial plants are reviewed. They represent a wide Engineer, lnstn. of Mech. Engineers, pp 135-147,variety of mounts and materials that have been developedto solve specific problems. 8 figs

Key Words: Vibration isolation, Isolators, Industrial facilities

This paper describes the analysis and evaluation of isolationsystems for pulverizing mills by measurement and analysis of

83-1327 vibration response and by the use of a rigid body mathemati-Effective Isolation is Answer to Shock, Vibration cal model with six degrees of freedom. Methods for analyzing

Questions and modeling the rocking response of the system due toC. Gilbert and H. LeKuch random excitation using spectral techniques, are outlined. .A er abs. Inc The model has shown good correlation with the measured

vibration response, and given a better understanding of theDev., 25 (2), pp 172-175 (Feb 1983) 3 figs dynamic forcing, damping of the mounting system, inertia

block shape and t' effectiveness of different spring mount-

Key Words: Shock isolators ings.

The authors briefly introduce the fundamentals of shockvibration and discuss typical vibration isolators, such aselastomers, wire rope, and cable isolators. They also con-sider the effects of temperature, drift, and creep, as well asthe most desirable and important characteristics an isolator 83-1330should have to perform well in severe service conditions. Tesing and Analysis of Complex Non.Modal Axial

ElementsH.D. Sigel and G.C. PardoenNewport Corp., Fountain Valley, CA, Intl. ModalAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,83.1 328 FL. Spons. Union College, Schenectady, NY, pp

Vibration Isolation in the Low and High Frequency 53-58, 11 figs, 8 refsRangeG.R. Tomlinson Key Words: Vibration isolation, Testing techniques, TransferManchester Univ., UK, Dynamic Vibration Isolation functions, Frequency-dependent parameters

and Absorption Conf., Sept 8, 1982, Univ. of South-ampton. Spons. Chartered Mechanical Engineer, The application of the classical differential equations of

Instn. of Mech. Engineers, pp 21-29, 7 figs, 1 table, motion for a rigid body was found to be unsatisfactory infdetermining accurate natural frequencies and mode shapes

4 refs for a structure supported by one or more complex isolationelements. The transfer functions of the element were found

Key Words: Vibration isolation, High frequencies, Low fre- to have frequency dependent stiffness and damping as well -.-

- quencies, Springs, Metals as varying as a function of the isolators pre-loed. Hence, amethod of generating an element model experimentally

An experimental investigation of the high and low frequency was needed in order to obtain an accurate systems analysis.vibration transmission properties of metal springs is made. A general testing technique is presented which allows accu-Several unusual phenomena are observed and It Is shown rate determination of the element's transfer function underthat recourse to classical theory for longitudinal wave trans- any arbitrary pre-load. The testing technique involves con-mission does not account for these phenomena. The theo- straining one end of the axial isolator and measuring theratical approach used employs the four-pole parameter meth- force developed at this point when a displacement (impact,od and It is shown that this Is not sufficient for accurate sine or random) is applied at the free end of the element.representation of the transmission behavior of helical springL The experimental transfer function data is acquired withIf the tranwerse properties of the springs are considered, a commercially available hydraulic shaker systems and digitalsatisfactory explanation of the phenomena Is possible. fourier analyzers.

52 .

. ., . ... . .. .. . ......... .. m.amm .....--.-- L

83-133] difficulty of handling blocks of concrete and the permanence

Random Vibration Isolation of Instrumentation of it, there can be problems in precisely tuning such a system.During Installation (Schwmungm ,lierung von Ger- For these reasons it was decided to investigate the use of a

fluid as the absorber mass, which would be supported on anaten hei zufil~enl Schwigungen am A ufstellunaort) air spring. The paper reviews earlier work in this area and

H. Tersch outlines the theoretical and experimental development of a

TH Ilmenau, Sektion Geratetechnik, German Dem. model absorber, particularly emphasizing the problem of

Rep., Feingeratetechnik, 32 (1), pp 27-28 (1983) estimating the absorber damping coefficent.

3 figs, 2 refs(In German)

Key Words: Vibration isolation, Foundations, Instrumenta-

tion, Random excitation 83-1334A Damped Vibration Absorber to Reduce Ship Hull

Equations for the calculation of the relationship between Vibrationrandom excitation and the vibration of instrumentation, G. Long and P.A. Farrellespecially precision instrumentation, are presented. Aeronautical Research Labs., Melbourne, Australia,

Dynamic Vibration Isolation and Absorption Conf.,Sept 8, 1982, Univ. of Southampton. Spons. Char- . -

tered Mechanical Engineer, Instn. of Mech. Engi- . -

83.1332 neers, pp 43-57, 11 figs, 3 refs

Nonlinear Models for Mechanical Seismic SnubbersD.P. Reddy and M.S. Agbabian Key Words: Dynamic vibration absorption (equipment),

Vibration absorption (equipment), Ship hulls, DampedAgbabian Associates, El Segundo, CA, ASME Paper structuresNo. 82-WA/PVP-3

A damped vibration absorber of mass 10 ton has been in-

Key Words: Snubbers, Seismic design, Piping systems stalled in a number of landing craft operated by the RoyalAustralian Navy. These ships have blunt blows and experi-

This paper describes the development of a detailed snubber ence very severe hull vibration, primarily in the two-node

process model. The responses of these nonlinear models are vertical mode, when operated in heavy seas. The vibration

compared with the available test data in the form of Lissajous absorber has increased the damping in the ship and effec-

patterns and dynamic time histories showing good agreement tively reduced the levels of vibration. The paper describes

between model and experiment. Simplified models are then briefly the absorber design and installation.

developed from the nonlinear models for use in the mathe-matical analyses of piping systems.

83-1335Dynamic Vibration Absorber Applications in Indu .

83-1333 trial Noise ControlA Fluid Dynamic Vibration Absorber P.M. WilsonJ.B. Hunt and A.J. McGill Lucas Industries Ltd., UK, Dynamic VibrationUniv. of Southampton, UK, Dynamic Vibration Isolation and Absorption Conf., Sept 8, 1982, Univ.Isolation and Absorption Conf., Sept 8, 1982, Univ. of Southampton. Spons. Chartered Mechanical Engi-of Southampton. Spons. Chartered Mechanical Engi- neer, Instn. of Mech. Engineers, pp 81-85, 5 figs, 3

neer, Instn. of Mech. Engineers, pp 109-124, 12 figs, refs

1 table, 10 refs

Key Words: Vibration absorption (equipment), Dynamic

Key Words: Vibration absorption (materials), Low frequen- vibration absorption (equipment), Noise reduction, Vibra-

cies, Fluids, Dynamic vibration absorption (equipment) tion control, Case histories

The absorption of large amounts of energy at low frequencies Industrial applications of dynamic vibration absorbers,

by the use of an auxiliary mass-spr.. . vstem necessitates the particularly with respect to retrospective noise and vibration

use of large masses and soft springs. Apart from the physical control are very scarce. This paper outlines two practical

53

6..

applications that have been successfully implemented. It is well separated natural frequencies. The design criterion is toconcluded that, although usually overlooked in some cases, reduce amplitudes of steady-state vibration at excitation fre-dynamic vibration absorbers can provide an effective retro- quencies in the vicinity of one resonance (probably, but notspective noise control technique with advantages over more necessarily, the fundamental) with the proviso that the othertraditional noise control measures such as enclosures. These resonances lie outside the range of excitation frequencies. Oadvantages include access, maintenance, cost and engineering The absorber, which consists of a damped single degree-of-elegance, freedom system, should be attached to the main system,

where its amplitude is a maximum (or reasonably large ifthe position of maximum amplitude is inaccessible). Themass of the absorber should be as large as practical circum-

stances permit. With the introduction of the absorber thereare two resonant peaks in the vicinity of the original reso- .5nance and it is required to minimize both these peaks.

83-1336Performance of a Non-Linear Vibration Absorber

"" Attached to a Multi-Degree of Freedom SystemJ.B. Hunt and K.G. LeaUniv. of Southampton, UK, Dynamic Vibration TIRES AND WHEELSIsolation and Absorption Conf., Sept 8, 1982, Univ. (Also see No. 1346)

of Southampton. Spons. Chartered Mechanical Engi-neer, Instn. of Mech. Engineers, pp 125-134, 10 figs,9 refs

83-1338Key Words: Vibration absorption (equipment), Multidegree Wheel Tread Profile as a Rail Vehicle Design Param-of freedom systems eter

It is shown that when an absorber is attached to a multi- N.K. Cooperrider and J.L. Wirthdegree-of-freedom system the suppression band can be Arizona State Univ., Tempe, AZ, ASME Paper No.increased considerably depending on the tuning of the 82-WA/DSC-3absorber relative to the resonant frequencies of the mainsystem. If the absorber is tuned below the dominant mode, Key Words: Wheels, Railway wheels, Suspension systemsa non-linear softening spring absorber will increase the sup- (vehicleslpression band, and for an absorber tuned above the dominantmode a softening spring absorber is less beneficial than a The dynamic performance of vehicles with low, moderate,linear absorber. and high conicity wheel profiles is reported. Design charts

for stability and curving are utilized to find optimum primarysuspension values to accompany each wheel profile.

83-1337A Design Procedure for AbsorbersGB. Warburton 83-1339Univ. of Nottingham, UK, Dynamic Vibration Isola- Comparative Performance Analysis of Conventionaltion and Absorption Conf., Sept 8, 1982, Univ. of and Damper Coupled WheelsetsSouthampton. Spons. Chartered Mechanical Engineer, R.V. Dukkipati, B.M. Bahgat, and M.O.M. OsmanInstn. of Mech. Engineers, pp 59-70, 4 figs, 3 tables, National Res. Council of Canada, Ottawa, Canada,7 ref s ASM E Paper No. 82-WAIRT- 13

Key Words: Absorbers (equipment), Vibration absorption Key Words: Wheelsets, Railway wheels, Stability(equipment), Design techniques

The dynamic instability of a railway wheelset is caused byWhen excitation causes large dynamic magnification factors the comhined action of the conicity of the wheels and theIn a system, the addition of a properly designed and located creep forces acting between the wheels and rails. In thisabsorber will produce significant reductions. The procedure paper, the instability is investigated for both the conven-Is applicable to systems which are lightly damped and have tional wheelset and the damper coupled wheelset.

54(>,. -'.- '-' . . . . . . . . . . . . . . . . . . .- - . - - -. -. -. - -- -- - - - - - - - - - - - -. 2 ~ ~ .-- ~~ .. - "..

BLADES Carnegie-Mellon Univ., Pittsburgh, PA, J. Aircraft,(Also see No. 1370) 20 (4), pp 372-376 (Apr 1983) 11 figs, 12 refs

Key Words: Gas turbines, Blades, Flutter, Coulomb friction83-1340A83 4 d pi IThis paper investigates the feasibility of using blade-to-

ground friction dampers to stabilize flutter in blades. The

Blade Damping response of an equivalent one mode model in which the

R.J. Dominic, P.A. Graf, and B.B. Raju aerodynamic force is represented as negative viscous damp-Res. Inst., Dayton Univ., OH, Rept. No. UDR-TR- ing is examined to investigate the following issues: the range

82-39, AFOSR-TR-82-0911, 57 pp (Aug 1982) of amplitudes over which friction damping can stabilizeAD-A 120 470 the response, the maximum negative aerodynamic damping

that can be stabilized in such a manner, the effect of simul-taneous resonant excitation on these stability limits, and the

Key Words: Blades, Tuoine blades, Friction damping determination of those damper parameters which will bethe best for flutter control.

Simulated blade to disk damping of a model turbine bladewas evaluated, both experimentally and analytically. Experi-mental work was performed with a unique apparatus thatintroduced friction damping at the blade platform. Analyti- 83.1343cal work was performed with a computer program based onthe lumped mass theoretical analysis developed by Muszyn- Shock Waves Ahead of a Fan with Nonuniform.ska and Jones. A test was performed also to evaluate the Bladescoefficient of friction at the test setup conditions. A.M. Cargill

Leeds Univ., Leeds, UK, AIAA J., 21 (4), pp 572-578(Apr 1983) 7 figs, 15 refs

83-1341 Key Words: Blades, Fan blades, Shock wave propagation

Turbofan Engine Blade Pressure and Acoustic Radi-atort at Simulated Forward Speed When a fan operates at supersonic tip speeds, shock waves are

generated ahead of the blades. If these blades are nonuni-J.S. Preisser, J.A. Schoenster, R.A. Golub, and C. form, then the shock waves are also nonuniform, and tones - -

Home at harmonics of the fan rotational frequency are generated.

NASA Langley Res. Ctr., Hampton, VA, J. Aircraft, This paper presents a simple theory for the relation between

20 (4), pp 289-297 (Apr 1983), 21 figs, 12 refs the strengths of the individual shock waves, the blade staggerangles and the blade thicknesses, when the shock wave isdetached from the blade leading edge. The results of the

Key Words: Blades, Fan blades, Turbofan engines, Sound theory are in good agreement with experiments and sopropagation provide a theoretical basis for the blade shuffling procedures

used to minimize blade-to.blade variations and to controlTests were conducted on a JT15-1 turbofan engine both shaft order tone generation by these variationsstatically and at simulated forward speed in the Ames 12x24m wind tunnel. Both for-field acoustic data and unsteadypressure data from transducers mounted on the fan bladeswere acquired. Results s a sound power reduction of -EA I'-about 10 dB in the fr-field acoustic levels with simulated BEARINGSforward speed over that measred without forward sed. (Also see No. 1459)

Blede-mounted transducer rt " s showed rotor-turbulenceinteraction dominated the nc field at very low Wspds

while an Interaction between the rotor and internal struts 83-1344dominated at higher s. Displacement Path of a Dynamically Loaded lin

Radial Bearing (Verlagerungsbahn eines dynaniachbelauteten Radialgcitlagers)I. Teipel and A. Waterstraat

83-1342 Institut f. Mechanik der Universit~t Hannover, Fed.

Frietion Damping of Flutter in Gas Turbine Engine Rep. Germany, Konstruktion, 5 (1), pp 11-15 (JanAirfoils 1983) 9 figs, 12, -fsA. Sinha and J.H. Griffin (In German)

55

Key Words: Bearings, Radial bearings, Plain bearings, Force Environmental Test and Integration Branch, Engrg.coefficients Services Div., NASA Goddard Space Flight Ctr.,

Intl. Modal Analysis Conf., Proc. 1st, Nov 8-10,The dynamic force equilibrium required for the calculationof deflection is presented. Thusa new parameter Is obtained, 1982, Orlando, FL, Spons. Union College, Schen- which Includes the masses of the moving bearing portions. ectady, NY, pp 390-395, 12 figs, 6 refsIn addition, the deviations from an isothermal case aretested. A satisfactory agreement between the celculated and Key Words: Bolts, Spacecraft, Shuttles (spacecraft), Vibra-measured data is obtained. tion tests

During the prototype vibration tests of the GAS adapterbeam, significant impacting of the beam at its support pointswas observed. The cause of the impacting was traced to gaps

83-145 under the mounting bolt heads. Because of the nonlinear

ROller Bearings With Long~elr if e nature of the response, it was difficult to evaluate the effects

which Shuttle launch dynamics might have on the mountingW.L. Bowen bolt loads. A series of tests were conducted on an electrody-Bowen Consulting, Harwinton, CT, Mach. Des., 5d namic exciter in which the transient acceleration time histo-(5), pp 227-231 (Mar 10, 1983) 6 figs ries, which had been measured during the Space Transporta-

tion System-I launch, were simulated. The actual flight dateKey Words: Bearings, Roller bearings had to be filtered and compensated so that it could be repro-

duced on the shaker without exceeding displacement and

Microfinishing of industrial bearings could Increase their velocity limitations. Mounting bolt loads were measureddynamic load capacity by 30%, or a 250% Increase in life. directly by strain gages applied to the bolts. Various gap

In the article, two ways of microfinishing are described, thicknesses and bolt torques ware investigated.

and the improved dynamic performance characteristics arediscussed. Applications range from automotive wheels andaxles to computer dilc drives.

* 83-1348Earthquake Resistant Tensile Lap SplicesJ.D. Aristizabal-Ochoa

8341346 Vanderbilt Univ., Nashville, TN 37235, ASCE J.The Effect of Side Bearing (earace on Vertical Struc. Engrg., 1Q (4), pp 843-858 (Apr 1983) 12

.:: Wheel Forces"" "WhdFre figs, 2 tables, 33 refs +;-'P.A. Tombers and R.P. SellbergTrailer Train Co., Chicago, IL, ASME Paper No. 82- Key Words: Seismic design, Joints (junctions), Fatigue lifeWA/RT-7

A review of current code requirements on lap splices and IR

Key Words: Bearings, Wheels, Damping their limitations in seismic design is presented. A simpleanalytical model of an embedded bar is examined and cor-

An analysis is completed concerning the effect of side bearing related with available experimental data. The force transferclearance on the vertical wheel forces for a 70 ton boxcar, mechanisms of lap splices and the effects of properly placedThis analysis Includes the effect of track cross level, track transverse reinforcement to avoid brittle failure are studied.stiffness, constant damped truck, variable damped truck androll angle on the side bearing clearance versus vertical wheelforce relationship.

VALVES(Also see No. 1384)

FASTENERS

83-134983-1347 Experknental Modal Survey - A Case HistoryEvaluation of Mounting Bolt Loads for Space Shuttle P. Avitabile and H. RobinsonGet.Away-Speciil (GAS) Adapter Been ITT Grinnell Corp., Providence, RI, Intl. ModalD.C. Talapatra and D.J. Hershfeld Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,

56

rs..C..C....- .. . , - . .-... -. " -.. --.... . -.. ........

-C .... +....-%... . .... ++..........-....,.... •.... . .

FL. Spans. Union College, Schenectady, NY, pp 83-135166-71, 8 figs, 2 refs Dynamic Analysis of a Low-Cost Catenary System

for Electric RailroadsKey Words: Valves, Nuclear reactor components, Modal G.R. Doyle, Jr.tests Battelle Columbus Lab., Columbus, OH, ASME Paper

No. 82-WA/RT-2Results of an analytical model and an experimental modalsurvey of a nuclear, safety-related valve assembly are pre-sented. Preliminary experimental investigation revealed two Key Words: Cateneries, Transmission lines, Electric railroadsfirst cantilevered bending modes of the main structure exist --at 30 Hz and 47 Hz. Subsequent investigation of all sub- A simplified railroad electrification system has been sug-components of the assembly reveal that the 47 Hz mode gested to reduce the construction and maintenance com-is the first cantilevered bending mode of the structure and plexities and cost associated with the conventional collector/that the 30 Hz mode is due primarily to an internal sub- conductor system. The new system includes a single-con-assembly that also caused the main structure to respond ductor catenary and a collector attached to the conductorin the shape of the first cantilevered mode. Without testing by two sets of rotating wheels. This paper outlines the dy-all sub-components, an improper description of the modal namic models, presents the parametric study, and recon-characteristics would have resulted, mends several guidelines to follow in designing the traveler/

conductor system.

83-1350 83-1352Resonant Frequency Analysis for Extended Struc- Measurement of the Mechanical Characteristics of atures Full Scale Transmission Line Conductor BundleH.M. Fishman S.J. PriceFranklin Res. Ctr., Philadelphia, PA 19103, Intl. Dept. of Mech. Engrg., McGill Univ., Montreal,Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982, Canada, Intl. Modal Analysis Conf., Proc. 1st, Nov 8-Orlando, FL. Spons. Union College, Schenectady, 10, 1982, Orlando, FL. Spans. Union College, Schen-NY, pp 630-635, 8 figs, 4 refs ectady, NY, pp 396-402, 7 figs, 12 refs

Key Words: Valves, Seismic analysis, Resonant frequencies Key Words: Transmission lines, Cables, Wind-induced excita-

The determination that the resonant frequency be suffi- tion, Aeroelasticity, Vibration measurement, Natural fre-

ciently large for certain structures may permit the use of quencies, Mode shapes, Modal damping

more economical static rather than dynamic structural analy- As a result of an aeroelastic investigation of overhead powersis methods for seismic qualification. An extended configure- conductors, the importance of the natural frequencies, modetion such as a valve yoke with massive actuator is frequently shapes, and modal damping values for the complete con-modeled as a cantilever beam with a single lumped mass at ductor-spacer system has become apparent. In this paper,its end; the natural frequency being a well known function an attempt to measure these parameters on a full scaleof the bending stiffness of the beam, length and mass. For experimental transmission line is described.actuators with a mass distribution, not readily represented byconcentrated mass, this could lead to gross errors In fre-quency calculation. To demonstrate this, a mathematicalmodel was formulated of a rigid dumbbell supported at theend of a cantilever beam. Closed-form solutions were ob-tained for natural frequencies of simple cantilever, combined 83-1353bending-rotation, torsional, and axial modes of vibration. Nolinear Dynamics of Cable Supported SystemsThe ratios of these frequencies were presented in terms of the Molieabr D a de Bacel"orstiffness and geometric parameters. M L. Gambhir and B deV. Batchelor

Thapar Engrg. College, Patiala, India - 147 001, Intl.Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,

STRUCTURAL COMPONENTS Orlando, FL. Spans. Union College, Schenectady,NY, pp 656-661, 6 figs, 9 refs

Key Words: Cables, Nonlinear systems, Finite element tech-CABLES nique

57

i , ." , , . .-.,".. . ., -,,". .. . ..- . -. . . -. .. . . -.. .-... . . : . . .... . . . - . *.

C.- --

The paper deals with the dynamic analysis of geometrically theory. The equations of vibration and the boundary condi-

nonlinear cable structures by finite element techniques. The tions are determined from the stationary conditions of the

changes in cable tension and in the geometry of the system Lagrangian of the bar in a period of vibration. The equations

are taken into account using nonlinear strain-displacement of vibration are solved exactly in a series solution. As numeri- 0

relationships. The unknown frequencies estimated from cal examples, the natural frequencies and the mode shapes

the linear equation obtained for a snall perturbation of of symmetric elliptic arc bars with both clamped ends and

amplitude, reduce the nonlinear vibration problem to an with both simply supported ends are obtained.

initial value problem solved by successive corrections to theassumed stiffness matrices. A single cable which is a basiccomponent of more complex cable supported systems, is

critically analyzed. BEAMS

(Also see Nos. 1322,1354,1396)

BARS AND RODS83-1356Eigenfrequencies, Mode Shapes and Modal Masses of

83-1354 Beams in Coupled Vibrations - Theory and Experi- -

Dynamic Analysis of Mechanical Concentrators and ment

Nonuniform Elements Through Modulation Func- 0. Friberg, S. Ohisson, and 8. Akessontiona Divisions of Solid Mechanics and Steel and TimberY. Frostig,J. Gluck, and G. Rosenhouse Structures, Chalmers Univ. of Tech., S-412 96 Goth-

Faculty of Civil Engrg., Technion - Israel Inst. of enburg, Sweden, Intl. Modal Analysis Conf., Proc.

Tech., Haifa, Israel, Israel J. Tech., 20 (1-2), pp 17- 1st, Nov 8-10, 1982, Orlando, FL. Spons. Union

30 (1982) 8 figs, 25 refs College, Schenectady, NY, pp 147-152, 8 figs, 1table, 6 refs

Key Words: Rods, Beams, Columns, Modulation functions,Green function Key Words: Beams, Natural frequencies, Mode shapes, Cou-

pled response

The dynamic behavior of elements such as ultrasonic con-centrators, nonuniform parts of machines, beams and col- Beam cross-sections with noncoinciding centers of geom-

umns is investigated. In order to present a general approach etry, shear and mass often occur In practice. Instead of pure

the concept of modulation functions is introduced. The tensional, flexural and torsional vibrations, a beam with

relation between these functions - applied as to prirmit such a crossection performs coupled vibrations. A fre-

approximations - Is demonstrated, and the influtnce of quency-dependent 12x12 stiffness matrix for a uniform beam

different nonuniformities on the response of dynamic forced element in coupled vibrations under stationary harmonic

systems is determined with the aid of Green functions. end excitation can be established by use of an analytic mth-

Numerical results of significant examples are represented by od. Eigenfrequencies and mode shapes of built-up frame

appropriate formulas and graphs, structures in space can thereby be determined. It is shown

here how modal masses (generalized masses) of these struc-

tures can be found from a double-sum (real) of complex-valued terms. Experimental results from a laboratory testing

of a space frame model are compared with computed values.

83-1355Out-of-Plane Vibrations of Curved Bars with Varying

Cross-Section2K. Suzuki, T. Kosawada, and S. Takahashi 83.1357Faculty of Engrg., Yamagata Univ., Yonezawa,

Facuty f Enrg. Yamgat Uni., onezwa, Large Amplitude Vibrations of Moderately ThickJapan, Bull. JSME, 26 (212), pp 268-275 (Feb 1983) Beams

17 figs, 13 refs M. Sathyamoorthy

Dept. of Mech. and Industrial Engrg., Clarkson Col-Key Words: Bars, Curved rods, Variable cross-section, Natural lege of Tech., Potsdam, NY 13676, Intl. Modal

frequencies, Mode shapes Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,

The out-of-plane fre vibrations of a curved bar of which FL. Spons. Union College, Schenectady, NY, pp 136-the crosssection varies, are analyzed using the classical 140, 5 tables, 12 refs -@4

58

.

-,-. -" -- f-. - -- o

Key Words: Beams, Transverse shear deformation effects, Key Words: Grids (beam grids), Dynamic stiffness, MatrixRotatory inertia effects methods, Flexural vibration, Torsional vibration, Natural

frequencies, Mode shapesModerately thick beams are widely used as structural ele-ments and the study of their dynamic behavior should con- The dynamic stiffness method has been used in the past -sider the transverse shear and rotatory inertia effects in the primarily for calculation of exact modal parameters andanalysis. A review of literature indicates that approximate frequency response of beams, frames, and trusses. The ..-solutions to this class of problems are very limited and are method is extended in this paper to another class of struc-based on some limited application of the finite element ture composed of one-dimensional members, the planemethod. In this paper, self-generating functions are used grillage. An example grillage is defined numerically, andto investigate the nonlinear dynamic behavior of beams exact modal solutions are presented. Approximate solutionsaccounting for the effects of transverse shear and rotatory calculated by the finite element method are also presented . 1inertia. Numerical results for nonlinear frequency ratios are for comparison.reported for beams with different boundary conditions.Effects of amplitude of vibration, length-to-radius of gyra-tion ratio, boundary conditions as well as coupling betweenmodes are studied.

83-1360Parametric Instalility of Curved GirdersS.A. AllKing Abdulaziz Univ., P.O. Box 9027, Jeddah, Saudi83-1358Arabia, ASCE J. Struc. Engrg., 109 (4), pp 829-842Damped Second-Order Rayleigh-Timoshenko Beam (Apr 1983) 3 figs, 21 refs .:-

Vibration in Space - An Exact Complex Dynamic ( 1 3 s rMember Stiffness Matrix Key Words: Beams, Girders, Curved beams, Pulse excitation,

R. Lunden and B. Akesson Parametric excitationDiv. of Solid Mechanics, Chalmers Univ. of Tech.,Gothenburg, Sweden, Intl. J. Numer. Methods The pairnetric inetability of a curved girder subjected to

Engrg., 19 (3), pp 431-449 (Mar. 1983) 7 figs, 1 equal and oppesrza periodic moments at the ends is exam-table, 23 refs ined. It is shown that the relationship of the frequencies at

which parametric resonance occurs differs from the frequen-cy relationship of ordinary resonance. For small values of the

Key Words: Beams, Rayleigh method, Timoshenko theory, applied couples at the ends, the parametric resonant fre-Damped structures, Harmonic response, Matrix methods quency is twice the natural frequency. The method pre-

sented can also be used to determine the natural frequenciesA uniform linear beam in a uniform linear ambient medium and static buckling moment for a curved girder. Specialis studied. The beam performs stationary harmonic damped analytical solutions and numerical results are obtained andnonsynchronous space vibration in simultaneous tension, presented in nondimensional formstorsion, bending and shear in the presence of a large staticaxial load. Hysteretic and viscous dampings of the beam ,,,-material and ambient medium are considered. Generalizedcomplex Koloulek functions are derived.

CYLINDERS

83-136183-1359 Non-Axisymmetrical Vibrations of a SheU-StiffenedCalelation of Exact Vibration Modes for PlaneGr l es by the Dynamic Stiffness Method I. Maljutin and A. NedbajW.L. Hallauer, Jr. and R.Y.L. Liu Vibrotechnika, A (34), pp 19-24 (1981) 2 figs, 2 refsVirginia Polytechnic Inst. and State Univ., Blacks- (In Russian)burg, VA 24061, Intl. Modal Analysis Conf., Proc.1st, Nov 8-10, 1982, Orlando, FL. Spons. Union Key Words: Cylinders, Stiffened structures, Shells, NaturalCollege. Schenectady, NY, pp 1-7, 3 figs, 1 table, frequencies, Transverse shear deformation effects, Numerical10 refs analysis

59* . * . . o

W7 7

This report discusses two-dimensional free vibrations of a Key Words: Framed structures, Spacecraft, impulse re-shell-stiffened elastic cylinder. Transverse shear in the shell sponse

is considered. Equations of cylinder motion are reduced to -

homogeneous and non-homogeneous Bessel's equations by The free flight deformation behavior of triangular frames,transformation method. Numerical analysis of natural fre- subjected to distributed and concentrated impulsive loads,quency dependence from cylinder inner radius is presented. is investigated experimentally. A numerical technique, based

on finite difference principles, is used to theoretically predictthe elastic-plastic response of the frames. The agreementbetween the experimental results and those predicted theo-retically appears to be reasonably good.

83-1362Forced Vibrations of a Viseo-Elastic Shell-StiffenedCylinderI. Maljutin and A. Nedbaj 83-1364Vibrotechnika, 4(34), pp 25-31 (1981) 3 figs, 4 refs Shear Deformation in Seismic Frame Structures(In Russian) R.C. Fenwick

Univ. of Auckland, Auckland, New Zealand, ASCEKey Words: Cylinders, Shells, Harmonic excitation, Forced J. Struc. Engrg., 109 (4), pp 965-976 (Apr 1983)vibration, Viscoelastic properties 12 figs, 8 refs

The subject of the study is the stress-strained state of a sys-tem comprising an orthotropic shell and a hollow isotropic Key Words: Framed structures, Buildings, Reinforced con-

visco-elastic shell-stiffened cylinder subjected to harmonically crete, Earthquake response

variable distributed loading. Shell motion is described bytechnical theory equations. Cylinder behavior is determined Inelastic cyclic loading in reinforced concrete members,

by three-dimensional elastic theory equations written in the which may occur in ductile frame structures under severe

form of vectors. These equations are solved by Lame method, seismic conditions, causes shear deformation to develop in

Visco-elastic properties of the cylinder are expressed by hinge zones. Experimental results illustrating this are pre-

complex module of elasticity. Problem solution is found in sensed.

double trigonometric series. A numerical example is given.

83.1365COLUMNS Structural Frame Vibration Analysis Baed on Mea.

(See Nos 1354,1396) wed Support Mobilities

B. Akesson, 0. Friberg, and E. KamphDiv. of Solid Mechanics, Chalmers Univ. of Tech.,S-412 96 Gothenburg, Sweden, Intl. Modal Analy-

FRAMES AND ARCHES sis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL.

Spons. Union College, Schenectady, NY, pp 463-476,

20 figs, 15 refs

83-1363 Key Words: Frames, Beams, Machine foundations, Founda-Experimental and Theoretical Study of the Grow tions, Modl analysis, Impact tests, Curve fitting, Finite

Deforsation Response of Unresrained Triangular element technique

Frames Subjected to Concentrated and Distributed A resiliently supported plane frame superstructure was con-

hpulasve Loads structed. They dynamic properties of this superstructure

M.S.J. Hashmi were calculated by use of the exact displacement finite ele-

Dept. of Mech. and Production Engrg., Sheffield City ment method as implemented in the computer programSFVIBAT-)AMP. Measured end calculated date for the

Polytechnic, Sheffield, UK, Intl. Modal Analysis separate lower beam and for the resiliently supported super-

Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL. structure showed a reasonable agreement in the frequencySpons. Union College, Schenectady, NY, pp 550-558, range studied (0-400 Hz) except for the damping% at the four

12 figs, 6 refs resonance frequencies of the superstructure.

60

. ..............- - .

. .. . . . . . . .. * .- . " -.- -.-- - - -"- , ., . ..

83-1366 toria, South Africa, Rept. No CSIR-TWISK-245,Dynamic Analysis of Rilid Frame Structures Sub- 28 pp (Jan 1982)jected to Non-Liaear Eathquake Vibration N83-11512I.C. ChangCollege of Staten Island, City Univ. of New York, Key Words: Plates, Rectangular plates, Flutter SStaten Island, NY, Intl. Modal Analysis Conf., Proc.1st, Nov 8-10, 1982, Orlando, FL. Spons. Union Flutter and divergence instabilities of a rectangular plate

7 with two independent loading parameters are studied. TheCollege, Schenectady, NY, p643-648, figs, 21 refs plate is subjected to the combined action of a tangential

follower force and a unidirectional axial force along oneKey Words: Framed structures, Seismic analysis edge. Two opposite sides of the plate are simply supported,

one side being clamped and the other being a free edge4 This paper attempts to establish a mathematical model for where the inplane forces act.

the dynamic analysis of rigid frames subjected to nonlinear*'. earthquake vibration. The nonlinear H. Nagaoka seismic

equation is investigated by the asymptotic method. Theresults are compared from the application of two methods:the perturbation technique of Bogoliubov and Mitropolskyand the operational method of Linsted and Liapounoff. 83-1369An optimization scheme for designing simple rigid frames GCeoneh-ically Nonlinear Transient Analysis ofis suggested. Three possible breakdown mechanisms are taken Lllad C lnpoulte late.into consideration: buckling, side-sway, and combined J'..ed-' J.N. Reddy ",, ~collapse. -",Virginia Polytechnic Inst. and State Univ., Blacks-

burg, VA, AIAA J., 21 (4), pp 621-629 (Apr 1983)14 figs, 27 ref s

83.1367Key Words: Plates, Composite structures, Layered mate-83-1367 yrials, Transient response, Finite element technique, Trans-verse sheer deformation effects, Rotatory inertia effects

C.H. Coan and R.H. PlautBechtel Power Corp., Los Angeles, CA, Intl. J. Earth- Forced motions of laminated composite plates are investi-quake Engrg. Struc. Dynam., 11 (2), pp 269-274 gated using a finite element that accounts for the trans-(Mar/Apr 1983) 7 figs, 12 refs verse sheer strains, rotary inertia, and large rotations (in the

von Kirmin sense). The present results when specialized " -for isotropic plates are found to be in good agreement

• .- Key Words: Domes, Grids (beam grids), Impulse response with those available in the literature. Numerical resultsof the nonlinear analysis of composite plates are presented

A shallow lattice dome subjected to three independent sets showing the effects of plate thickness, laminzation scheme,of step or impulse loads is investigated. Symmetric and boundary conditions, and loading on the deflections andasymmetric loading distributions are considered. The dy- stresses. The new results for composite plates should servenamic response is determined by numerical integration, as bench marks for future Investigations.and critical loads are defined by the Budiansky-Roth cri-terlon. Interaction curves for fixed maximum response andfor snap-through instability are obtained, and a comparisonis made with previous results for static loading.

83-137010 Vibration Ansly-.- of Twisted Plates

PLATES V. Ramamurti and S. SreenivasamurthyDept. of Appl. Mechanics, Indian Inst. of Tech.,Madras 36, India, Intl. Modal Analysis Conf., Proc.1st, Nov 8-10, 1982, Orlando, FL. Spons. Union

83 1368 College, Schenectady, NY, pp 303-309, 6 figs, 3Stalblity of a Reeagular Plate under Noneonserva- tables, 21 refstive and Con ervative Forces

" S. Adali Key Words: Plates, Cantilever plates, Flexural vibration,National Res. Inst. for Mathematical Sciences, Pre- Torsional vibration, Compressor blades, Blades . "

""61

"-. . . . .. . .

The trends of variation of the first five frequencies of low 83-1373aspect ratio cantilever plates with pretwist angle have been The Effects of Boundary Conditions on the Vibrationstudied using three dimensional elements as well as shell of Transverse Isotropic Thick Plateselements. Both the analyses agree as far as the trend of Lien-Wen Chen, Ji-Liang Doong, and Tin-Yew Yevariation is considered.LinWnCeJ-in o g adT-Yw eDept. of Mech. Engrg., National Cheng Kung Univ.,

Tainan, Taiwan, R.O.C., Intl. Modal Analysis Conf.,Proc. 1st, Nov 8-10, 1982, Orlando, FL. Spons.Union College, Schenectady, NY, pp 319-325, 9

83-1371 figs, 1 table, 14 refsModal Andly-s of Perforated Plates with TriangularPatterns of Ckcular Holes Key Words: Plates, Rectangular plates, Finite strip method,S.N. Plyat and A.P. Villasor, Jr. Boundary condition effects, Natural frequencies

Nuclear Technology Div., Westinghouse ElectricCopPitbrgP,-nl MdlAnlss of, The free vibration problems of a rectangular thick plateCorp., Pittsburgh, PA, Intl. Modal Analysis Conf., under arbitrary initial stresses are solved by the finite stripProc. 1st, Nov 8-10, 1982, Orlando, FL. Spons. method. The initial stresses are taken to be a uniform exten-Union College, Schenectady, NY, pp 326-332, 7 sional stress plus a bending stress. The effects of differentfigs, 6 tables, 6 refs boundary conditions and various parameters on natural

frequencies are investigated.

Key Words: Plates, Hole-containing media, Modal analysis

The concept of equivalent solid plate elaborated for stress-strain problems of perforated plates with triangular pene-tration patterns is found sufficiently accurate for modal 83-1374analysis of such plates. The replacement solid plate must be Vibration of a Plate of Arbitrary Shape with Freeconsidered anigotropic with the effective elastic constantsdetermined according to the theory by O'Donnell, et al. and Simply Supported Mixed EdgesWith any combination of simply supported/fixed boundary K. Nagaya

* condition at the circumference, a maximum discrepancy of Dept. of Mech. Engrg., Faculty of Engrg., Gunmaabout 8% on the first natural frequencies results. This devi- Univ., Kiryu, Gunma 376, Japan, J. Acoust. Soc.ation increases to 22% with free/partlally free condition at Amer., 2a (3), pp 844-850 (Mar 1983) 7 figs, 4the circumferential edges. tables, 15 refs

Key Words: Plates, Natural frequencies, Boundary conditioneffects

83-1372"1372 oA method for solving vibration problems of a plate of arbi-A Study of the Mode Shaps and Natural Frequencies trary shape with free and simply supported mixed edges isof Two Plates Coupled Together with Radial Stiffen- presented. In the analysis the exact solution of the equationerg of motion which includes terms representing the reactionA. Gupta and C.E. Passerello forces of the simply supported edges is applied. The bound-Michigan Technological Univ., Houghton, Ml 49931, ary conditions along the edges of arbitrary shape are otisfiled

directly by making use of the Fourier expansion collocationIntl. Modal Analysis Conf., Proc. 1st, Nov 8-10, method. The equation for finding the eigenfrequencies of1982, Orlando, FL. Spons. Union College, Schenec- plates of arbitrary shape with free and simply supportedtady, NY, pp 310-318, 2 figs, 3 tables, 3 refs mixed edges is obtained. Numerical calculations are carried

out for polygonal plates, trapezoidal plates, truncated ellipti-

Key Words: Plates, Stiffened plates, Natural frequencies, cal plates, and parabolic plates with mixed edges.Mode shae

This paper examines the mode shapes and natural frequenciesof a system composed of two annular plates. The plates areconnected by tranwerse stiffeners located In the radial direc- 83-1375Siena. The boundary conditions are prescribed so that alledges are free except for the inner edge of one of the disks The Influence of Mid-Plane Nor.al Stress and Cromwhich is fixed. The stiffeners along the radial directions are Section Deformation in Free Vibrating Platesapproximated as line springs. H. Irretier

62..................... .

7-- - -

Institut f. Mechanik, Universitat Hannover, Hannover, Key Words: Plates, Cantilever plates, Natural frequencies,

Bundesrepublik Deutschland, Mech. Res. Comm., Mode shapes, Aircraft wings10O (1), pp 53-61 (Jan/Feb 1983) 6 figs, 2 tables,7 refs A numerical method for the free vibration analysis of canti-7 ref s lever quadrilateral plates of general shape is presented. Using

%..; ~~quadrilateral coordinates and integral equation of beams, -.. j

Key Words: Plates, Free vibration the expressions for the strain energy and kinetic energy are*%- developed. The formulation and derivation of equations are - ,

The classical plate-theory, as introduced by Kirchhoff, as- in the matrix form "ab initio." The eigenvalue problem isSsumes, in the form of the hypothesis of nondeformable solved for frequencies and mode shapes.

normals, a linear distribution of the in-plane deformationacross the thickness of the plate and also neglects the influ-ence of normal stresses with respect to the middle-plateswrface. In this paper the influence, in the sense of thetwo-dimensional plate theory, of the in-plane displacements SHELLSand normal stresses (the secondary effects) on the eigen- (Also see Nos. 1361, 1362)frequencies, eigenforms and stress distributions are investi-gated. For this purpose a simply supported, free vibratingplate is considered by inserting double Fourier series solu-tions into the different plate equations and then solving 83-1378 Mthese using a Newton-Raphson iteration method. Dynamic Stability of a Thin Cylindrical Shell M idel

of a Spin Stabilized SatelliteW.N. Dong and A.L. Schlack, Jr.Sperry-Univac, Santa Clara, CA, Intl. Modal AnalysisConf., Proc. 1st, Nov 8-10, 1982, Orlando, FL.

83-1376 Spons. Union College, Schenectady, NY, pp 692-697,Dynamic (Transient) Anally-- of Layered Aniaotropic 4 figs, 3 refsComposite-Material PlatesJ.N. Reddy Key Words: Shells, Cylindrical shells, Satellites, StabilityDept. of Engrg. Science and Mechanics, VirginiaPolytechnic Inst. and State Univ., Blacksburg, VA, A dynamic stability analysis employing Liapunov's direct

Intl. J. Numer. Methods Engrg., 9 (2), pp 237-255 method is presented for studying the influence of structuralflexibility on the attitude stability of a spin stabilized setel-

( 9 5 3 l 5lite. The satellite is modeled as a thin elastic circular cylindri-cal shell attached to a rigid structural frame of finite mass.

Key Words: Plates, Composite structures, Layered materials, The Flugge shell theory is employed and the shell's deforma-Transient analysis tions are described by a complete infinite series of functions

satisfying boundary conditions.A sheer-flexible finite element is employed to investigate thetransient response of isotropic, orthotropic and layeredanisotropic composite plates. Numerical convergence andstability of the element is established using Newmark's directintegration technique. Numerical results for deflections and 83-1379stresses are presented for rectangular plates under variousboundary conditions and loadings, The parametric effects The Structural Analysis of a Solar Furnaceof the time step, finite element mesh, lamination scheme and R.S. Pinkham, Ill and L.J. LaFranceorthotropy on the transient response are Investigated. General Dynamics Corp., San Diego, CA, Intl. Modal

- Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,FL. Spon Union College, Schenectady, NY, pp

709-713, 4 figs, 3 tables, 4 refs

"-1377 Key Words: Solar cells, Shells, Modal analysisFree Vibration of Cantilever Quadrilateral PlatesR.S. Srinivasan and B.J.C. Babu The dynamic analysis of a 25.6 meter radar dish converted

to a high temperature solar test facility is described. TheIndian Inst. of Tech., Madras-800036, India, J. finite element modeling of the structure is discussed. TheAcoust. Soc. Amer., 73 (3), pp 851-855 (Mar 1983) mode shapes and eigenvalues are compared to the structure's

3 figs, 1 table, 15 refs vortex shedding frequencies.

63

"EL'

-:77777 7-7 7- 1.-8-.-r-x

W31380 The determination of flutter frequencies and flutter bound-

Modal Analysis of Damped Cylindrical Shella with ary pressures of conical shells is carried out using finiteelement analysis. Static condensation procedure with Q.R.algorithm is used for the extraction of eigenvalues of the

S.N. Singhal and E.G. Lovell system. An empirical relation for determining the values of

Shell Development Co., Houston, TX 77001, Intl. flutter boundary pressures of clamped-clamped conicalModal Analysis Conf., Proc. 1st, Nov 8-10, 1982, shells is proposed. It is seen that there is an optimum semi-

Orlando, FL. Spons Union College, Schenectady, vertex angle at which a given conical shell of prescribedfigs, 4 ref length and initial radius offers maximum resistance for flut-

NY, pp 686-691, 2 ter.,4 ef ter. .:

Key Words: Shells, Cylindrical shells, Damped structures,Temperature effects, Modal analysis, Transient response

Modal analysis is used to determine the transient response PIPES AND TUBESof isotropic, elastic, thin, damped cylindrical shells with (Also see No. 1332)temperature-dependent material properties. Flugge's shellequations are modified to include the temperature-depen-dence of the elastic modulus and thermal strain coefficient.A perturbation technique is used with small parameters 83-1383identifying the changes in material properties. Aoustialy Induced Piping Vibration in High

Capacity Pressure Reducing SystemsV.A. Carucci and R.T. MuellerExxon Res. and Engrg. Co., Florham Park, NJ, ASMEPaper No. 82-WA/PVP-8

83-1381Vibration Studies and Tests of Liquid Storage TFiks Key Words: Piping systems, Noise induced excitation, Reso-

M.A. Haroun nant response, Fatigue lifeUniv. of California, Irvine, CA, Intl. J. Earthquake"""Ungrv. oftCalifrna, Irvine, CA, pnl 179-206 E ar e This paper describes the causes of high acoustic energy,

how it can excite remnant piping vibration and ultimatelyApr 1983) 21 figs, 3 tables, 27 refs result in fatigue failures, and provides highlights of failure

experience. Correlations are presented based on sound ..

Key Words: Shells, Storage tanks, Fluid-filled containers, power level, line size and operating experience which maySeismic design, Vibration tests be used to evaluate systems for potential problems.

Theoretical and experimental investigations of the dynamicbehavior of ground-supported, deformable, cylindrical liquidstorage tanks were conducted. The study was carried out inthree phases: a detailed theoretical treatment of the coupledliquid-shell system for tanks rigidly anchored to their founda- 83-1384tions; an experimental investigation of the dynamic charac- Analysis of Relief/Safety Discharge Loads by Modalteristics of full-scale tanks; and a development of an im- Approachproved seismic design procedure. Zs. R~vgsz

Electrowatt Engineering Services Ltd., CH-8022Zurich, Switzerland, Intl. Modal Analysis Conf.,Proc. 1st, Nov 8-10, 1982, Orlando, FL. Spons.Union College, Schenectady, NY, pp 296-302, 7

83.1382 figs, 10 refsOptimum Cone Angles in Aeroelastic FlutterP.J. Sunder, C.V. Ramakrishnan, and S. Sengupta Key Words: Piping systems, Valves, Nuclear power plants,Dept. of Appl. Mech., Indian Inst. of Tech., New Seismic excitation, Fluid-induced excitation, SubstructuringDelhi, India, Computers Struc., 1Z (1), pp 25-29 methods

(1983) 2 figs, 4 tables, 5 refs The paper summarizes what has been done to account for

dynamic loading associated with Relief/Safety Valve DisKey Words: Flutter, Aeroelasticity, Conical shells, Shells, charge (R/SVD) and other foads such as weight, thermalFinite element technique effects and seismic loads in a main steam line with attached

.... ..... . ...

R/SVD lines in a boiling water reactor plant. The analysis 83.1387included the entire portion of the piping. The paper presents Dynamic Impact Requirements for Deign of Pipean industrial application, in which economy of computation Break Whip Restraintsplayed an important role. The results demonstrate thatcomprehensive analysis of a complex piping system can be R.C. Sampsn -

performed economically with modal analysis up to rela- Bechtel Power Corp., San Francisco, CA, ASMEtively high frequencies. Paper No. 82-WA/PVP-5

Key Words: Piping systems, Energy methods, Impact re-sponse

This paper describes the application of the energy method to

83-1385 the problem of determining the structural requirements and

A Time-Averagimg Tranmient Testing Metlod for pipe break performance on the basis of lumped eiementmodels. Simple relationships based on the energy-limited

Acosic Properties of Piping Systems and Mufflers forced displacement of several different types of restraints

wak Flow are developed.T.Y. Lung and A.G. DoigeNGL Dept., Dome Petroleum Ltd., Box 200, Calgary,Alberta, Canada T2P 2H8, J. Acoust. Soc. Amer.,

23 (3), pp 867-876 (Mar 1983) 20 figs, 27 refs83-1388

Key Words: Piping systems, Acoustic properties, Mufflers, Dynamic Response of Piping Systems at VaryingTesting techniques Load Amplitudes. Experimental Studies of Damping

A time-averaging transient testing technique has been devel- G.E. Howard, W.B. Walton, D.E. Chitty, P. Ibanez,oped to allow for a rapid measurement of the matrix param- H.T. Tang, and Y.K. Tangeters and other frequency-dependent characteristics of ANCO Engineers, Inc., Culver City, CA, ASME Paperacoustical systems with or without mean flow. The tech- No. 82-WA/PVP-9nique is applicable to systems with substantial flow noisecontamination which is either random or periodic in nature. K o P g e Nwr n aFlowand o-fow eperment wer coductd o labrs- Key Words: Piping systems, Nuclear power plants. Variable=- ".

Flow and no-flow experiments were conducted on labors-tory models of exhaust mufflers, variable area ducts, and amplitude excitation, Dampingcomplex piping networks. In 1979 a series of analyses and tests of a nuclear power plant

piping system were begun to investigate the dynamic charac-teristics of such a system. The ultimate goal of the researcheffort is the development of improved analysis methodsfor piping systems subjected to dynamic loads. Among themajor objectives of the research were investigations of

83-1386 piping system damping and nonlinear phenomena as a func-ynmll Beavior of Piping anid Supports at F - tion of response amplitude, and the development of bench-

Load Lerds - Experimental Study of a Scaled Sys- mark data for validating nonlinear analysis methods

tonK. Blakely, P. Ibanez, and S. GriffithANCO Engineers, Inc., Culver City, CA, ASME PaperNo. 82-WA/PVP-4 83-1389

Damping in Nodimear Piping SystemsKey Words: Piping systems, Nuclear power plants, Seismic D.E. Chitty, G.E. Howard, and W.B. Walton -.response, Crash research (aircraft) ANCO Engineers, Inc., Culver City, CA, ASME Paper

A one-third scale model of an existing nuclear power plant NO. 82WA/PVP-10piping system and its concrete support points were testedto asse=s their ability to withstand dynamic loads resulting Key Words: Piping systems, Damping coefficientsfrom an earthquake and from an aircraft impacting thecontainment structure. Velocity scaling was used, which A numerical study was made of various methods for calcu-maintained stress and strain equality between the prototype lating damping from experimental structural response data.and the scale model. It is shown that the various methods can produce signifi-

65

..- -..- ,-'....... .............

cantly different damping values. This is a significant result Key Words: Pipelines, Pipe whip, Finite element technique,since many, if not most, structural systems encountered in Beamspractice have some measurable nonlinearity.

Calculations of pipe whip are performed with the help of afinite element code using a beam formulation. Impact issimulated by introducing the local nonlinear stiffness of thepipe. This resistance curve is obtained by a shell calculation

831390 in good agreement wih a static crush test.

Seimuic Testing and Analysis of a Prototypic Non-limer Piping systemD.A. Barta, M.J. Anderson, and L.K. Severud BUILDING COMPONENTSWestinghouse Hanford Co., Richland, WA, ASMEPaper No. 82-WA/PVP-6

83-1393Key Words: Piping systems, Seismic response, Dynamic tests Dynamic Centrifuge Testing of a Cantilever Retaining

WalA series of seismic tests and analysis of a nonlinear Fast FluxTest Facility prototypic piping system are described, and L.A. Ortiz, R.F. Scott, and J. Leemeasured responses are compared with analytical predic- Soil Mechanics Lab., Div. of Engrg. and Appl. Sci-tions. ence, California Inst. of Tech., Pasadena, CA 91125,

Intl. J. Earthquake Engrg. Struc. Dynam., 11 (2),pp 251-268 (Mar/Apr 1983) 14 figs, 7 tables, 48 refs

Key Words: Walls, Dynamic tests83.1391Upper Bounds of Modal Representation Applied to Two correctly-scaled model cantilever retaining wells ofPiping Anallysis different stiffnesses were tested under dynamic loading

conditions in a centrifuge. A medium-dense fine send wasM.Z. Leeretained with a range of backfill slopes For the centrifuge

Gilbert/Commonwealth Co., Reading, PA 19603, model, an earthquake-generating mechanism was designed

Intl. Modal Analysis Conf., Proc. 1st, Nov 8-10, to produce seismic shaking equivalent to that generated at

1982, Orlando, FL. Spans. Union College, Schenec- ground surface in the epicentral area of an earthquake of

tady, NY, pp 272-277, 8 refs approximate magnitude 5-5, The response of the modelretaining walls to the input dynamic motion was measuredby strain gauges, pressure transducers and accelerometers.

Key Words: Modal analysis, Piping systems, Seismic response, From the measurements plots were constructed of moment,Spatial response shear, pressure and displacement over the height of the wells

as a function of time. The results are compared with calcu-Mathematical bases of both modal response analysis in the lations based on the quasi-static Mononobe-Okabe theory.time and frequency domains, and the method of computingupper bounds of seismic responses by using incompleteeigenvalue solutions, are reviewed. Theoretical justificationsare given for the application of those upper bounds to pipinganalysis. A method of computing an upper bound of spatialresponse combination is introduced and illustrated by appli- 831394cation to the analysis of typical, simple, piping configurations Response of Structures with Flexible Floor Systemsinstalled In on arbitrarily-rotated orientation. Subect to Vertical Ground Motion

S.L. Chin, M.P. White, and F.J. DzialoYankee Atomic Electric Co., Framingham, MA, Intl.Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,Orlando, FL. Spans. Union College, Schenectady,

8,-pipe NY, pp 614-621, 6 figs, 2 tables

A Simplified Methodology for Calculations of PipepJ.-.Grct Cp ard wh Ts tsKey Words: Floors, Nuclear power plants, Ground motion

J.-L. Garcia, P. Chouard, and A. MartinKeCommissariat A L'Energie Atomique, France, ASME An analytical method to predict the dynamic response ofPaper No. 82-WA/PVP-2 structures with flexible floor systems, and subject to the

.4

66 "

. vertical component of a ground motion are developed. Pre- number of degrees of freedom, and only a given number of

scribing mode shapes and coordinates which couple the lower modes can be computed accurately. This paper shows

bending and rigid body motion between the floor slabs and how to design a reduced-order controller to control a coin-elastic columns, and then operating with Lagrange's equa- plex structure during earthqu)ke

tions on the respective energies of the system, a set of cou-pled equations is determined. The resulting equations areuncoupled in mass-stiffness form, and solutions for free and

forced vibration are determined by classical normal modetheory. The solutions are applied to an existing nuclear DYNAMIC ENVIRONMENTpower plant facility. Numerical results giving frequencies, .normalized mode shapes, and floor responses for bothflexible and rigid slabs due to a suddenly applied ground

acceleration are presented.ACOUSTIC EXCITATION

83-139783-1395 Ground Runup Noise Suppression Program. Part 3.Finite Element Analyss of Reinforced Concrete Dry Suppressor Technology BaseStructures R. Glass and M. LeporN.G. Sarig{il Naval Ocean Systems Ctr., San Diego, CA, Rept. No.

Istanbul Technical Univ., Turkey, Intl. Modal Analy- NOSCITR-674, 205 pp (June 20, 1982)

sis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL. AD-A122 025Spons. Union College, Schenectady, NY, pp 26-31,

8 figs, 4 refs Key Words: Noise reduction, Experimental test data

The Ground Runup Noise Suppression Final Report consistsKey Words: Structural members, Reinforced concrete, Coin- of three documents. The first document is an executiveputer programs, Finite element techniques summary which provides a brief, technical description and

overview of the program conducted at the Naval Ocean Sys-A finite element displacement method is developed for theaanalysis of two dimensional reinforced concrete structures documented history of NOSe's participation in the Dry Jet

under short time, monotonic loading. It is assumed that doise hston of Tis documen in te " Jetcracks of concrete may occur and propagate at the nodes technical

instead of assuming smeared cracks along the whole element, summary of the information and data developed during theprogram. This report integrates predictive techniques, scale-

A computer code is developed for the numerical compute- model test results, and full-scale test results for the new air-tions, A uniformly loaded reinforced concrete beam is cooled noise suppressor technology. All program deta are

studied as an example. summarized to assist the architect/engineer in the design of

air-cooled noise suppresors."

83-13%-Control of Structures Subjected to Seimic Excita- 83-1398tion Anti-Noise - The Esex Breakthrough

L. Meirovitch and L.M. Silverberg B. ChaplinVirginia Polytechnic Inst. and State Univ., Blacks- Wolfson Centre for the Cancellation of Nok,- andburg, VA 24061, ASCE J. Engrg. Mech., 109 (2), Vibration, Univ. of Essex Colchester, Essex, UK,

pp 604-618 (Apr 1983) 12 figs, 11 refs Chartered Mech. Engr., 30 (1), pp 41-47 (Jan 1983)19 figs, 8 refs

Key Words: Seismic excitation, Beams, Columns, Finiteelement technique Key Words: Noise reduction

Complex structures represent assemblages of distributed The principle of noise cancellation is based upon the addition

components such as beams, columns, etc. A method capable of pure tone (sinusoid) to an antiphase version of equalof modeling complex structures is the finite element method, amplitude. A method for generating the antiphase noise,The resulting discrete model generally possesses a large called the waveform synthesis, is described.

67

~*, * 2 *, I".,

p..0

83-1399 Key Words: Acoustic intensity method, Measurement tech-

Prediction of the Acoustic Intenity Basnd on Mode niques, Two microphone techniquehalpes-.Sas A theoretical derivation is presented for the spectral density

of the acoustic velocity in terms of the auto- and cross-Kath. Univ. Leuven, Departement Werktuigkunde, spectral densities of the signals from two closely spacedCelestijnenlaan 300B, B-3030 Leuven, Belgium, microphoneb. This result, together with a Fast Fourier

Intl. Modal Analysis Conf., Proc. 1st, Nov 8-10, Transform minicomputer and a two-microphone probe,1982, Orlando, FL. Spons. Union College, Schenec- was used to measure the surface velocity of a vibrating flat

panel. The surface velocity thus measured agrees quite well,tady, NY, pp 403-409, 7 figs, 15 refs below the panel critical frequency, with that measured by

an accelerometer. The two-microphone probe was thenKey Words: Sound intensity, Mode shapes, Modal analysis, used to measure the acoustic intensity, and by summation,Noise reduction the acoustic power radiated by the same panel when it was

acoustically and mechanically excited. The panel radiationThis contribution reports on research conducted in the field efficiencies were calculated from these results for the aous-of noise control, especially the relation between modal tic and mechanical excitation caseL Satisfactory agreementdeformations and radiated sound power. The reported tech- was obtained with the theoretical panel radiation efficiency.nique fills in the gap between structural vibrations andradiated sound power. It enables, already in the designphase, accurate estimates of noise reduction measures.

83-1402Acoustic Scattering by Elastic Solid Cylinders and

83-1400 Spheres in Viscous FluidsInter-Laboratory Variability of Sound Absorption W.H. Lin and A.C. RaptisMeasurement Components Technology Div., Argonne Natl. Lab.,R.E. Halliwell Argonne, IL 60439, J. Acoust. Soc. Amer., 73 (3),Div. of Bldg. Res., National Res. Council of Canada, pp 736-748 (Mar 1983) 8 figs, 4 tables, 40 refs - .Ottawa, Ontario, Canada K1A OR6, J. Acoust.Soc. Amer., 73 (3), pp 880-886 (Mar 1983) 8 figs, Key Words: Acoustic scattering, Cylinders, Spheres

3 tables, 15 refsThis paper deals with analytic studies and numerical results

Key Words: Acoustic absorption, Test facilities, Measure- of the scattering of plane sound waves from an elastic circular

ment techniques cylinder and from an elastic sphere in a viscous fluid. Theelastic properties of the cylinder and the sphere and the

Sound absorption measurements have been made at a number viscosity of the surrounding fluid are taken into account

of acoustical laboratories in Canada and the United States in the solution of the acoustic-scattering problemL The

using the same specimen and the same measurement equip- associated acoustic quantities, such as the acoustic-scattering

ment and procedure. The results provide insight into the patterns, the acoustic-radiation forces, and the acoustic

effect of reverberation room and diffuser geometry on mea- attenuation, are first derived in closed forms and then evalu-

sured absorption coefficients. ated numerically for a given set of materiel properties.Numerical results show that increasing fluid viscosity tendsto increase the directionality of the angular distribution ofthe scattering patterns, especially in the forward direction.

83-1401Estimation of Acoustic Velocity, Surface Velocity,and Radiation Efficiency by Use of the Two-Micro-phone Technilque 83-1403B. Forssen and M.J. Crocker Acoustical Characteristics of Rigid Fibrous Absor-Ray W. Herrick Labs., School of Mech. Engrg., Pur- bents and Granular Materialsdue Univ., West Lafayette, IN 47907, J. Acoust. K. AttenboroughSoc. Amer., 73 (3), pp 1047-1053 (Mar 1983) 8 figs, Engrg. Mechanics Discipline, Faculty of Technology,28refs The Open Univ., Milton Keynes MK7 6AA, UK, J.

68:.:

,-,,~~~~~~~~~.....'...-.,.. ........... ............. .. ,........ ..... . .

U.- ..

Acoust. Soc. Amer., 3 (3), pp 785-799 (Mar 1983) should be used to produce closely spaced profiles as a stan-

22 figs, 5 tables, 28 refs dard pert of applying these acoustic propagation codes.

Key Words: Soils, Acoustic properties

A model is developed that predicts the acoustical charac- 83-1406teristics of rigid fibrous absorbent soils and sands fromfive parameters: porosity, flow resistivity, tortuosity, steady Optimum Frequency of Propagation in Shallow Waterflow shape factor, and dynamic shape factor. Environments

F.B. Jensen and W.A. KupermanSACLANT ASW Res. Centre, 19026 La Spezia, IItaly, J. Acoust. Soc. Amer., 7Z3 (3), pp 813-819(Mar 1983) 9 figs, 1 table, 23 refs

83-1404Geometric Disperson of Acoustic Signals Propagated Key Words: Underwater soundin a Deep Ocean Channel .The optimum frequency of propagation in shallow-water

K.D. Flowers environments is the result of competing propagation and

Naval Res. Lab., Washington, DC 20375, J. Acoust. attenuation mechanisms at high and low frequencies. It is

Soc. Amer., 73 (3), pp 806-809 (Mar 1983) 6 figs, shown that the optimum frequency is strongly dependent10 refs on water depth, that it has some dependence on the sound-

speed profile, while it is only weakly dependent on the" .bottom type. A comparison between experimental data and -

Key Words: Underwater sound normal-mode theory indicates the importance of shear

waves in the bottom, both in determining the optimum fre-Two sinusoidal signals generated in such a way as to have a quency of propagation and in determining the actual propa-constant frequency ratio are considered. Except for dieper- gation-loss levels at lower frequencies.sive effects of the propagation channel, the two signal fre-quencies should remain correspondingly related at a distantreceiver. As a measure of this relationship a correlation func-tion is defined for signals of different frequencies. In general,it is concluded that the dispersive effects of the ocean chan- 83-1407nel at long range can be significant for broadband signals Oa od u cwhen signal coherence isan important consideration. On the Caloulaton of Normal Mode Group Veocity

and AttenuationR.A. Koch, C. Penland, P.J. Vidmar, and K.E.HawkerAppl. Res. Labs., The Univ. of Texas at Austin,Austin, TX 78712-8029, J. Acoust. Soc. Amer., 73

83.1405 (3), pp 820-825 (Mar 1983) 10 refs

A Cautionary Note on the Use of Range-DependentPropagation Models in Underwater Acoustics Key Words: Underwater sound

R.F. Henrick The group velocity for a normal mode can be calculated

The Johns Hopkins Univ., Applied Physics Lab., without invoking a finite difference approximation requiring

Johns Hopkins Rd., Laurel, MD 20707, J. Acoust. a second eigenmode calculation. The reciprocity relation is

Soc. Amer., 2 (3), pp 810-812 (Mar 1983) 3 figs, employed in a derivation of the normal mode group velocity8 refs and attenuation coefficient. The group velocity thus celcu-

iated is more accurate than a comparable finite differenceapproximation. Arbitrarily arranged layers of solid and

Key Words: Underwater sound fluid media are considered.

A caution is given to the users of range-dependent modelsthat utilize single ocean sound-speed profiles for discreterange intervals. It is shown that, if new profiles are not inputevery few kilometers, the effect of the discontinuities in the 83-1408ocean may produce erroneous results. An example illustrates

potential errors of as much as 18 dB using the ParabolicEquation Method to compute propagation through a Gulf Fsisd InterfaceStream ring. It is argued that range interpolation routines J.N. Tj~tta and S. Tj tta

69

"i .

I I i n nn nall ld~i lf -k .i . .iln l l unm ... . . " -_. " .*• -

Dept. of Mathematics, Univ. of Bergen, Bergen, Nor- This report provides a detailed presentation and critique of away, J. Acoust. Soc. Amer., 73 (3), pp 826-834 model used to characterize the surface ground motion(Mar 1983) 17 figs, 13 refs following a contained, spelling underground nuclear explo-

sion intended for calculation of the resulting atmosphericacoustic pulse. Some examples of ts use are included. Some

Key Words: Underwater sound, Pulse excitation discussion of the general approach of ground motion modelparameter extraction, not dependent on the specific model,

The transmission of an acoustic pulse with a plane front at a is also presented.two-fluid interface is considered. An exact solution is ob-tained and several properties are derived. Numerical examplesare given, showing patterns of the transmitted signal fordifferent pulse shapes and incident angles. It appears thatpenetration at angles above the critical incidence (accordingto Snell's Law) is possible, depending on how the incident

pulse is shaped.83-1411Monotonic and Cyclic Consitutive Law for ConcreteM.N. Fard is, B. Alibe, and J.L. TassoulasMassachusetts Inst. of Tech., Cambridge, MA, ASCE

83.1409 J. Engrg. Mech., 109 (2), pp 516-536 (Apr 1983)Response of Underwater Structures to Convective 11 figs, 38 refsComponent of Flow Noie.K.L. Chandiramani Key Words: Concretes, Cyclic loading, Constitutive equationsBolt Beranek and Newman, Inc., 10 Moulton St.,Cambridge, MA 02138, J. Acoust. Soc. Amer., 73 A simple time-independent, mathematical model is proposed

for the monotonic and cyclic behavior of concrete under(3), pp 835-839 (Mar 1983) 6 f igs, 5 refsmutxilsrscodin. multioxial stress conditions.-.-

Key Words: Underwater structures, Plates, Sound trans-mission

Convective component of flow noise (for example, a turbu-lent boundary layer) is characterized by length scales of theorder U/f, where U is the mean flow speed and f is the fre-quency. Nonresonent response of underwater structures 83-1412to the convective component of flow noise is often of inter- Predtions of CoUpse Modes in Grub-Impaledest. An exact theory of transmission of sound across an iso- of.p-dnCd aetropic flat plate, involving longitudinal and shear waves, is Structures Using a Finite-Element, Modal Energy,modified so as to apply at high, convective wavenumbers. ApproachClosed form results are presented. KJ. Saczalski

Northern Arizona Univ., College of Engrg. and Tech.,Flagstaff, AZ 86011, Intl. Modal Analysis Conf.,Proc. 1st, Nov 8-10, 1982, Orlando, FL. Spons.

SHOCK EXCITATION Union College, Schenectady, NY, pp 160-166, 7figs, 2 tables, 8 refs

83-1410 Key Words: Crshworthiness, Collision research (automo-tive), Crash research laircrSft), Modal analysis, Finite element

Analytic Model for Surface Ground Motion with techniqueSpi Induced by Underground Nudear TestsD.H. MacQueen A modMi technique employing linear system eigenvalues and

Lawrence Livermore National Lab., CA, Rept. No. elgenvectors, In conjunction with finite-element strainUCRL-53266, 36 pp (Apr 1982) energy density distributions and average internal reaction

loads, is utilized with empirically modified yield and buck-DE82016783 ling criteria to Identify nonlinear collapse mode patterns

in crash-impacted structural systems. This paper outlines

Key Words: Underground explosions, Nuclear explosions, the technique and compares results with preliminary investi-Sound generation gations of crash-impacted frame type structures.

70

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V . . , ' . . - - . - . - - - . . ... - . . . . . . - * -- - . . . . - . ..

.Y -

83-1413 Univ. of Vilnius, Vilnius, Lithuanian SSR, Vibro-P rotectimg PCBa from Shock technika,A (34), pp 73-78 (1981) 4 refsD.S. Steinberg (In Russian)Mech. Engrg. Dept., Litton Guidance and ControlSystems, Woodland Hills, CA, Mach. Des., 5 (5), Key Words: Vibration measurement, Time-dependent param-

pp 189-191 (Mar 10, 1983) 5 figs eters

The simple exact expressions of Fourier-coefficients of aKey Words: Circuit boards, Shock resistant design, Design signal and its phase-modulation, due to the arbitrary pen-Stechniques odical fluctuation of tape velocity during recording, are

obtained. The formulas contain no reverse functions. SeveralA design procedure to reduce mechanical shock in electronic exmlsaeiutred

* equipment is described. By designing the printed circuit

boards to a resonant frequency one-half that of the chassis

provides some isolation from shock induced vibration. De-'4 signing to this reverse octave rule keeps chassis vibration

from being amplified. This technique also aliows MECHANICAL PROPERTIESmounting brackets to better withstand the smell movementsthat occur with high chassis resonant frequency.

DAMPINGVIBRATION EXCITATION (Also see Not 1324,1388)

83-1414 83-1416Dynamical Relation between Non-Conservative Sys- Constrained Layer Damping as a Vibration and Noisetan and Fish Propuluon Mechanian Control MethodT. Iwatsubo B. JohanssonThe Faculty of Engrg., Kobe Univ., Rokko, Nada, Antiphon AB, Sweden, Dynamic Vibration IsolationKobe, Japan, Bull. JSME, 26 (212), pp 283-290 and Absorption Conf., Sept 8, 1982, Univ. of South-(Feb 1983) 23 figs, 13refs ampton. Spons. Chartered Mechanical Engineer,

Instn. of Mech. Engineers, pp 87-108, 30 figs, 7 refsKey Words: Self-excited vibrn.tions, Energy conversion,Propulsion systems Key Words: Layered damping, Vibration control, Noise

reductionThis paper is concerned with the character of vibration afterthe self excited vibration has occurred and with the relation Information is presented on the different damping techniquesof energy conversion mechanism between the fish propulsion and the properties of damping materials showing how theand the instability problems which occur in non-selfadjoint modulus of elasticity, sheer modulus, and loss factors aresystem. Block diagrams of these two behaviors are shown. affected by temperature and frequency. Explanation is madeThe self excited vibration of a column subjected to tangential of the properties of a constrained layer system and how theforce, tubular cantilever conveying fluid, flutter of the wing, loss factor varies with unsymmetric and symmetric configure-and oil whip of rotor system are investigated for eigenvalues, tions and the thickness of the constrained layer compound.phase difference, and energy by means of two degree-of-freedom models. In the fish propulsion system, the vibration

mode of a fish is analyzed from the viewpoint of phase angle - "

between the deflection and attack angle. Then the relation 8-1,17of energy conversion and the vibration mode is discussed.

The Use of Damping and Cancellation Devices toReduce Punch Press VibrationsC. Stimpson """

Univ. of Southampton, UK, Dynamic Vibration83-1415 Isolation and Absorption Conf., Sept 8, 1982, Univ.The Tine-Distortion of Signal Due to the Periodical of Southampton. Spons. Chartered MechanicalFluctuationof Tape Velocity during Recording Engineer, Instn. of Mech. Engineers, pp 1-6, 7 figs,T. Zemaitis, A. Seilius, and A. Graiulevi6 ius 3 refs

71

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_ , ~ - - . . . . ] , , , . , " ' " • - . " - _ _ ; - . . .• . . " . . .

Key Words: Dampers. Semi-active isolation, Machine tools, A dynamic mechanical analysis procedure, which measuresVibration control, Noise reduction the viscoelastic properties (modulus and damping) of a

material as a function of time and temperature, is considered

During a blanking or piercing operation on a power press, for application in several types of composite& They includehigh levels of structural vibration can occur as the frame classical glass/epoxy systems (cured and uncured), continu-

springs back following the very rapid release of strain energy ous-filament graphite/epoxy advanced composites (cured andas the work-piece material fractures. The ensuing transient uncured), aramid-fabric-reinforcd epoxy, and a chopped-vibration is a major source of noise and often leads to high glass-reinforced thermoplastic polyester.

rates of press wear. Smoothing the very rapid unloading ofthe structure is an effective form of noise control which can

also give extended press life. The paper reviews currentdevices and reports on measurements made on a 25 ton C '10

frame press and a 200 ton straight-sided press.

83-1420FATIGUE On Path-Independent Integrals and Fracture Criteria

in Non-Linear Fracture DynamicsC. Ouyang

83-1418 Dept. of Mathematics, Fudan Univ., Shanghai, China,Tank Car Head Shield Fatigue Evaluation Intl. J. Nonlin. Mech., 18 (1), pp 79-86 (1983) 5W.F. Jackson and C.E. Anderson, Jr. figs, 3 refsBallistic Res. Lab., Army Armament Res. and D-v.Command, Aberdeen Proving Ground, MD, Rept. Key Words: Fracture propertiesNo. ARBRL-MR-03209, SBI-AD-F300 119, 44 pp(Nov1982) A new path-independent integral for nonlinear fracture

dynamics is proposed. First the elastic case is examined,AD-A121 606AD-A11606then the elasto-plastic case. A relation between the new

integral and the crack extension force in fracture dynamics

Key Words: Fatigue tests, Railroad cars, Tank cars is presented.

An experimental program was performed to evaluate thefatigue damage sensitivity of a railroad tank car heed shield,required by federal regulation HM-144 in the transport ofcertain hazardous materials. The test procedures and data

collected are documented. Analysis of the data obtainedfrom these tests showed that currently applicable head shieldspecifications were met.

83-1421

Numerical Problems of Nonlinear StablAity Analysisof Elastic Structures

ELASTICITY AND PLASTICITY Z. WaszczyszynTechnical Univ. of Cracow, ul. Warszawska 24, 31-455 Krakow, Poland, Computers Struc., 17 (1), pp13-24 (1983) 11 figs, 45 refs

83-1419Dynamic Mechanical Analysis Assures Composite Key Words: Stability, Elastic systems, Finite element tech-

Quality nique

P.S. GillClinical & Instrument Systems Div., DuPont Co., Basic definitions and relations for stability of elastic discrete

Wilmington, DE, Indus. Res. & Dev., 25 (3), pp 104- systems under one-parameter conservative loads are brieflypresented. On the basis of the potential energy function the

107 (Mar 1983) 3 figs, 6 refs Incremental FEM equations are derived. Various methods

of computation of paths of equilibrium are discussed. Differ-

Key Words: Composite materials, Viscoelastic properties, ant stability criteria for computation of critical points areTime-dependent parameters, Temperature effects, Variable discussed. Tracing of a postbifurcation path of equilibrium

material properties Is pointed out.

72

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,..... ........ ........... -. ,. . ..-...........-...:..:,,:.. .. * . * . ... - ... ,- , :. *., , : :, .. , ' i , i ; .. . . . - -

...- -- _

PER MENTATION the back-to-back accelerometer a greeter potential as anEXPERIM NTAT O accurate, repeatable, and stable vibration standard. Recentwork in this area is presented along with a description of atypical back-to-back transducer calibration. 0

MEASUREMENT AND ANALYSIS

(Also see Nos. 1281,1296,1297,1298,1313,1314,1315,1317,1401,1419,1460,1462,1463,1464,1481,1496)

83.1424A New Frequency for Piezoelectric Reaonator Mea-

83-1422 surement

luterferometric Phase Calibration of Vibration Pick. W.H. Horton and R.C. Smythe

upS IEEE, Proc., 71 (2), pp 280-282 (Feb 1983) 2 figs,M.R. Serbyn 7 refsNational Bureau of Standards, Washington, D.C.

20234, Intl. Modal Analysis Conf., Proc. 1st, Nov 8- Key Words: Piezoelectric transducers, Resonators. Vibration

10, 1982, Orlando, F L. Spons. Union College, Schen- measurement, Measuring instruments

ectady, NY, pp 223-229, 7 figs, 7 ref s A new frequency associated with the reflection coefficient

of a piezoelectric resonator is described which is independentKey Words: Vibration measurement, Measuring instruments, of the length of the uniform transmission line connecting theAccelerometers, Sensitivity analysis, Calibrating resonator with the measurement system. The frequency is

also independent of the resonator motional resistance andAn absolute method for measuring the phase component of has other properties which make it potentially useful forpickup sensitivity is described. The phase calibration is in special measurement purposes.terms of the time interval between zero crossings and can beperformed along with magnitude calibration on an automatedMichelson interferomater. The procedure is simplest whenthe peak vibrational displacement is between about 30 and120 nm.

83-1425Multicomponent Dynamometera Using Quartz Crys-tals as Sening Elements

83-1423 K.H. MartiniThe Use of Back4o-Back Aecelerometesas Precision Kistler Instrumente AG, Switzerland, ISA, Trans.,Vibration Standards 22 (1), pp 35-46 (1983) 11 figs, 21 refsB.F. PayneNational Bureau of Standards, Washington, D.C. Key Words: Dynamometers, Quartz crystals. Transducers20234, Intl, Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL. Spons. Union College, Schen- The unique characteristics of quartz crystal make it posibleectady, NY, pp 212-215, 7 figs, 2 refs to resoive any force acting on a quartz sensing element (3-

component transducer) into three orthogonal componentsdirectly. A multicomponent dynamometer is usually com-

Key Words: Accelerometers, Vibration measurement, Me- posed of typically four elements that wre sandwiched be-suring Instruments, Calibrating tween two plates. Forces and moments are obtained by

_ adding and subtracting Individual force components mee-Precision vibration measurements depend on accurate and sured by the sensing elements involved. By evaluating therepeatable calibration methods. Standardization of calibre- individual force outputs It is also possible under certaintion test equipment and measurement techniques ensures conditions to calculate the coordinates of the point of forcemore accurate and repeatable measurements. The use of application and the free movement (torque) around a vertical

• ' back-to-beck accelerometers as laboratory standards has axis. The main characteristics of quartz and strain gagsbecome widespread. However, this use has been somewhat dynamometers are compared; advantages and disadvantageslimited because of Inadequate calibration methods. Recent are discussed. Reference is made to successful applications,developments in improved calibration methods has given and respective publications are cited.

73...... ...... ......

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83.1426 FL. Spons. Union College, Schenectady, NY, ppThe Digital Approach to Engineering Meamrement - ix-xiiiPart IP. Colwill and M. Caudell Key Words: Modal analysis, ReviewsData Laboratories Ltd., Chartered Mech. Engr., 30(3), pp 51-52 (Mar 1983) 4 figs This paper is brief review of the material which was covered

in the keynote speech given at the first International ModalAnalysis Conference held at Orlando, Florida, November 8-

Key Words: Measuring instruments, Computer-aided tech- 10, 1982.niques, Digital techniques

This article aims to present the capability of the transientwaveform recorder in mechanical engineering measurement.The first part examines the instrument's main features, withspecial attention to its connection with a computer via an 83-1429interface; the second part discusses the digital measurement impulsle Testing Validation of a Mathematical Modelof physical signals and easy-to-use measurement systems J.H. Bondbased upon the transient waveform recorder, and concludes Corporate Consulting and Development Co., Ltd.,with a look at some of the applications of the instrument. alCRaleigh, NC, Intl. Modal Analysis Conf., Proc. 1st, ,o:

Nov 8-10, 1982, Orlando, FL. Spons. Union College,Schenectady, NY, pp 238-244, 5 figs, 2 tables, 8 refs

Key Words: Impulse testing, Testing techniques, Naturalfrequencies, Mode shapes

83.1427A Correlation Coefficient for Modal Vector Analysis Impulse testing is a means by which natural frequencies andR.J. Allemang and D.L. Brown mode shapes can be determined experimentally. The process

involves determining the transfer function, or the ratio ofMech. and Industrial Engrg., Univ. of Cincinnati, a measured response of a structure to a specific input in theCincinnati, OH 45221, Intl. Modal Analysis Conf., frequency domain. Natural frequencies and mode shapes canProc. 1st, Nov 8-10, 1982, Orlando, FL. Spans. be scaled from the transfer function results. When impulseUnion College, Schenectady, NY, pp 110-116, 11 testing was used to validate a mathematical analysis of arefs cantilever beam, results showed that the rigid boundary

condition used in the mathematical model was stiffer thanthe experimental results indicated. By relaxing the boundary

Key Words: Modal analysis, Correlation techniques condition In the mathematical model of the structural prob-lem, the analytically determined frequencies and modeMultiple, independent modal vector estimates may be gener- shapes were found to correspond with the experimentally

ated whenever multiple rows or columns of the frequency determined results.response function matrix are available. These Independentestimates of the same modal vector need to be processedInto a single best estimate of that particular modal vector.The development of the concept of consistency of model

%" vectors, evaluated through the use of the model assuranceand modal scale factor, is useful in computing a best estimate 83-1430of the modal vector and useful in understanding the errors An Algorithm for Hidden Line Estimation of Obliqueamong separate estimates of the same model vector. Projection

J. SatoIntl. Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,Orlando, FL. Spons. Union College, Schenectady,NY, pp 118-122, 2 refs

0-1428 Key Words: Model analysis, AlgorithmsModal Analyss- Psit, Present and FutureD.L. Brown An effective algorithm for outline detection, drawing and

hidden line elimination of three-dimensional objects usingUniv. of Cincinnati, Cincinnati, OH, Intl. Modal an XY-plot is dealt with in this paper. Illustrative examplesAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, are given along with results of the oblique projection.

74

... ....... .. ....... •:. .: , .. . . .... ...: , ,. ... ., ..-. . . . . . .. . .. ,.-. .

* - --- -.-- .-- - - - -.- '~'-% *.-.•x -. o

- . --- ---- ---,- - ". - .,-

0.%1431 Key Words: Modal aaolysis, Time-dependent parameters,BscConsieration of Experimental Moda Analys-i- Nonlinear systems .-

N. Okubo and S. Honda Whenever the relationship between two quantities is anythingChuo Univ., Tokyo, Japan, Intl. Modal Analysis other then a straight line, time variations of one quantity at

Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL. one set of frequencies will result in time variations of theSpons. Union College, Schenectady, NY, pp 130- other quantity at a different set of frequencies. Nonlinear

135, 16 figs, 6 refs systems are frequency-creative. Some of the consequencesof the frequency-creative ability of nonlinear systems onthe design of measuring systems will be developed in this

Key Words: Modal analysis, Impact tests paper and supported by examples.

For the application of impact excitation to a mechanicalstructure which has a nonlinear element, a numerical simu-lation based on mathematical models and also a test of dy- -1

namic behavior of the structure, are carried out to analyzethe frequency response function. A discussion is made on 83-1434current techniques for the extraction of natural frequency An Iexpene. Microcomputer-Baed, Modal Analy-damping ratio from measured data and necessary considera-tions to improve them are given. -;- and Testing System

M.S. Darlow, E. Willstaedt, and S.A. MarquissDept. of Mech. Engrg., Aeronautical Engrg. andMechanics, Rensselaer Polytechnic Inst., Troy, NY,Intl. Modal Analysis Conf., Proc. 1st, Nov 8-10,1982, Orlando, FL. Spons. Union College, Schenec-

83-432 tady, NY, pp 245-251,3 figs, 19 refsOn the Determination and Use of Reidual Flexi.hilitica, Inertia Restral lintsad Rigid-Body Modes Key Words: Modal analysis, Impulse testing, Finite element

M.A. Lamontia technique

E.I. DuPont de Nemours & Co., Inc., Wilmington,DE, Intl. Modal Analysis Conf., Proc. 1 st, Nov 8-10, An integrated modal analysis and testing system is described

1982, Orlando, FL. Spons. Union College, Schenec- in this paper. This system is built around a personal micro-computer and is relatively inexpensive. The computer is :09tady, NY, pp 153-159, 9 figs, 3 refs capable of performing sophisticated analysis with substantialquantities of data. Of particular interest here are an inter-

Kay Words: Model analysis, Residual flexibility effects, active finite element analysis package and a general transferInertia restraints, Rigid-body modes matrix analysis package.

For some structures, model analysis by itself is inadequatefor creating a structural model. Rather, high-frequencyresidual flexibility effects and low-frequency inertia restraintsor the equivalent rigid-body modes must be found. Theimportance of these residual effects Is demonstrated with 83-1435real structures. Methods of computing the terms for both Combining Analytical and Experknental Modalsymmetric and asymmetric structures are outlined. Analysis for Effective Structural Dynamical Model-

lingT.G. Pal and R.A. SchmidtbergNicolet Scientific Corp., Northvale, NJ, Intl. ModalAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,

83-1433 FL. Spons, Union College, Schenectady, NY, pp 265-Dynamic Measurements on and with Non-Linear 271,3 figs, 2 refsSystems. Problems ad ApproaehesP.K. Stein Key Words: Model analysis, Finite element technique

Stein Engineering Services, Inc., Phoenix, AZ, Intl.This paper reviews the basic principles of both analytical- Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982, and experimental model analysis, highlighting the strengths

"6 Orlando, FL. Spons. Union College, Schenectady, and weaknesses of each technique. Some guidelines forNY, pp 358-389, 23 figs, 31 refs selecting the appropriate analysis procedure are also pr-

75

T-~~ 7.7- 77-7.

tnted. Examples are offered from a recently developed 83-1438mini-computer system, which provides both experimental Sei mic Qulification Using Digital Signall Processing/and analytical (finite element method) modal analysis caw- Modl Teating ad Finte Element Techique.bilities.MoaTetnanFiieEeetTcipw3iaJ.B. Steedman and A. Edelstein

Structural Dynamica Lab., Fullerton, CA, Intl. ModalAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,FL. Spons. Union College, Schenectady, NY, pp 622-

83-1436 629, 5 figs, 2 tablesGlobal Fittinl, an Efficient Method of ExperimentalModal Amallyaaof Mechaiceal Systems Key Words: Equipment response, Signal processing tech-

J.G. Gimenez and L.1. Carrascosa niques, Modal tests, Finite element technique, Seismic

Escuela Tecnica Superior de Ingenieros Industriales, analysis

Universidad de Navarra, San Sebastian, Spain, Intl. A systematic procedure in which digital signal processing,Modal Analysis Conf., Proc. 1st, Nov B-10, 1982, modal testing and finite element techniques can be used to . -Orlando, FL. Spons. Union College, Schenectady, seismically qualify Class 1E equipment for use in nuclear

NY, pp 528-533, 5 figs, 1 table, 7 refs generating stations is presented. A new method was alsodeveloped, in which measured transmissibility functions andFourier transformation techniques were combined to com-

Key Words: Modal analysis, Global fitting method, Viscous pute instrument response spectra.damping

A method is proposed for the experimental modal analysisof mechanical systems based on the simultaneous treatment 83-1439of all available transfer functions. Although this method may A New Complex Exponential Frequency Domainbe used for other types of damping, it has been codified Technique for Analyzing Dynamic Response Dataunder the hypothesis of non-proportional viscous damping L.W. Schmerrwith complex natural modes of vibration. It is based on thetheoretical curve fitting of the experimental transfer func- Dept. of Engrg. Science and Mechanics and thetion. The authors describe various applications to practical Engrg. Res. Inst., Iowa State Univ., Ames, IA 50011,problems where other methods have shown serious limita- Intl. Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,tions. Orlando, FL. Spons. Union College, Schenectady,

NY, pp 183-186, 12 refs

Key Words: Frequency domain method, Time domain math-83-1437 od, Vibration tests, Testing techniques, Modal analysis

Dynamics of Periodic Struturee by Means of Trans- Accurate measurements of the dynamic characteristics of

fer Matrices structures and materials are becoming increasingly important

H. Pastorel, M. Massoud, and J.G. Beliveau in modern analysis and design procedures A crucial factorMark Hot Industries, Longueuil, Quebec, Canada, in the use of such measurements Is the ability to obtain

important physical parameters such as natural frequencies,Intl. Modal Analysis Conf., Proc. 1st, Nov 8-10, damping values, etc. directly from the dynamic test data.

1982, Orlando, FL. Spons. Union College, Schenec- Recently, two new methods, Ibrahim's Time Domain Modal

tady, NY, pp 489-494,6 figs, 1 table, 12 refs Identification Algorithm and the Single-Station Time-Domain 1AVibration Testing Technique, have proven to be particularlysuccessful in extracting the natural frequencies and associ-

KyWords: Periodic structures, Transfer matrix method,Key ated damping ratios from the free vibration time response .-Resonant frequencies, Mode shapes of a structure. This paper describes the development of a

frequency-domain version of these methods, which may haveDynamic characteristics of periodic (repetitive) structures, certain advantages with respect to ampling and filtering overmay be obtained from their transfer matrices. In this paper,

thes matrices are calculated without successive mutiplica- the time-domain algorithms, and its use for a simple system.

tion of identical elementary transfer matrices of substructureor the calctu;ation of their eigenvalues and elgenvectors. Theanalysis allows the effects of external forces and moments 83-1440acting on the structure to be Included, The procedure re-quires les memory and allows greater accuracy in the results Finite Element Model Validation Via Modal Testingthan existing procedureL J.B. Stimpson and D.T. Griffith

P,, 76

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. -. - ., .,. , .. .. ,2. . .- 2. . ,- : -. . .: . :. . . . :, -. . : - :. .. ::. . : 2 .: 2. - , . .: 2 : . :, : : : :, . , ... • . . . " -..

V °

" " ° ° " " ', .' ,' . .. , / . '. % . . -'. ", - . . . - . - - .. - . ", , • " , , - , , ' - " ' , , - - '- : -' - _,.--- - - - - - . . . . . . . ..,. . %o ..... .. . .. °- . "." . ., .".a. ,& .'k ts~,; ;a. . x=~ .

. , .

Raytheon Co., Portsmouth, RI, Intl. Modal Analysis 1982, Orlando, FL. Spons. Union College, Schenec-Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL. tady, NY, pp 436-442, 4 figs, 10 refsSpons. Union College, Schenectady, NY, pp 456-461,8 figs, 3 tables Key Words: Mode modification method, Finite element tech-

nique .'

Key Words: Modal analysis, Modal tests, Finite elementtehnonce avldmd oftescA method is presented for predicting the effect of design

changes on system eigenvalues The method uses a finite

Finite element analysis can be an extremely effective design element preprocessor to find derivatives of the mass and .,stiffness matrices, and computationally efficient techniques

toonelementi model inprdtn the stut resoantd freexperimentally validated model increases the confidence to find aigenvector derivatives. Example problems illustratelevel in the analysis of proposed design changes. This paper the strength and limitations of the technique.. -

shows how modal testing was used to improve the accuracyof a finite element model in predicting the resonant fre- .I

quencies and corresponding mode shapes of a test fixture.Two different mounting configurations were studied.

83-1443Modal Control of Vibrating SystemsA.N. Andry, Jr., E.Y. Shapiro, and J.C. Chung

83-1441 Lockheed California Co., Burbank, CA, Intl. ModalExperimental Modal Analysis, Structural MOdifiea- Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,Exeimna Spons. Unionis Structura ScenctdyiNfpi..a-.tions and FEM Analysis - Combining Forces on a FL. Spons. Union College, Schenectady, NY, pp

Desktop Computer 430-435, 10 refs

K.A. Ramsey and A. FirminStructural Measurement Systems, Intl. Modal Analy- Key Words: Mode modification method, Active control

sis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL. An active eigenstructure modification method and the theorySpons. Union College, Schenectady, NY, pp 443-455, behind It is described. Basically, the method utilizes the13 figs, 2 tables, 4 refs response of the system in feedback in order to modify the -

eigenvalues and eigenvectors of the system. "*

Key Words; Modal analysis, Modal tests, Finite element tech- en sd n t fh tnique, Mode modification method

This paper discusses structural dynamics technology interms of its two most important parts; the experimentalportion and the analytical portion. It discusses how experi- 83-1444mental and analytical methods are used to solve noise andvibration problems and how they may be used together for System Modeling and Modification Via Modal Analy-even greater benefit. It also shows how structural modifi- siscation techniques are used asa complement to both methods Y.W. Lukand how all of the toolsmay be ombined on an inexpensive Zonic Corp., Milford, OH 45150, Intl. Modal Analysisdesktop computer. The paper concludes with an example Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL.showing how experimental modal analysis, structural dy-namics modification and finite element analysis were used Spons. Union College, Schenectady, NY, pp 423-429,to analyze a test structure. 1 table, 18 refs

Key Words: Modal analysis, Mode modification method

This paper deals with the different ways of modifying aprototype structure analytically. This modified model is

8-1442 used to predict the new dynamic characteristics of the

An Efficient Method for Predicting the Dynamic modified structure resulting from changes in its mass, stiff-Effects of Rolede ness, or damping properties. There are three ways that

modifications can be made: in the physical coordinatesM.N. Rizai and J.E. Bernard model; in both the physical and modal coordinates models;Intl. Modal Analysis Conf., Proc. 1st, Nov 8-10, and in the modal coordinates model.

77

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-7. . . . .-. . .

-Ae

83-1445 Univ. of Missouri-Columbia/Kansas City, Indepen-. A Structural Modification Procedure Using Complex dence, MO 64050, Exptl. Mech., 23 (1), pp 89-98

Modes (Mar 1983) 10 figs, 27 refsJ. O'Callahan and P. Avitabile 0Univ. of Lowell, Lowell, Massachusetts, Intl. Modal Key Words: Cracked media, Transient response, Pulse excite-

Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, tion, Plates, Impact tests, Interferometric techniques, Testing

FL. Spons. Union College, Schenectady, NY, pp techniques

418-422, 1 fig, 7 refs This experimental investigation studies the opening displace- ...

ment of a central electromachined slot in a thin aluminumKey Words: Mode modification method, Model tests, Experi- plate subjected to an elastic tensile pulse. The tensile pulsemental test data, Finite element technique was generated by an impact apparatus, and in-plane displace-

ments were measured by interferometric techniques. Coi-A general procedure is presented that performs structural parison with existing analytical and finite-element solutionsmodifications of modal data from either a finite element was good for short times.analysis using the undamped or damped (complex) modaldata or usigg modal data obtained from an experimentalmodal analysis. With this modal data, a projection of physicalchanges of mass, damping, and stiffness matrices are formedin modal coordinates. A complex eigensolution is performed 83.1"-to extract the modal matrix that reflects the system physical 83-1448

changes. Dynamic Wheel-Testing Rig (Fahrdynamischer Rider. " "prAfstand)S. Angerer and H. NaundorfAutomobiltech. Z., 85 (2), pp 71-76 (Feb 1983)8 figs, 14 refs

83-1446 (In German)A Study of impulse Excitation and the Modal Param-

eters Identifwation for Mechanical Structure Key Words: Dynamic tests, Test facilities, Wheels, VehicleYongfang Zhou, Yueming Sun, Naiyan Lu, Yaodong wheels

Cheng, and Zhongfang Tong The dynamic wheel-testing rig developed by BMW has been

Zheiang Univ., Hangzhou, Zhejiang, China, Intl. designed in such a way as to reproduce actual road condi-

Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982, tions, thus making it possible to simulate In the laboratory

Orlando, FL. Spons. Union College, Schenectady, the complex stresses involved. The article gives an account

NY, pp 350-357, 12 figs, 3 refs of the development and construction of the test rig.

Key Words: Modal analysis, Impulse testing, Parameteridentification technique

A procedure consisting of impulse excitation and 6%-VntifI- 83-1449-J cation of structural modal parameters is presented. Through Airfoil Vibration Test Apparatus

Fast Fourier Transform of force and response signals, cross-spectral and auto-spectr8l density can be obtained and the C.B/Joneratio sWws the transfer function. Dept. of the Air Force, Washington, D.C., U.S. Patent

4-350 043, 7 pp (Sept 1982)

Key Words: Test equipment and instrumentation, Vibration

DYNAMIC TESTStes(Also - No. 1316) This patent describes an apparatus for inducing high fre-

quency out-of-phase, vibrations in adjacent span-wise panel

portions of a plate type structure, such as an airfoil blade

83;1447 of a gas turbine engine. The apparatus includes a novel .Tranient Reaonw of a Central Crack to a Tensle bifurcated duct for conducting and directing two out-of-

phase streams of gaseous flow, and a uniquely structuredpwsle air chopper which generates the two out-of-phase gaseousA.A. Sukere and W.N. Sharpe, Jr. streams.

78

All

83-1450 Key Words: Vibration tests, Test facilities, Hydraulic sys-

Vibrational Modes of Plates and Cymbals tems, Vibrators (machinery), Machine toolsT.D. Rossing, R.B. Shepherd, R.W. Peterson, and"

C.A. Anderson The dynamic characteristics of a simple new hydraulic

Northern Illinois Univ., DeKaib, IL, Intl. Modal vibrator are investigated theoretically and experimentally.The main transfer functions of the vibrator; i.e., source

Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, impedances and force transmissibility, and energy relation-FL. Spons. Union College, Schenectady, NY, pp 88- ships are derived. Theoretical calculations are compared

94, 12 figs, 1 table, 3 refs with experimental results.

Key Words: Musical instruments, Vibration tests, Testingtechniques

83-1453A study is made of the vibrational modes of percussion Random Vibration Testing of a Single Test item withmusical instruments by several techniques, including Chladni a Multiple Input Control Systempatterns, time-averaging holographic interferometry, digital D.0 Smallwoodmodal analysis, and direct probing of the near-field soundwith a microphone. These techniques are described, and Sandia National Labs., Albuquerque, NM, Rept. No.examples are given of their application to circular plates and SAND-81-201 1C, CONF-820411-1,8 pp (1981)cymbals. DE82005687

Key Words: Random vibration, Vibration tests, Shakers,

Control equipment, Algorithms

This paper develops an algorithm for a multiple shaker*83-1451 random vibration control system. The system is designed

*Dynamic Analysis Techniques for Aluminm-Filled for several shakers driving a single test item with full cross-

Epoxy Models coupling control. The method allows for cross-coupled me-W.R. Shapton and R.N. Lund chanical systems with partially coherent control points.

Michigan Technological Univ., Houghton, MI 49931,Intl. Modal Analysis Conf., Proc. 1st, Nov 8-10,1982, Orlando, FL. Spons. Union College, Schenec- 83-1454tady, NY, pp 208-211,4 figs, 1 table Random Vibration Control System for Testing a

Single Test Item with Multiple InputsKey Words: Testing techniques, Modal analysis, Test models D.O. SmallwoodThis paper discusses the use of aluminum-filled epoxy struc- Sandia National Labs., Albuquerque, NM, Rept. No.tural models for dynamic modal analysis. Model ease of SAND-82-1631C, CONF-821019-1, 7 pp (1982)preparation and evaluation indicate that aluminum-filled DE82018973epoxy can be extended from static stress analysis to dynamicanalysis. Test procedures are investigated and results are . "d Rrdiscussed. Key Words: Random vibration, Vibration tests, Shakers,

Control equipment

This paper describes a multiple shaker control system devel-oped for driving a single test item with random excitation.The system allows for cross-coupled mechanical systems withpartially coherent control F,_ nts, The system uses time-

83-1452 domain randomization to generate the continuous Gaussian

The Dynamic Characteristics of a New Hydraulic drive signals.

VibraiorJiaqiang Pan, Yaodong Cheng, Zhongfang Tong, andYueming SunZhejiang Univ., Hangzhou, Zhejiang, China, Intl. 83-1455Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982, A Generalized Approach to the Transient ResponseOrlando, FL. Spons. Union College, Schenectady, of Servovalve Controlled Asymmetric Actuators andNY, pp 230-237, 11 figs, 4 refs Its Practical Realization

79

,, *,% i,',...=. . .............. . .. .. - .. . . . • . ,', • • ,., • .. ' ".. ".. . . ".. . , . . , " . ". .

J. Watton This paper describes new model test methods that are useful

University College, Cardiff, Wales, ASME Paper No. in obtaining a modal model with accuracy suitable foranalytical work. Techniques to verify that the modal modelaccurately represents the test item are reviewed. Also de-scribed are the analytical methods that directly use the test

Key Words: Test equipment and instrumentation, Transient data. A case history is presented documenting the applica-

response, Fatigue life, Ground vehicles, Aircraft tion of the suggested methods to solving a severe vibration

problem in a large process machine. Initial test results, ana-The transient performance of a servovelve controlled asym- iytical modifications and correlation of analysis with themetric actuator of the type used for fatigue testing of vehicle modified system are given.and airframe systems is assessed both analytically and experi-mentally.

BALANCING

SCALING AND MODELING

83-145883-1456 Does a Microprocessor System Help in a Univeral.Model Studies of Acoustic Propagation over Finite Balancing Machine? (Niitzt ein Mikroprozessor-Impedance Ground System bei einer Universalauswuchmaschine?)D.A. Hutchins, H.W. Jones, and L.T. Russell H. SchneiderPhysics Dept., Dalhousie Univ., Halifax, Nova Scotia, Feinwerktechnik & Messtechnik, 91 (1), pp 25-27Canada, Acustica, 52 (3), pp 169-178 (Feb 1983) (1983) 6 figs, 1 table18 figs, 18 refs (In German)

Key Words: Scaling, Elastic waves, Sound propagation, Key Words: Balancing machines, Microprocessors (com-Acoustic impedance puters)

A scale modeling technique is described, which is capable A detailed look into the tasks of a universal balancing me-of predicting sound levels following propagation over flat chine shows that the use of a microprocessor system can beground of finite impedance. Experimental model data has purposeful if the specific situation and the required dialoguebeen compared favorably to both outdoor measurements, between the operator and the measuring device are accountedobtained in a neutral atmosphere or at short ranges, and to for. Operating and display elements are also investigated.theory with flow resistivity as the parameter.

DIAGNOSTICS MONITOR ING

83-1457 83-1459Troubledooting In-Plant Equipment Using Combined Measurement of BaH Bearing VibrationsTest and A lymiu L. Geller

G.F. Mutch and R. Russell Vibrotechnika, 4(34), pp 7-11 (1981) 6 refsGE CAE International, Intl. Modal Analysis Conf., (In Russian)Proc. 1st, Nov 8-10, 1982, Orlando, FL. Spons.Union College, Schenectady, NY, pp 252-258, 18 Key Words: Bearings, Ball bearings, Diagnostic techniques

figs, 1 ref A method for the control of low frequency vibration of

small ball bearings is described. It is shown that bell bearing

Key Words: Diagnostic techniques, Modal tests, Industrial quality can be determined from its vibration characteristics

facilities, Equipment response by measuring the rectification signal of vibration velocity.

- -,7

- - . .-.. . . . . . . . . . . .. . . . . . . . .. -.. .

. ... . . .. . . . . . . . ... 1

, -o °% .'- .' % , * - - , . . . . . * . . .- - 0. • , .o • ° , • . - ,, ' .. -, . . .•.

" ; ' - " " ' " -" ' ' " ' " " " ' " ' " " " " " '.. . . .. . . . " - .' .. . . . . . ..* , " "." * - " - - • • " , " - -. . ' " " r , "

7 - *-

intervals. Results are shown to correspond closely withANALYSIS AND DESIGN previous findings.

,2 83.1462ANALYTICAL METHODS Modal Analysis for Asymmetric Systems

D.J. InmanDept. of Mech. and Aerospace Engrg., State Univ. of

83-1460 New York at Buffalo, Buffalo, NY 14260, Intl., Method of Quantifying the Accuracy of Modal Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,

Truncation in Three-Dimensional Seismic Analyses Orlando, FL. Spons. Union College, Schenectady,

T.H. Lee NY, pp 705-708, 5 refsGeneral Atomic Co., P.O. Box 81608, San Diego, "

-

CA 92138, Intl. Modal Analysis Conf., Proc. 1st, Key Words: Modal analysis, Linear systems, Asymmetry, ,

Nov 8-10, 1982, Orlando, FL. Spons. Union College, Viscousdamping, Gyroscopic effects

Schenectady, NY, pp 636-642, 2 figs, 1 table, 11 refs A method of factoring asymmetric matrices into the product

of two symmetric matrices is exploited to provide a modalKey Words: Seismic analysis, Modal truncation analysis technique for a certain subclass of asymmetric

linear dynamic systems. This subclass consists of systemsA method is presented for assessing the deviations in response whose coefficient matrices have real eigenvalues, but arevalues of a dynamic system determined by a truncated-mode not necessarily symmetric. The method is first presentedsolution as compared to those given by an all-mode solution. for systems without velocity dependent forces. The tech-The technique was developed by first deriving the matrix nique is then extended to include systems subject to viscousequation which serves as a quantitative measure for the damping and gyroscopic forces. An example is presentedaccuracy of the truncated analysis From the properties illustrating the details of the method.of this measure, correction schemes can be developed toimprove the accuracy of a dynamic solution using lowermodes only. Application of the method is illustrated byconsidering a three-dimensional seismic analysis.

83-1463Comparison of Finite Element and ExperimentalModal Analyses of a Complex Structure

83-1461 F.S. Heming, Jr. and B.J. Simmons -_

Solution of a General Eigenvalue Problem by Singular Dept. of Engrg. Mechanics, USAF Academy, CO

Value Analysis 80840, Intl. Modal Analysis Conf., Proc. 1st, Nov 8-F.R. Bourne and M.W. Dixon 10, 1982, Orlando, FL. Spons. Union College, Schen-Mech. Engrg. Dept., Clemson Univ., Clemson, SC ectady, NY, pp 603-607, 14 figs, 3 refs29631, Intl. Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, F L. Spons. Union College, Schen- Key Words: Modal analysis, Modal tests, Finite element

ectady, NY, pp 141-146, 4 figs, 1 table, 14 refs technique

The development of a sub-seismically quiet platform forKey Words: Eigenvalue problems, Beams, Elastic founds- testing higher precision gyros and accelerometers providedtions, Free vibration the impetus for a comparison of experimental and finite

element modal analysis techniques on a complex structure.

A technique that may be used to solve the elgenvalue prob- To gain confidence in predicting performance of new plat-lem A(Ix = 0 is presented. The technique involves com- form designs, a comparison of experimental and finite ele-puting the singular value decomposition of AM ) to deter- ment results was made of modal analyses of an existingmine when A00J is singular. It is shown that by using this instrument test platform. This paper summarizes the tech-method, the eigenvectors we easily recovered. The technique niques, models, and results used for the comparison. TheIs applied to the free vibration analysis of a continuous comparison illustrates the accuracy and design value of thebeam supported by elastic elements placed at periodic experimental and finite element techniques used and how

81

" " . .. ' " i. . -. . . . . . .:::: .: ! ! . . " . ::. . . . . . . . . . . . . . . . . . . . . . .," ._ " ",-' . - . . " '. .

design confidence can be enhanced prior to a major commit- ciency of the finite element method using substructuring

ment in fabrication expense. techniques is discussed for acoustic problems. The methodis applied to a problem involving a repeated geometry andto a parameter study. The cases studied indicate that the

method is accurate and practical and also illustrate the useof superelements for design studies. A technique is proposedfor integrating the methods discussed into optimal design

83-1464 algorithms.

Accuracy of Modal Approximations for Dynamic Re.spoen Analysis of Non-Proportionally DampedMechanical StructuresH.N. Ozguven and S.E. SemercigilMiddle East Technical Univ., Ankara, Turkey, Intl. 83-1466

Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982, Load Cell Technique for Coupling Separate StructuralSimulationsOrlando, FL. Spons. Union College, Schenectady, S hpard

NY, pp 662-670, 9 figs, 4 tables, 21 refs G.D. ShepardUniv. of Lowell, Lowell, MA, Intl. Modal Analysis

Key Words: Modal analysis, Damped structures, Mode Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL.superposition method Spons. Union College, Schenectady, NY, pp 508-

513, 7 figs, 2 tables, 2 refsNon-proportional damping does not allow the classical modesuperposition for the determination of the dynamic response Key Words: Substructuring methods

of structures, and necessitates more time consuming and KSicomplex computation techniques to be used. In order to Structural dynamic models of large space structures often

avoid the expense of these solution techniques, different must account for significant nonlinear effects such as gyro-apsproximate methods have been proposed. The most popular scopic and centrifugal forces, configuration dependent messof these is the uncoupled mode superposition method. The and stiffness matrices, and nonlinear constitutive relationssingle mode method has recently been suggested as an alter- for control components. The solution of the nonlinear "

native and tested for simple discrete systems In this paper, system equations must proceed by computer simulation.the accuracy of the single mode method when used for the It is often necessary to couple existing separate dynamicdynamic response analysis of structures is investigate#, by

with mlaMtions By introducing a hypothetical load cell at theanalyzing clamped-clamped and clamped-free beams interface, reactions proportional to the lack of compatibilityvarying amountsand distribution of damping. can be generated. The reactions then act to reduce the

incompatibility to acceptable limits. The addition of aload cell has the undesirable side effect of causing extra

AL vibration modes which are localized at the interface region.These modes may adversely affect the cost, stability andfidelity of the simulation. Using a root locus technique, twostrategies for reducing the adverse side effects of the load

The Application of Substructuring Methods to call are examined. A simulation example which models

Acoustic Finite Element Analysis a rigid interface between two beams shows the feasibilityR.J. Bernhard and D.K. Holger of the load cell technique.

Ray W. Herrick Labs., School of Mech. Engrg., Pur-due Univ., West Lafayette, IN 47907, Intl. ModalAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,FL. Spons. Union College, Schenectady, NY, pp 514-519, 3 figs, 3 tables, 12 refs 83-1467

A Family of Subspace Iteration Algorithms for the

* Key Words: Substructuring methods, Sound propagation, Eigensolution of Large Structural Systems Composed

Finite element technique of SubstructuresA.L. Hale

Finite element analysis has been successfully applied to a Aeronautical and Astronautical Engrg. Dept., Univ.wide variety of acoustic propagation problems. However, of Illinois at Urbana, IL, Intl. Modal Analysis Conf.,the economics of the method makes it unsuitable for manyproblems that are of practical Interest. Substructuring tech-niques can improve the efficiency of the finite element Union College, Schenectady, NY. pp 500-507, 21method In such cases. The accuracy, convergence and effi- refs

82

A. .

* .' .- " ..

Key Words: Eigenvalue problems, Substructuring meth- The techniques being used to correlate experimentally de-ads rived structural dynamics parameters predicted by use of

finite element models are reviewed. Criteria for success of

Subspace iteration is a direct iterative method for producing correlation of the test and analysis data are discussed. Thethe partial eigensolution of large structural systems. The structural dynamics parameters which are directly relatedclassical subspace iteration method is a combination of a to structural integrity are emphasized. The increased com-

' Rayleigh-Ritz order reduction and simultaneous matrix plexitiesof transient response are discussed.*iteration for the whole structure. This paper is concerned

with a family of subspace iteration algorithms that extendthe classical method and that are based on a division of thewhole structure into substructures. Multiple levels of sub-structures are considered.

831470System Prediction Using Reduced ComponentModes

83-1468 K.F. Martin and K.H. GhlaimComplex Mode Extraction by a Conjugate Subspace Univ. of Wales Inst. of Science and Tech., Cardiff, - -

Inverse Power Method Wales, UK, Intl. Modal Analysis Conf., Proc. 1st,

J. O'Callahan and C. Finch Nov 8-10, 1982, Orlando, FL. Spons. Union College,

Univ. of Lowell, Lowell, MA, Intl. Modal Analysis Schenectady, NY, pp 520-525, 3 figs, 2 tables, 11 refsConf., Proc. 1st, Nov 8-10, 1982, Orlando, FL.Spons. Union College, Schenectady, NY, pp 495-499, Key Words: Component mode synthesis, Natural frequencies,

1 table, 2 refs Low frequencies

Key Words: Eigenvalue problems This paper describes a component mode method, with

reduction, to find the lower natural frequencies of a system.

A complex elgensolution of a structural system is accom- The method applies where the connections can be charac-

plished by a method using a conjugate subspace, containing terized by stiffness and damping. A matrix set involving the

a trial mode vector and a pseudo conjugate vector. These eigenvalues and eigenvectors of the components together .

vectors are used to project physical information into modal with a connection matrix is solved to give eigensolutions of

space. An inverse power method is then used to extract the the system; reduction is affected by approximating the

dominant eigenvalue and its corresponding eigenvector from components by a reduced set of eigenvalues and an equally

the conjugate subspace. Once the dominant eigenpair has reduced set of displacements in the egnvector.been obtained, a Gram Schmidt orthogonalization process

is used to purge the effects of the eigenpir (and its conju-gate) from the system equation Additional eigenpairs canthen be extracted. An advantage of this technique is thatany number of eigenpairs can be obtained.

a.,,183-1471Impact Modal Pseudoforce Technique for Nonlinear

Dynamic Analysi83-1469 M.J. Yan and R.E. ClarkCorrelation of Experimental and Analytical Stumc- Babcock and Wilcox, Lynchburg, VA, ASME Papertura Dynamis Parameters - A 1982 Overview No. 82-WA/PVP-7M.P. PakstysElectric Boat Div., General Dynamics, Groton, CT, Key Words: Modal superposition methodIntl. Modal Analysis Conf., Proc. 1st, Nov 8-10,1982, Orlando, FL. Spons. Union College, Schen- It is shown by example cases that the technique of modal

superposition and model pseudoforce based on impact theoryectady, NY, pp 59-65, 3 figs, 2 tables, 17 refs calculates accurate results for the gap and linear dynamic

structures. Results obtained with this technique compareKey Words: Correlation technique, Experimental test data, very well with a theoretical solution and with solutions fromFinite element technique, Reviews another code.

83

82 "-.

83-1472 FL. Spons. Union College, Schenectady, NY, ppAssembling Large Scale System Modelsfronm Test and 698-704, 10 figs, 1 refAnalyss Using Interactive ComputingJ. Klahs, M. Goldstein, R. Madabusi, and R. Russell Key Words: Gyroscopes, Modal analysis, Eigenvalue problems

Structural Dynamics Res. Corp., Milford, OH, Intl.Modal Analysis Conf., Proc. 1st, Nov. 8-10, 1982, This paper presents a theoretical dynamic analysis of the

free rotational modes of oscillation of a two-degree ofOrlando, FL. Spons. Union College, Schenectady, freedom control moment gyroscope, with a flexible outer

NY, pp 46-52, 8 figs, 3 refns gimbal. The primary concern of the analysis is to study theeffect of gimbal torquer inertia on frequency and shape of

Key Words: Component mode synthesis, Computer-aided the flexible gyrodynamic rotational modes of oscillation.

technique These are the free modes which most affect the stability andclosed loop bandwidth of the gyro gimbal drive servos.

The advent of the super-mini computer has brought com- Based on a four degree-of-freedom mechanical model of the

puting power closer to the working engineer and made rotational system, equations of motion are derived, that

. interactive capabilities more feasible. This paper discusses include inertial, gyroscopic, elastic and structural damping

the implementation of system analysis capabilities in an matrices. Modal analysis leads to a complex matrix eigen-

interactive environment. Graphically oriented methods value problem, which is solved via digital computer. The 0for data entry, verification and results interpretation are modes consist of two rigid body modes, one free gyro nuta-

presented. Solution methods oriented toward the super- tion mode, and two structural modes.

mini computer are also discussed. The potential impact ofthese new methods on the design process is reviewed.

83-1475Longitudinal Elastic Wave Propagation in Laminated

83-1473 Compositeswith BondsA Study of Nonlinear Periodic Systems via the E.A. Nassar and A.H. NayfehPoit Mapping Method Mech. Engrg. Tech. Dept., Saginaw Valley StateH. Flashner and C.S. Hsu College, University Center, M1 48710, Intl. ModalTRW Space and Defense Systems Group, Redondo Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando,Beach, CA, Intl. J. Numer. Methods Engrg., 19 (2), FL. Spons. Union College, Schenectady, NY, pp 15-pp 185-215 (Feb 1983) 15 figs, 3 tables, 22 refs 25, 7 figs, 2 tables, 7 refs

Key Words: Point mapping method Key Words: Layered materials, Composite structures, Bondedstructures, Wave propagation, Elastic waves, Finite element

It is well known that one way to treat nonlinear periodic techniquedynamical systems governed by ordinary differential equa-

tions is to find first the corresponding point mappings. This The finite element displacement method is extended to studyapproach has many advantages but it has a main obstacle the propagation of longitudinal elastic waves in laminated

in that it is difficult to obtain the exact mapping except in composites with bonds. The geometric arrangement of the

very special cases. Presented in this paper is a procedure composite model considered in this paper is treated as awhich allows us to determine the point mapping in a poly- special type of a trilaminated composite in which each ofnomial form up to any specific degree of accuracy. After its major constituents is sandwiched between two bondingpresenting the algorithm for finding the point mappings, layers. The dispersion characteristics of this model are

the method is applied to several problems in order to study presented here and compared with those obtained usingthe dynamical properties of the systems and to demonstrate continuum theory with microstructures.the usefulness of the method.

MODELING TECHNIQUES83-1474Natural Rotational Modes of a Flexible Two Degree-of-Freedom Control Moment Gyroscope 83-1476R.1. Sann Electrotopography - A New Tool for Modeling Dy. - "

Manhattan College, Riverdale, NY, Intl. Modal namic Mechanicsl StructuresAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, M. Ensanian

"84

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Laboratory for Robot Sensor Technology, Ensanian Ohio State Univ., 206 W. 18th Ave., Columbus, OHPhysicochemical Inst., Eldred, PA 16731, Intl. Modal 43210, Intl. Modal Analysis Conf., Proc. 1st, Nov 8- %Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, 10, 1982, Orlando, FL. Spons. Union College, Schen-FL. Spons. Union College, Schenectady, NY, pp 216- ectady, NY, pp 8-10, 4 figs, 4 tables, 15 refs222, 4 figs, 3 tables, 4 refs

Key Words: Fluids, Natural frequencies, Mode shapes, FiniteKey Words: Electrotopography, Mathematical models, Modal element technique, Mobility method

. analysisOne-dimensional fluid systems can be analyzed for natural

Electrotopography is a new science and technology and it frequencies and modes using an available structural finiteis concerned with the n-dimensional physicochemical charac- element program, with the aid of the mobility analogy. Interization of engineering components. It is based upon a this paper, the methodology, strength and limitation of the

- new type of transducer system. The method permits one to solution technique are discussed. This method is validated* perform a systems analysis on metallurgical structures in by considering several example cases and comparing results

. terms of their chemical elemental constituents. Funda- with theory, experiment or other numerical techniques.mentally, this provides a new approach to modeling dynamicmechanical structures and modal analysis. This paper pro-vides a brief overview of the new field. Al

83-14798 4Optimization of Model Matrices by Means of Experi-83-1477 mentally Obtained Dynamic DataTransient Load Modeling: Clipped Normal Processes W. Heylen0. Ditlevsen and H.O. Madsen Katholieke Univ. Leuven, Belgium, Intl. Modal Analy-Danmarks Ingeniorakademi, Bldg. 373, DK 2800 sis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, FL.Lyngby, Denmark, ASCE J. Engrg. Mech., 109 (2), Spons. Union College, Schenectady, NY, pp 32-38,pp 494-515 (Apr 1983) 6 figs, 26 refs 2 tables, 14 refs

Key Words: Mathematical models, Transient excitation, Key Words: Mathematical models, Optimization, Experi-Stochastic processes mental test data

The paper discusses the possibility of using a class of sto- Model optimization is a name for all techniques using experi-chastic processes, called clipped normal processes, for simu- mental model parameters to modify an existing analyticallating transient load effect phenomena in structures. Mean model, expressed by a mass, stiffness and damping matrix.upcrossing rates of some level, for sums of clipped normal A survey is given of the various techniques reported in theprocesses, can be calculated by the use of a general method literature. These techniques can be divided into two maincalculating mean outcrossing rates of normal vector pro- groups: methods based essentially upon equations of motioncesses from convex polyhedral sets in a multi-dimensional and upon orthogonality conditions; methods using sensi-real space. The mean upcrossing rate of a high level gives tivity analysis techniques. A number of particular problemsthe essential term of an upper bound on the failure prob- are discussed - selection of the unknown structural param-ability, i.e., the probability of exceeding the given level with- eters, typical limitations of the experimental data, descrip-In a given time period. That this upper bound for high levels tion methods of the damping.may be close to the exact failure probability is demonstratedby an example calculating a lower bound based on thebivarlste distributions of the generating normal processes.Both the upcrossing rate determination and the calculationof the lower bound are based on some well-known general N L A N Yformulas for optimized upper and lower bounds. NONLINEAR ANALYSIS

83-148083-1478 A Conmstent Eulerian Formulation of Large Defor-Finite Element Moddinig of Fluid Systems Using the mation Problems in Statics and DynamicsMoblity Analogy Approach M.S. Gauala, G.A'E. Oravas, and M.A. DokainishR.J. Gaines and R. Singh Ontario Hydro, Res. Div., Toronto, Ontario MBZ

85

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5S4, Canada, Intl. J. Nonlin. Mech., 18 (1), pp 21- Key Words: Numerical analysis, Dynamic stability

35 (1983) 1 fig, 37 refsNumerical analysis is used to study parametric system sta-

bility under periodic piecemeal-constant excitation. TheKey Words: Nonlinear theories effects of damping and excitation on the instability region

transformation are investigated. The results of the investi-A concise survey of formulation methods of geometric and gation are presented in a graphical form.material nonlinearity problems is given. The survey is con-cerned mainly with the differences between updated Lagran-

"; glen and Eularien formulations, and with the specific natureand basic characteristics of each. The underlying mechanicsand the spatial discretization for an Eulerian formulation arediscumd. PARAMETER IDENTIFICATION

(Also see No. 1493)

NUMERICAL METHODS(Also se No. 1361) 83-1483

Modeling and Identification of Mechanical StructuresK.A.F. MoustafaCollege of Engineering, Mosul Univ., Mosul, Iraq, Intl.

83-1481 Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,The Numerical Implementation of a Multi-Input Orlando, FL. Spons. Union College, Schenectady,Modal Estimation Method for Mini-Computers NY, pp 671-678, 13 refsH. Void and G.T. RocklinStructural Dynamics Res. Corp., Milford, OH, Intl. Key Words: Parameter identification techniquesModal Analysis Conf., Proc. 1st, Nov 8-10, 1982,Orlando, FL. Spons. Union College, Schenectady, Mathematical models for a mechanical structural system areNY, pp 542-548, 12 refs derived. The unknown model parameters are identified by

on-line schemes that utilize excitation and response records.

Key Words: Modal analysis, Frequency response function,Curve fitting, Poly reference method, Numerical analysis

-' The poly reference complex exponential method has,through its application in fields such as seismic, aerospaceand automotive industries been shown to handle structures 83-1484with high modal density, repeated roots and high damping. Parameter Estimation from Frequency Response Mea-Simultaneous use of date from multiple exciter locations ures ets Using Rational Fraction Polynomialsreduces the user interaction and judgement required to ob- M.H. Richardson and D.L. Formentitain consistent modal models of complex structureL This Structural Measurement Systems, Inc., San Jose, CA,paper presents various methods for numerical implementa- Itl.cMoal Aaysieenst , Proc.1, nJove 81,

tion of the poly reference technique and compares their Intl. Modal Analysis Conf., Prec. 1st, Nov 8-10,merits for the short precision mini-computer environment. 1982, Orlando, FL. Spons. Union College, Schenec-

tady, NY, pp 167-181,24 figs, 6 refs

Key Words: Parameter identification technique, Frequencyresponse function, Rational fraction polynomials

83-1482This Is a new formulation which overcomes many of theThe Staldity of Parametric Systems under Plece•a. numerical analysis problems associated with an old least

Constmat Excitation squared error parameter estimation technique. OvercomingJ. Fedorov these problems has made this technique feasible for imple-Ivanovskii Energeticheskii Institut im. B.I. Lenin, mentation on mini-computer based measurement systems.USSR, Vibrotechnika, A. (34), pp 13-17 (1982) 5 This technique is not only ueful in modal analysis appllca-Ugs, rstions for identifying the modal parameters of structures,figs, 4 refs but it can also be used for identifying poles, zeros and(In Russian) resonances of combined electro-mechanical servo-sstems.

86 8":2

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83-1485 Zhejiang Univ., Hangzhou, Zhejiang, China, Intl.Estimation of Modal Parameters in a Noise-Driven Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,Linear System by an Averaged Short-Time Fourier Orlando, FL. Spons. Union College, Schenectady,Technique NY, pp 187-191,4 figs, 4 refs "D.H. Friedman -Dept. of Electrical Engrg., Rutgers Univ., P.O. Box Key Words: Parameter identification technique, Modal909, Piscataway, NJ 08854, Intl. Modal Analysis analysis, Viscous damping, Curve fitting, Machine tools

4; Conf., Proc. Ist, Nov 8-10, 1982, Orlando, FL.Spons. Union College, Schenectady, NY, pp 123-129, A method of identification is proposed which enables identi-- Uo ogSe ty Y pfication of modal parameters of mechanical systems with8 figs, 4 refs viscous damping in a wide frequency band, including a large

number of modes. Theoretically, the identified frequency

Key Words: Parameter identification technique range and number of modes are unlimited. According tocomplex modal theory, the relationship between modal

A method is presented for estimating the modal parameters parameters and frequency response is formulated. Structure

of a linear system from its output when driven by an inacces- is excited at one point and frequency response data are Isible wideband noise process, based on the ratio of a short- measured at many stations of interest. The curve fitting

time Fourier transform and its derivative with respect to time is based on the least squares principle and term by term

location. Theory indicates that the mean estimated damping finting is used. By using the method proposed simultaneousfactors in particular are nearly independent of relative mode curve-fitting of many frequency response curves measured

amplitudes and unaffected by observation noise, by forcing the structure at one point is available. The pro-cedure has been successfully used for the dynamic investi-gation of a surface grinding machine.

.4 83448 83-1488 A.,

Accuracy of Modal Parameters from Modal Testing Advanced Matrix Methods for Experimental Modal

W. Looser Analysis - A Multi-Matrix Method for Direct Param-Inst. of Machine Tool Design and Production Engrg., eta ExtractionSwiss Federal Inst. of Tech., Zurich, Switzerland, J.M. Leuridan and J.A. KundratIntl. Modal Analysis Conf., Proc. Ist, Nov 8-10, Structural Dynamics Ret Corp., Mifford, OH, Intl.1982, Orlando, FL. Spons. Union College, Schenec- Modal Analysis Conf., Proc. 1st, Nov 8-10, 1982,

tdNY, pp 201-207, 12 f igs, 6 refs MdlAayi ofPo.1t o -0 92tady, NOrlando, FL. Spons. Union College, Schenectady,

NY, pp 192-200, 15 figs, 1 table, 12 refsKey Words: Parameter identification technique, Modal tests,Error analysis

Key Words: Parameter identification technique, Matrix

The accuracy of modal parameters from model testing is of methods, Modal analysis

-J paramount importance when they are used for furthercalculations such as structure modifications, coupling of With the multi-matrix method, a matrix polynomial is esti-

substructures etc. The measurement itself can be faulty, mated using frequency responses, relative to several reference

depending on type, location and intensity of excitation. locations, simultaneously. From the matrix coefficients, a

Considerable differences can also occur when measurementp consistent set of modal parameters is calculated. Two appli-

are repeated. For structures with strong resonance coupling cation examples are used to show how this method, by

and high damping, identification with conventional tech- taking full advantage of the redundancy in the frequency

nology places high demands. Error sources and limits in responses, cen handle structures with various dynamic

measurement and identification are shown. New procedural characteristics such as repeated modes, high modal damping

possibilities are also presented. and high modal density.

83-148983-1487 Modification and Refinement of Large DynamicIdentification of Structural Modal Parameters from Structural Models: Efficient Algorithms and Com--Measured Multi-Station Data puter ApplicationsC. Yaodong, S. Dunzhi, and S. Yueming K.D. Blakely and M.W. Dobbs

87

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ANCO Engineers, Inc., Culver City, CA, Intl. Modal Key Words: Submerged structures, System identificationAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, techniques, Structural modification techniques, Experi-F L. Spons. Union College, Schenectady, NY, pp 598- mental test data

602, 2 figs, 2 tables, 12 refs The finite element method applied to the calculation of

hydrodynamic added mass implies error and high computerKey Words: System identification techniques, Mode modifi- cost. The proposed method aims at identifying the addedcation method, Off-shore structures, Drilling platforms, mass by using the measurement of the modes of the struc-Dams ture, both dry and in contact with the fluid. The discrete

model which expresses the dynamic behavior of the fluidSystem identification involves the modification of a struc- structure system is obtained through an optimization pro-tural model to accurately reflect actual structural behavior. cedure. The prediction of the influence of structural modifi-The model modification process Is described herein, including cation was obtained by applying the method to the case oftheory and previous implementation. Current, efficient a plate partially immersed in water.implementation, via closed-form response sensitivity calcu-lations and design variable linking, is given. Forced-vibra-tion testing and subsequent model modification are pre-sented for a concrete arch dam and a steel offshore oil plat-form. OPTIMIZATION TECHNIQUES

83-1492Sensitivity Analysis of Mechanical Structures, Based

83-1490 on Experimentally Determined Modal ParametersIntegrated System Identification: The Union of Test- P. Vanhonackeriag and Analysis Leuven Measurement and Systems, Heverlee, Bel-K.D. Blakely and M.W. Dobbs gium, Intl. Modal Analysis Conf., Proc. 1st, Nov 8-ANCO Engineers, Inc., Culver City, CA, Intl. Modal 10, 1982, Orlando, FL Spons. Union College, Schen-Analysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, ectady, NY, pp 534-541, 6 figs, 18 refsFL. Spons. Union College, Schenectady, NY, pp259-264, 9 figs, 2 tables, 14 refs Key Words: Sentvity analsi, Optimization, Dynamic

response, Modal analysis, Viscous damping

Key Words: System identification techniques, Piping systems, A al ifiAs the sarch for optimal design or modification of linear -.-Nuclear power plants, Containment structures, Off-shorestructures structures becomes increasingly important, it is important

to estimate efficiently the sensitivity of the dynamic behavior

The four phases of integrated system identification - formu- with respect to the changes of system parameters like mass,ltion and use of a pre-test analytical model, dynamic testing stiffness or damping distribution. Efficient methods for, and uste dto, predtestianalticalf model dynamictestin, evaluating the derivatives of natural frequencies and modeland data reduction, identification of modal characteristics, dslcmnsaepooe.Epai spae nsniand post-test model verification/refinement -- are presentedas they pertain to correlating a linear elastic finite element tivity methods which require only model parameters as

model to match test data. Application of each phase to input data and In which the general viscous damping repre-sensation is usedl. Expresions for both differential and";modal testing and analysis of large-scale structures is given. snIntegrated system identification, linking testing and analysis finite difference ctilvitis of elgenvalues and egenvetorsby utilizing both the analyst and experimentalist, is shown are presented. Practicl applicatons on the use of sensitivityto be an effective tool In deriving accurate structural models, analysis In prototype optimization and troubleshooting

problems are presented.

83-1491 DESIGN TECHNIQUESHydrodyunsc Added-Mas Identification from Reo-meee TestsL. Jezequel 83-1493Ecole Centrale de Lyon, Ecully, France, AIAA J., Optimal Redesin Based on Modal Data21 (4), pp 608-613 (Apr 1983) 1 fig, 5 tables, 18 refs J.M. Starkey and J.E. Bernard

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Michigan State Univ., East Lansing, MI, Intl. Modal R.L. Huston, M.W. Harlow, and N.L. GausewitzAnalysis Conf., Proc. 1st, Nov 8-10, 1982, Orlando, Inst. of Appl. Interdisciplinary Res., CincinnatiFL. Spons. Union College, Schenectady, NY, pp 591- Univ., OH, Rept. No. ONR-UC-MIE-090182-14, 52

597, 6 figs, 4 tables, 4 refs pp (Sept 1982) -

AD-A120 403 gKey Words: Mode modification technique, Design techniques

Key Words: Computer programsStructural redesign problems can be classified as either pre-diction problems; that is, predicting new natural frequencies This is a user's manual for the computer program UCIN-and mode shapes given a description of the proposed changes, EULER. The program is designed and developed to studyor specification problems, in which details of the design the dynamics of multibody systems. The multibody systemschange are sought which will yield desirable dynamic charac- encompassed by EULER are systems of linked rigid bodiesteristics. This paper illustrates a technique which uses modal with no closed loops, such as robot arms, chains, antennas,data as a basis for specifying an alternative design which has manipulators, and human body models. The manual providesimproved structural dynamics, The technique allows the instruction for using EULER to study multibody systemspecification of undesirable frequency bands and costs for dynamics, It also provides sample input and output data.design changes, and attempts to find a cost-effective design Input procedures and commands are expressed in terms ofwhich removes frequencies from these bends. keywords in order to make the program useful and readily

accessible to even the casual user.

COMPUTER PROGRAMS

831494 GENERAL TOPICS

PVAST" a Finite Element Program for Propdler GTVbainand Strength Analysist.-, D.R. Smith and M.E. Norwood

CONFERENCE PROCEEDINGSSDefence Res., Establishment Atlantic, Dartmouth,

Nova Scotia, Canada, Intl. Modal Analysis Conf.,Proc. 1st, Nov 8-10, 1982, Orlando, FL. Spons. 83-1496Union College, Schenectady, NY, pp 679-685, 14 Internatioml Modal AnalysisConferencefigs, 1 table, 6 refs Proc. of the 1st, Orlando, FL. Nov 8-10, 1982. Spons.

Union College, Schenectady, NYKey Words: Computer programs, Propellers, Marine pro-pellers, Vibration analysis Key Words: Modal analysis, Proceedings

A computer program, PVAST, which has been developed for The lastest theories, research activities, and practical appli-the linear elastic analysis of marine propellers is described. cations of experimental model analysis techniques wereThe program is based on the finite elmeent method of presented at this conference. Dozens of papers are devotedstructural analysis, It has been designed to automatically entirely to analytical methods and dozens more to experi-generate finite element models from a large library of elemental techniques and case histories, Considerable emphasisments for a wide variety of propeller geometries Graphic is given to the latest efforts to link analysis and experimentdisplays of the geometry and the finite element model are through their respective computers, thereby blurring the . -

provided for data checking purposes. The program has the boundary between traditionally separate disciplines,ability to carry out static, natural frequency, and dynamicresponse analysis and to account for the effects of fluidstructure interaction. Computer results are processed bythe program to show stress, displacements, natural frequency USEFUL APPLICATIONSof vibration and dynamic response in graphic form for easeof Interpretation.

83-1497A Method for Measring the Ma. Concentration ofSolid Particles in Fluids wills the Aid of Transvermlly

83-1495 Vibrating Filter Bands (Maenbeimmung disperserUser's Manual for UCIN-EULER. A Multipurpose. Stoffe mit Hilfe transveral sehwiigender Filter.Multilhody Systems. Dynamics Computer Program binder)

89

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H. Bahner and Th. Gast filter bands is described. The precipitated particles con-Auguste-Viktoria-Str. 4, 1000 Berlin 33, Techn. tribute to the mass of the filter and affect its natural fre-

Messen-TM, 50 (1), pp 3-13 (Jan 1983) 14 figs, quency. Thus, a comparison between the respective fre-1"tble1 refsquencies of a fresh and an exposed filter allows to calculate

the masn concentration of the particulate matter. The meth-(In German) od provides absolute values which are independent of the

chemical or physical composition of the solid. In this regard

Key Words: Measurement techniques, Fluids, Vibratory it needs no empirical correction. Suitable filter materials

techniques, Filters (mechanical) have been selected and thai vibrational behavior has beentested.

A method for meauring the mass concentration of solidparticles in fluids with the aid of transverselly vibrating

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AUTHOR INDEX

Abel, J.F ............... 1291 Chen, Lien-Wen .......... 1373 Flowers, K.D ............ 1404

Adali, S... ........... 1368 Cheng, Yaodong ..... 1446, 1452 Formenti, D.L ........... 1484Agbabian, M.S ........... 1332 Chestnutt, D ............ 1309 Forssen, B .............. 1401Akesson, B. 1356, 1358, 1365 Chin, S.L.............. 1394 Friberg, 0......... 1356, 1365

All, S.A ............... 1360 Chitty, D.E ......... 1388, 1389 Friedman, D.H ........... 1485Alibe, B ............... 1411 Chouard, P ............. 1392 Frostig, Y .............. 1354Allemang, R.J. .. 1313,1315,1427 Chung, J.C ............. 1443 Fujukawa, T ............ 1280

Anderson, C.A ........... 1450 Clark, R.E .............. 1471 Gadala, M.S ............. 1480Anderson, C.E., Jr........ 1418 Coan,C.H.............. 1367 Gaines, R.J............. 1478

Anderson, M.J .......... 1390 Colwill, P .............. 1426 Galyardt, D ............. 1304Andry, A.N., Jr.......... 1443 Cooperrider, N......... 1338 Gambhir, M.L........... 1353

Angerer, S .............. 1448 Cossalter, V ............. 1294 Gamon, M.A ............ 1318

Aristizabal-Ochoa, J.D...... 1348 Costa, A ............... 1283 Garcia, J.-L ............. 1392Attenborough, K......... 1403 Crocker, MJ............ 1401 Garro, A............... 1305

Avitabile, P ......... 1349, 1445 Darlow, M.S ............ 1434 Gast, Th ............... 1497Babu, B.J.C ............. 1377 DeWispelare, A.R ......... 1312 Gattass, M .............. 1291Bahgat, B.M ............. 1339 Ditlevsen, 0 ............. 1477 Gausewitz, N.L .......... 1495

Bahner, H.............. 1497 Dixon, M.W............. 1461 Geller, L............... 1459

Balendra, T ............. 1287 Dobbs, M.W ......... 1489, 1490 Ghlaim, K.H ............ 1470

Barbiero, D ............. 1305 Doige, A.G ............. 1385 Giansante, N ............ 1282Barta, D.A .............. 1390 Dokainish, M.A .......... 1480 Gilbert, C.............. 1327Bastick, M .............. 1293 Dominic, R.J ............ 1340 Gill, P.S ............... 1419Batchelor, B.deV......... 1353 Dong, W.N............. 1378 Gimenez, J.G............ 1436Beliveau, J.G ............ 1437 Doong, Ji-Liang .......... 1373 Glass, R ............... 1397Berman, A .............. 1282 Doyle, G.R., Jr ........... 1351 Gluck,J ............... 1354

Bernard, J.E........ 1442,1493 Dukkipati, R.......... 1339 Goldstein, M............ 1472

Bernhard, R.J........... 1465 Dunzhi, S .............. 1487 Golub, R.A ............. 1341Bhat, R.B .............. 1281 Dzialo, F.J ............. 1394 Graf, P.A .............. 1340

Bjorkman, M ............ 1321 Earles, S.W.E ............ 1324 Gralulevi~ius, A .......... 1415Blakely, K.D .... 1386, 1489, 1490 Edelstein, A ............. 1438 Griffin, J.H ............. 1342Bond, J.H.............. 1429 Elkins, J.A............. 1306 Griffith, D.T............ 1440

Bourne, F.R ............ 1461 Ellingwood, B ........... 1290 Griffith, S .............. 1386Bowen, W.L............ 1345 Engelstad, R.L........... 1296 Gupta, A............... 1372

Brickey, C.E............ 1316 Enochson, L........ 1304, 1317 Hale, A.L.............. 1467

Brown, D.L .... 1313,1315,1427, Ensanian, M ............. 1476 Hall,W.J ............... 1292*............................1428 Fard is, M.N ............. 1411 Hal lauer, W. L., Jr..1322, 1359

Bulanow, W.B ........... 1323 Farrell, P.A ............. 1334 Halliwell, R.E ........... 1400

Carbon, G.D ............ 1315 Fedorov, J .............. 1482 Harlow, M.W ............ 1495Cargill, A.M............. 1343 Fenwick, R.C ............ 1364 Haroun, M.A ............ 1381Carrasoose, L.I ........... 1436 Ferencz, R.M ........... 1289 Hashmi, M.S.J ........... 1363Carucci, V.A ............ 1383 Finch, C ............... 1468 Hawker, K.E ............ 1407Caudell, M .............. 1426 Firmin, A .............. 1441 Heming, F.S.,Jr .......... 1463Chandiramani, K.L ........ 1409 Fishman, H.M ........... 1350 Henrick, R.F ............ 1405Chang, L.C .............. 1366 Flannelly,W.G ........... 1282 Hershfeld, D.J ........... 1347Chaplin, B .............. 1398 Flashner, H ............. 1473 Heylen, W .............. 1479

91

., V~ ~~ . .V . .. . . . . . V* * * .

Hill, R.G ............... 1300 Liberatore, G ............ 1294 Pan Jiaqiang ............ 1452 . . .

Holger, D.K ............. 1465 Lin, W.H ............... 1402 Pardoen, G.C ............ 1330

Honda, S ............... 1431 Lin, Y.K............... 1285 Passerello, C.E ........... 1372

Horne, C.............. . 1341 Liu, R.Y.L ............. 1359 Pastor, T.P ............. 1297

Horton, W.H ............ 1424 Long, G............... 1334 Pastorel, H............. 1437

Howard, G.E ........ 1388, 1389 Looser, W .............. 1486 Patterson, J.F ........... 1300

Howes, R.L ............. 1317 Lovell, E.G ......... 1296, 1380 Payne, B.F ............. 1423

Hsu, C.S ............... 1473 Lu, Naiyan ............. 1446 Penland, C .............. 1407Huckelbridge, A.A., Jr ...... 1289 Luk, Y.W.............. 1444 Peterson, R.W ........... 1450Hunt, J.B .......... 1333,1336 Lund, R.N .............. 1451 Pinkham, R.S., Ill ........ 1379Huston, R.L ............ 1495 Lunden, R.............. 1358 Plaut, R.H.............. 1367Hutchins, D.A ........... 1456 Lung, T.Y .............. 1385 Plyat, S.N .............. 1371

Ibanez, P ........... 1386, 1388 M6tt~nen, M ............ 1302 Preisser, J.S ............. 1341

Inman, D.J ............. 1462 MacQueen, D.H .......... 1410 Price, S.J ............... 1352Inskeep, D.W............ 1308 Madabusi, R ............ 1472 Pyke, R ............... 1293Irani, F.D .............. 1307 Madsen, H.O ............ 1477 Racca, R ............... 1325Irretier, H .............. 1375 Malam, D .............. 1329 Raju, B.B .............. 1340Isenberg, J .......... 1295,1299 Maljutin, I .......... 1361,1362 Ramakrishnan, C.V........ 1382

Iwatsubo, T ......... 1280, 1414 Marquiss, S.A ........... 1434 Ramamurti, V........... 1370

Jackson, W.F ............ 1418 Martin, A .............. 1392 Ramsey, K.A ............ 1441

Janczy, J.R ............. 1319 Martin, K.F ............. 1470 Raptis, A.C ............. 1402Jensen, F.B ............. 1406 Martini, K.H ............ 1425 Reddy, D.P ............. 1332Jezequel, L ............. 1491 Martins, H .............. 1279 Reddy, J.N ......... 1369, 1376

Joanides, J ............. 1?20 Massoud, M ............. 1437 Rev~sz, Zs .............. 1384

Johansson, B ............ 1416 McGill, A.J ............. 1333 Richardson, M.H ......... 1484Jones, C.B .............. 1449 Meirovitch, L ............ 1396 Ripple, A.G ............. 1319 -. -

Jones, H.W ............. 1456 Mesquita, L.C ........... 1322 Rizai, M.N .............. 1442KamphE..............1365 Morgan, J.R.............1292 Roberts,GYP............1329Kanok-Nukulchai, W ....... 1288 Moriwaki, Y ............ 1293 Roberts, J.A ............ 1308Karasudhi, P ............ 1288 Moustafa, K.A.F .......... 1483 Robinson, H ............ 1349Kawai, R ............... 1280 Mueller, R.T ............ 1383 Rocklin, G.T ............ 1481

Klahs, J ............... 1472 Mutch, G.F ............. 1457 Rosenhouse, G .... ...... 1354

Koch, R.A .............. 1407 Nagaya, K .............. 1374 Rossing, T.D ............ 1450 .4Kosawada, T ............ 1355 Nassar, E.A ............. 1475 Rost, R.W .............. 1313

Kot, C.A ............... 1299 Naundorf, H ............ 1448 Russell, L.T............. 1456

Kundrat, J.A............ 1488 Nayfeh, A.H............ 1475 Russell, R..........1457,1472Kuperman, W.A .......... 1406 Nedbaj, A .......... 1361,1362 Saczalski, K.J ............ 1412

Kurohashi, M ............ 1280 Newell, J.P ............. 1329 Sampson, R.C ........... 1387

La France, L.J ........... 1379 Newmark, N.M ........... 1292 Sann, R.I .............. 1474

Lai, Shih-Shenq Paul ...... 1286 Norwood, M.E ........... 1494 Sarig~l, N.G ............. 1395Lamontia, M.A ........... 1432 O'Callahan, J ........ 1445, 1468 Sas, P ................. 1399Lea, K.G ............... 1336 Ohlsson, S .............. 1356 Sathyamoorthy, M ........ 1357

Lee, J ................. 1393 Ohrstrom, E ............ 1321 Sato, J ................ 1430

Lee, M.Z............... 1391 Okubo, N.............. 1431 Schlack, A.L., Jr..... .... 1378

Lee, S.-Y ............... 1288 Oravas, G.A'E ........... 1480 Schmerr, L.W ............ 1439

Lee, Seng-Lip ........... 1287 Ortiz, L.A .............. 1393 Schmidtberg, R.A ......... 1435Lee, T.H ............... 1460 Osman, M.O.M ........... 1339 Schneider, H ............ 1458

LeKuch, H ............. 1327 Ouyang, C .............. 1420 Schoenster, J.A ...... ... 1341Lepor, M............... 1397 Ozguven, H.N........... 1464 Scott, R.F.............. 1393

Leuridan, J.M ........... 1488 Pakstys, M.P............ 1469 Seilius, A .............. 1415

Leyendecker, E.V ......... 1290 Pal, T.G ............... 1435 Sellberg, R.P............ 1346

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iM

Semercigil, S.E ........... 1464 Stein, P.K .............. 1433 Void, H ............... 1481Sengupta, S............. 1382 Steinberg, D.S........... 1413 Vorus, W.S............. 1284Serbyn, M.R ............ 1422 Stern, F ............... 1284 Vullo, V ............... 1305Severud, LK ............ 1390 Stimpson, C ............. 1417 Walton,W.B ........ 1388, 1389Shapiro, E.Y............ 1443 Stimpson, J.B ........... 1440 Warburton, G.B .......... 1337Shapton, W.R ........... 1451 Sukere, A.A ............. 1447 Waszczyszyn, Z .......... 1421Sharpe, W.N., Jr .......... 1447 Sun, Yueming ....... 1446, 1452 Waterstraat, A ........... 1344Shepard, G.D ............ 1466 Sunder, P.J ............. 1382 Watton, J .............. 1455Shepherd, R.B ........... 1450 Suzuki, K .............. 1355 Weaver, H.J ............. 1298Shycoff, D ............. 1318 Takahashi, S ............ 1355 Weinstock, H............ 1306Sigel, H.D .............. 1330 Talapatra, D.C ........... 1347 White, M.P............. 1394Silverberg, L.M ........... 1396 Tang, H.T .............. 1388 W ilkins, L.J ............. 1324Simmons, B.J ............ 1463 Tang,Y.K .............. 1388 Willshire, W.L., Jr ......... 1310Singh, R ............... 1478 Tassoulas, J.L ........... 1411 Willstaedt, E ............ 1434Singhal, S.N............. 1380 Tat, Chan Went.......... 1287 Wilson, N.G............. 1307Sinha, A............... 1342 Teipel, I............... 1344 Wilson, P.M............. 1335Skidmore, G.R ........... 1322 Tersch, H .............. 1331 Wirth, J.L .............. 1338Smallwood, D.O. . 1453, 1454 Teschner, K ............. 1279 Witte, G ............... 1303 - .Smiley, R.G ............. 1314 Tj~tta, J.N ............. 1408 W ittlin, G .............. 1318 ". ".1Smith, D.R ............. 1494 Tjtta, S .............. 1408 Yan, M.J ............... 1471Smythe, R.C ............ 1424 Toffolo, F .............. 1294 Yang, J.N .............. 1285Snoeys, R .............. 1399 Tombers, P.A ............ 1346 Yao, J.T.P .............. 1290Spizyna, D.N............ 1323 Tomlinson, G.R.......... 1328 Yaodong,C............. 1487Sreenivasamurthy, S ....... 1370 Tong, Zhongfang ..... 1446, 1452 Ye, Tin-Yew ............ 1373Srinivasan, M.G .......... 1299 Udaka, T ............... 1293 Young, J.W ............. 1320Srinivasan, R.S ........... 1377 Vanhonacker, P .......... 1492 Yueming, S ............. 1487Stager, R.P ............. 1312 Vaughan, D.K ...... 1295,1299 Zemaitis, T ............. 1415Starkey, J.M ............ 1493 Vidmar, P.J ............. 1407 Zhou, Yongfang ......... 1446Steedman, J.B .......... 1438 Villasor, A.P., Jr .......... 1371

t ,

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CALENDAR

AUGUST 1983 Pasadena, CA (Mr. Henry C. Pusey, Director, SVICNaval Research Lab., Code 5804, Washington, DC8-11 Computer Engineering Conference and Exhibit 20375) ;",

[ASME] Chicago, IL (ASME Hqs) 20..

31-Nov 4 John C. Snowdon Vibration Control Seminar8-11 West Coast International Meeting [SAE] Van- [Applied Research Lab., Pennsylvania State

couver, B.C. (SAE Hqs.) Univ.] University Park, PA (Abry Ann Solic,410 Keller Conference Center, University Park,

SEPTEMBER 1983 PA 16802 - (814) 8654591)

11-13 Petroleum Workshop and Conference [ASME] NOVEMBER 1983Tulsa,Q0lK (ASME Hqs.J

6-10 Truck Meeting and Exposition [SAE] Cleveland,11-14 Design Engineering Technical Conference [ASME] OH (SAE Hqs.)

Dearborn, MI (ASME Hqs)

7-11 Acoustical Society of America, Fall Meeting12-15 International Off-Highway Meeting & Exposition [ASA] San Diego, CA (ASA HqL)

[SAE] Milwaukee,Wl (SAEIHqs.)13-18 American Society of Mechanical Engineers. Winter

14-16 International Symposium on Structural Crashwor- Annual Meeting [ASME] Boston. MA (ASMEthiness [University of Liverpool] Liverpool, UK Hqs.)(Prof. Norman Jones, Dept. of Mach. Engrg., TheUniv. of Liverpool, P.O. Box 747, Liverpool L693BX, England) MARCH 1984

25-29 Power Generation Conference [ASME] Indianapo- 20-23 Balancing of Rotating Machinery Symposium

I is, IN (ASMEHqs.) [Vibration Institute] Philadelphia, Pennsylvania(Dr. Ronald L. Eshlenn, Director, The Vibration

28-30 Rotating Machinery Vibration Symposium [Vibra- Institute, 101 W 55th St., Suite 206, Clarandon

tion Institute] Worcester, MA (Dr. Ronald L. Hills, IL 60514 - (312) 654-2254) ..

Eshlemn, Director, The Vibration Institute, 107W. 55th St., Suite 206, Clarendon Hills, IL 60514 - APRIL 1984(312) 654-2254)

9-12 Design Engineering Conference and Show [ASME]0CTOBER 1983 Ch icago, I L (ASME Hqs)

3-7 Advances in Dynamic Analysis and Testing [SAE 9-13 2nd International Conference on Recent AdvancesTechnical Committee G-5] SAE Aerospace Con- in Structural Dynamics [Institute of Sound andgress and Exposition, Long Beach, CA (Roy W Vibration Research] Southampton, England (Dr.Mustain, Rockwell Space Transportation and Sys- Maurice Petyt, Institute of Sound and Vibration

tern, Group, A0 Ste. AB97, 12214 Lakewood Research, The University of Southampton, S09

Blvd., Downey, CA 90247) 5NH, England - (0703) 559122, ext. 2297)

3-7 SAE Aerospace Congress and Exposition [SAE) MAY 1984Long Beach, CA (SAE Hqs.)

7-11 A'oustical Soer!ty of America, Spring Meeting17-19 Stapp Car Crash Conference (SAE) San Diego, CA [ASe] Norfik, VA (ASA Hq)"

(SAE Hqs.)"_010-11 12th Southeastern Conference on Theoretical

17-20 Lubrication Conference [ASME1 Hartford, CA and Applied Mechanics [Engineering Extension(ASMEHqL) Service, Auburn University, Alabama] Callaway

Gardens, Pine Mountain, GA (P. Fred O'Brien,18-20 54th Shock and Vibration Symposium [Shock and Director, Engineering Extension Service, Aubwn

Vibration Information Center, Washington, DC] University, AL 36849 - (205826-4370)

94

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AHS: American Helicopter Society IFToMM: International Federation for Theory of

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AIAA: American Institute of Aeronautics and

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E: New York, NY 10017 "N YkY 0SAE: Society of Automotive Engineers

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21 Bridge Sq.ICF: International Congress on Fracture Westport, CT 06880

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IEEE: Institute of Electrical and Electronics Engineers

Engineers 74 Trinity PI.

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1 Birdcage Walk, Westminster, Naval Research Lab., Code 5804

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95

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PUBLICATION POLICY

Unsolicited articles are accepted for publication in the Shock and Vibration Digest. Feature articles should be tutorials and/or reviews of areas of interest to shock and vibration engineers. Literature review

articles should provide a subjective critique/summary of papers, patents, proceedings, and roports of a pertinent topic in the shock and vibration field. A literature review should stress important recent technology. Only pertinent literature should be Cttöb. Illustrations are encouraged. Detailed mathematical derivations are discouraged, rather, simple formulas representing results should be used. When complex formulas cannot be avoided, a functional form should be used so that readers wilt understand the interaction between parameters and variables

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Manuscripts must be typed (double-spaced) and figures attached. It is strongly recommended that line figures be rendered in ink or heavy pencil and neatly labeled. Photographs must be unscreened glossy black and white prints. The format for references shown in DIGEST articles ts to be followed

Manuscripts must begin with a brief abstract, or summary. Only material referred to in the text should be included in the list of References at the end of the article. References should be cited tn text by cpnsecu- tive numbers in brackets, as in the example below.

Unfortunately, tuch Information it often un- reliable, particularly statistical data partinant to a reliability niaiiment, at hat baan previout- lv noted ID.

Critical and certain ralatad axcitatlon» ware fint applied to tha problem of attesting tyttem reliability almoat a decade ago (21. Since then, the variation* that heve been developed and tha practical application« that have been explored [3-7! indicate that. . .

The format and style for the list of References at the end of the article are as follows:

• each citation number at It appeen in text (not in alphabetical order)

• Istt name of author/editor followed by initial« or fint name

• titlet Of articles within quotation*, title* of book« underlined

• abbreviated title of Journal in which article wat published (tee Periodicals Scanned list in January, Juno, and December issues)

* volume, number or ittue, and pages for journals; publisher for books

e year of publication in parenthetet

A sample reference list is given below.

1 Platzet, M.F., 'Trantonic Blade Flutter - A Survey." Shock Vib. Dig...7 (7), pp 97-106 (July 1976).

2. Bisplinghoft. R.L.. Ashley, H , and Half man, R.L., Aeroelatticlty, Addition-Wetley (1S55).

Jones, W.P., (Ed.). "Manual on Aeroelastio- ty," Part II, Aerodynamic Aspect*. Advltory Group Aeronaut. Ret. Devel. (19671.

Lin, C.C., Retainer, E., and Ttien, H., "On Two Dimensional Nontteady Motion of a Slender Body in a Compretiible Fluid," J. Math. Phy*., 27 (3), pp 220-231 (1948).

Transonic Flow, Landahl, M., IJnjteedjL Pergemon Pre*» (1961).

6 Miles, J.W., 'The Compressible Flow Past an Otcillatlng Airfoil In a Wind Tunnel," J. Aeronaut Sei., 22 <*). PP 671-678 (1956).

7. Lane, F., "Supertonic Flow Past an Otcil- latlng Caecede with Supertonic Leading Edge L_OCU»," J. Aeronaut. Sei., 24. (1), PP 65-66 (1957).

Articles for the DIGEST will be reviewed for technical content and edited for style and format. Before an article is submitted, the topic area should be cleared with the editors of the DIGEST. Literature review topics are assigned on a first come basis. Topics should be narrow and well defined. Articles should be 1500 to 2500 words in length. For additional information on topics and editorial policies, please contact:

MildaZ. Tamulicnis Research Editor

Vibration Institute 101 W. &5th Street, Suite 206 Clarendon Hills, Illinois 60514

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THE SHOCK AND VIBRATION OlGEST

Volume 15, No. 7 July 1983

EDITORIAL

1 SVIC Note« 2 Editor* Rattle Space

ARTICLES AND REVIEWS

3

27

IS

17

Feature Article - INDUSTRIAL NOISE CONTROL: THE PAST THREE YEARS; . Ft.J. Peppin)

Literature Review

- INSTABILITY OF CIRCULAR CYL- INDER ARRAYS IN CROSS FLOW I S.S. Chen

^-"IMONSTATIONARY RESONANCE OSCDLLATIONSy *>«->/■ , B.N. Agrawal and R.M. Evarvlwan owski ^""

34 Book Reviews

CURRENT NEWS

37 Short Couraea

ABSTRACTS FROM THE CURRENT LITERATURE ' er~ "

40 Abstract Content» 41 Abstracts. 83 1279 to 83-1497 91 Author Index

CALENDAR

THE SHOCK AND VIBRATION DIGEST · 2016. 1. 28. · vibration theory, it is a natural application...

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