AGMA index

iAugust 2006 Publications Catalog

AGMACatalog of Technical Publications

1990 -- 2006

TABLE OF CONTENTS

Topic Page

American Gear Manufacturers Association ii. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .How to Purchase Documents iii. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Index of AGMA Standards and Information Sheets by Number 1. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Index of AGMA Standards and Information Sheets by Topic 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

Aerospace 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Calibration and Measurement Uncertainty 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Couplings 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Design and Assembly -- Bevel 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Design -- Fine Pitch 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Design -- Sound and Vibration 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Design -- Spur and Helical 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Design -- Wormgear 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Drive Components 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Enclosed Drives 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Failure Modes 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .High Speed Units 5. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Inspection and Tolerances 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Lubrication 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Materials 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Metric Usage 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Nomenclature 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Plastics Gears 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Powder Metallurgy Gears 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Proportions 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Rating: Spur, Helical and Bevel Gears 6. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Sound and Noise 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Style Manual 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Thermal 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Vehicle 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Wind Turbine Units 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Wormgears 7. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

AGMA Standards and Information Sheets 9. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .ISO Standards by Technical Committee 60 19. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Gear Software 20. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .Fall Technical Meeting Papers: 1990 -- 2005 21. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2005 PAPERS 21. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2004 PAPERS 25. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2002 PAPERS 28. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2001 PAPERS 30. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2000 PAPERS 32. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1999 PAPERS 33. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1998 PAPERS 36. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1997 PAPERS 37. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1996 PAPERS 39. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1995 PAPERS 42. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1994 PAPERS 44. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1993 PAPERS 46. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1992 PAPERS 48. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1991 PAPERS 50. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1990 PAPERS 52. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

ii August 2006Publications Catalog

American Gear Manufacturers Association

AGMA is a voluntary association of companies, consultants and academicians with a direct interest in the design,manufacture, and application of gears and flexible couplings. AGMA was founded in 1916 by nine companies inresponse to the market demand for standardized gear products; it remains a member-- and market--drivenorganization to this day. AGMA provides a wide variety of services to the gear industry and its customers andconducts numerous programs which support these services. Some of these services and programs are:

D STANDARDS: AGMA develops all U.S. gear related standards through an open process under theauthorization of the American National Standards Institute (ANSI).

D ISO PARTICIPATION: AGMA is Secretariat to TC60, the committee responsible for developing allinternational gear standards. TC60 is an ISO (International Organization of Standardization) committee.

D MARKET REPORTS AND STATISTICS: AGMA’s Operating Ratio Report, Wage & Benefit Survey, andMonthlyMarket TrendReports help you stay competitive by giving you up--to--date information on the gearindustry.

D THE MARKETING AND STATISTICAL COUNCILS enhance your competitiveness by sharinginformation and by developing creative solutions to common industry problems.

D THEPUBLICAFFAIRSCOUNCIL gives you an active voice inWashington, promoting the gear industry toour nation’s legislators and regulators.

D GEAR EXPO: This is the only trade show dedicated solely to the gear industry.

D TECHNICAL COMMITTEEMEETINGS are the core of the open AGMA standard writing process keepingmembers abreast of new developments while ensuring that AGMA standards are kept current.

D THE AGMA TRAINING SCHOOL FOR GEAR MANUFACTURING uses current technology to offerhands--on training in hobbing, shaping, and inspection. At the ”Gear School”, operators learn how tomaximize their productivity. Enrollment is open to all.

D NEWS DIGEST, AGMA’s quarterly newsletter, offers you timely, useful information you can useimmediately.

If you would like additional information about our programs, or on how to become a member of AGMA, pleasecontact AGMA Headquarters.

American Gear Manufacturers Association500 Montgomery Street, Suite 350

Alexandria, VA 22314--1560

Phone: (703) 684--0211FAX: (703) 684--0242

E--Mail: [email protected]: www.agma.org

Leading the Gear Industry Since 1916

iiiAugust 2006 Publications Catalog

How to Purchase Documents

Unless otherwise indicated, all current AGMAStandards, Information Sheets and paperspresented at Fall Technical Meetings are

available for purchase, in electronic form,through the AGMA website, www.agma.org.

1August 2006 Publications Catalog

Obsolete documents should not be used, please use replacements. Most obsoleteand superseded documents are available for puchase. Contact AGMA Headquarters

for price and availability.

Index of AGMA Standards and Information Sheets by NumberItalicizing denotes a current standard

Number Page Title or reference

110.04 Replaced by 1010--E95

112.05 Incorporated into 1012--G05

114.02 Replaced by 910--C90

115.01 Replaced by 933--A03

116.01 Incorporated into 1012--G05


120.01 Withdrawn

121.02 Replaced by 120.01




141.01 Withdrawn


170.01 Replaced by 6002--B93

201.02 Withdrawn

202.03 Replaced by 2005--C96

203.03 Withdrawn

207.06 Replaced by 1003--G93

208.03 Replaced by 2005--C96

209.04 Replaced by 2005--C96


211.02A Replaced by 420.04

212.02 Replaced by 2003--B97

215.02 Replaced by 218.01 &2003--B97

216.01 Replaced by 2003--B97


217.01 Withdrawn

218.01 Replaced by 2001--D04 &908--B89



222.02 Replaced by 2003--B97


223.02 Replaced by 2003--B97

224.01 Incorporated into 240.01



226.01 Replaced by 908--B89

230.01 Replaced by 2007--C00

231.52 Replaced by 2002--B88

234.01 Replaced by 390.03a

235.02 Replaced by 2000--A88

236.05 Replaced by 390.03a


239.01 Replaced by 2000--A88

239.01A Replaced by 390.03a

240.01 Replaced by 2004--B89










246.02A Replaced by 926--A99




250.04 Replaced by 9005--E02

251.02 Replaced by 9005--E02



255.03 Replaced by 6001--D97

260.02 Replaced by 6001--D97

265.01 Replaced by 6001--D97



295.04 Replaced by 6025--D98

297.01 Replaced by 6025-- D98

298.01 Replaced by 6025-- D98


321.05 Replaced by 6004--F88

323.01 Replaced by 6005--B89



2 August 2006Publications Catalog


330.01 Replaced by 2005--C96

331.01 Replaced by 2008--C01

341.02 Replaced by 6022--C93

342.02 Replaced by 6035--A02

360.02 Withdrawn


374.04 Withdrawn

390.03 Replaced by 390.03a &2000--A88

390.03a Replaced by 2009--B01 and2011--A98


420.04 Replaced by 6010--F97

421.06 Replaced by 6011--i03

422.03 Withdrawn


424.01 Withdrawn


426.01 Replaced by 6000--B96

427.01 Incorporated into 6011--H98


431.01 Withdrawn

440.04 Replaced by 6034--A87

441.04 Replaced by 6035--A02

442.01 Replaced by 6035--A02

460.05 Replaced by 6019--E89

461.01 Replaced by 6035--A02

480.06 Replaced by 6021--G89

481.01 Replaced by 6021--G89

510.03 Replaced by 9009--D02

511.02 Replaced by 9002--A86

512.01 Replaced by 9002--A86

513.01 Replaced by 9002--A86

514.02 Withdrawn

515.02 Replaced by 9000--C90

516.01 Replaced by 9008--B00


900--G00 9 Style Manual for thePreparation of Standards,Information Sheets andEditorial Manuals

901--A92 9 Procedure for thePreliminary Design ofMinimum Volume Gears

904--C96 9 Metric Usage


906--A94 Withdrawn

908--B89 9 Geometry Factors forDetermining the PittingResistance and BendingStrength of Spur, Helicaland Herringbone GearTeeth

910--C90 9 Formats for Fine--PitchGear Specification Data

911--A94 9 Design Guidelines forAerospace Gearing

912--A04 9 Mechanisms of Gear ToothFailure

913--A98 9 Method for Specifying theGeometry of Spur andHelical Gears

914--B04 10 Gear Sound Manual -- PartI: Fundamentals of Soundas Related to Gears; Part II:Sources, Specifications andLevels of Gear Sound; PartIII: Gear Noise Control

915--1--A02 10 Inspection Practices -- Part1: Cylindrical Gears --Tangential Measurements

915--2--A05 10 Inspection Practices -- Part2: Cylindrical Gears --Radial Measurements

915--3--A99 10 Inspection Practices -- GearBlanks, Shaft CenterDistance and Parallelism

917--B97 10 Design Manual for ParallelShaft Fine--Pitch Gearing

918--A93 10 Numerical ExamplesDemonstrating theProcedures for CalculatingGeometry Factors for Spurand Helical Gears

920--A01 10 Materials for Plastic Gears

921--A97 Replaced by 6006--A03

922--A96 10 Load Classification andService Factors for FlexibleCouplings

923--B05 10 Metallurgical Specificationsfor Steel Gearing

925--A03 11 Effect of Lubrication onGear Surface Distress

926--C99 11 Recommended Practice forCarburized AerospaceGearing

927--A01 11 Load Distribution Factors --Analytical Methods forCylindrical Gears





930--A05 11 Calculated Bending LoadCapacity of PowderMetallurgy (P/M) ExternalSpur Gears

931--A02 11 Calibration of GearMeasuring Instruments andTheir Application to theInspection of Product Gears

932--A05 11 Rating the PittingResistance and BendingStrength of Hypoid Gears

933--A03 11 Basic Gear Geometry

935--A05 11 Recommendations Relativeto the Evaluation of RadialComposite Gear DoubleFlank Testers

938--A05 12 Shot Peening of Gears

1003--G93 12 Tooth Proportions forFine--Pitch Spur and HelicalGears

1006--A97 12 Tooth Proportions for PlasticGears

1010--E95 12 Appearance of Gear Teeth --Terminology of Wear andFailure

1012--G05 12 Gear Nomenclature,Definitions of Terms withSymbols

1102--A03 12 Tolerance Specification forGear Hobs

1106--A97 12 Tooth Proportions for PlasticGears

1328--1 12 Cylindrical Gears -- ISOSystem of Accuracy -- Part1: Definitions and AllowableValues of DeviationsRelevant to CorrespondingFlanks of Gear Teeth

1328--2 12 Cylindrical Gears -- ISOSystem of Accuracy -- Part2: Definitions and AllowableValues of DeviationsRelevant to RadialComposite Deviations andRunout Information

2000--A88 Replaced by 915--1--A02,915--2--A05, 2015--1--A01,and 2015--2--A06

2001--D04 13 Fundamental Rating Factorsand Calculation Methods forInvolute Spur and HelicalGear Teeth


2002--B88 13 Tooth ThicknessSpecification andMeasurement

2003--B97 13 Rating the PittingResistance and BendingStrength of GeneratedStraight Bevel, Zerol Bevel,and Spiral Bevel Gear Teeth

2004--B89 13 Gear Materials and HeatTreatment Manual

2005--D03 13 Design Manual for BevelGears

2007--C00 13 Surface Temper EtchInspection After Grinding

2008--C01 13 Assembling Bevel Gears

2009--B01 13 Bevel Gear Classification,Tolerances, and MeasuringMethods

2010--A94 13 Measuring InstrumentCalibration ---- Part I,Involute Measurement

2011--A98 14 Cylindrical WormgearingTolerance and InspectionMethods

2015--1--A01 14 Accuracy ClassificationSystem -- TangentialMeasurements forCylindrical Gears

2015--2--A06 14 Accuracy ClassificationSystem -- RadialMeasurements forCylindrical Gears

Supplementto 2015/915--1--A02

14 Accuracy ClassificationSystem -- TangentialMeasurement ToleranceTables for Cylindrical Gears

2101--D04 14 Fundamental Rating Factorsand Calculation Methods forInvolute Spur and HelicalGear Teeth (Metric)

2110--A94 14 Measuring InstrumentCalibration ---- Part I,Involute Measurement(Metric)

2111--A98 14 Cylindrical WormgearingTolerance and InspectionMethods (Metric)

2113--A97 14 Measuring InstrumentCalibration, Gear ToothAlignment

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2114--A98 15 Measuring InstrumentCalibration, Gear Pitch andRunout Measurements

2116--A05 15 Evaluation of Double FlankTesters for RadialComposite Measurement ofGears

6000--B96 15 Measurement of LinearVibration on Gear Units

6001--D97 15 Design and Selection ofComponents for EnclosedGear Drives

6002--B93 15 Design Guide for VehicleSpur and Helical Gears

6004--F88 Withdrawn

6005--B89 Withdrawn

6006--A03 15 Standard for Design andSpecification of Gearboxesfor Wind Turbines

6008--A98 15 Specifications for PowderMetallurgy Gears

6009--A00 Replaced by 6013--A06

6010--F97 Replaced by 6013--A06

6011--I03 15 Specification for High SpeedHelical Gear Units

6013--A06 16 Standard for IndustrialEnclosed Gear Drives

6017--E86 Replaced by 6035--A02

6019--E89 Replaced by 6009--A00

6021--G89 Replaced by 6009--A00

6022--C93 16 Design Manual forCylindrical Wormgearing

6023--A88 16 Design Manual for EnclosedEpicyclic Gear Drives

6025--D98 16 Sound for Enclosed Helical,Herringbone and SpiralBevel Gear Drives

6030--C87 Replaced by 6035--A02

6032--A94 16 Standard for Marine GearUnits: Rating

6033--B98 16 Materials for MarinePropulsion Gearing

6034--B92 16 Practice for EnclosedCylindrical WormgearSpeed Reducers andGearmotors

6035--A02 16 Design, Rating andApplication of IndustrialGloboidal Wormgearing


6109--A00 Replaced by 6113--A06

6110--F97 Replaced by 6113--A06

6113--A06 17 Standard for IndustrialEnclosed Drives (Metric)

6123--A88 17 Design Manual for EnclosedEpicyclic Metric ModuleGear Drives

6133--B98 17 Materials for MarinePropulsion Gearing (Metric)

6135--A02 17 Design, Rating andApplication of IndustrialGloboidal Wormgearing(Metric)

9000--C90 17 Flexible Couplings --Potential UnbalanceClassification

9001--B97 17 Flexible Couplings --Lubrication

9002--B04 17 Bores and Keyways forFlexible Couplings (InchSeries)

9003--A91 17 Flexible Couplings --Keyless Fits

9004--A99 17 Flexible Couplings -- MassElastic Properties and OtherCharacteristics

9005--E02 18 Industrial Gear Lubrication

9008--B00 18 Flexible Couplings – GearType – Flange Dimensions,Inch Series

9009--D02 18 Flexible Couplings --Nomenclature for FlexibleCouplings

9112--A04 18 Bores and Keyways forFlexible Couplings (MetricSeries)

10064--1 18 Cylindrical Gears -- Code ofInspection Practice -- Part 1:Inspection of CorrespondingFlanks of Gear Teeth

10064--2 18 Cylindrical Gears -- Code ofInspection Practice -- Part 2:Inspection Related to RadialComposite Deviations,Runout, Tooth Thicknessand Backlash

14179--1 18 Gear Reducers -- ThermalCapacity Based on ISO/TR14179--1


Index of AGMA Standards and Information Sheets by Topic

Aerospace

AGMA 911--A94 Design Guidelines for AerospaceGearing.

AGMA 926--C99 Recommended Practice forCarburized Aerospace Gearing.

Calibration and Measurement Uncertainty

AGMA 931--A02 Calibration of Gear MeasuringInstruments and Their Application to the Inspection ofProduct Gears.

AGMA 935--A05 Recommendations Relative to theEvaluation of Radial Composite Gear Double FlankTesters.

ANSI/AGMA 2010--A94 Measuring MachineCalibration -- Part I, Involute Measurement.

ANSI/AGMA 2110--A94 Measuring InstrumentCalibration -- Part I, Involute Measurement (Metric).

ANSI/AGMA 2111--A98 Cylindrical WormgearingTolerance and Inspection Methods (Metric).

ANSI/AGMA 2113--A97 Measuring InstrumentCalibration, Gear Tooth Alignment Measurement.

ANSI/AGMA 2114--A98 Measuring InstrumentCalibration, Gear Pitch and Runout Measurements.

ANSI/AGMA 2116--A05, Evaluation of Double FlankTesters for Radial Composite Measurement of Gears.

Couplings

AGMA 922--A96 Load Classification and ServiceFactors for Flexible Couplings.

ANSI/AGMA 9000--C90 Flexible Couplings --Potential Unbalance Classification.

ANSI/AGMA 9001--B97 Flexible Couplings --Lubrication.

ANSI/AGMA 9002--B04 Bores and Keyways forFlexible Couplings (Inch Series).

ANSI/AGMA 9003--A91 Flexible Couplings -- KeylessFits.

ANSI/AGMA 9004--A99 Flexible Couplings -- MassElastic Properties and Other Characteristics.

ANSI/AGMA 9008--B00 Flexible Couplings – GearType – Flange Dimensions, Inch Series.

ANSI/AGMA 9009--D02 Flexible Couplings --Nomenclature for Flexible Couplings.

ANSI/AGMA 9112--A04 Bores and Keyways forFlexible Couplings (Metric Series).

Design and Assembly - Bevel

ANSI/AGMA 2005--D03 Design Manual for BevelGears.

ANSI/AGMA 2008--C01 Assembling Bevel Gears.

Design - Fine Pitch

AGMA 910--C90 Formats for Fine--Pitch GearSpecification Data.

AGMA 917--B97 Design Manual for Parallel ShaftFine--Pitch Gearing.

Design - Sound and Vibration

ANSI/AGMA 6000--B96 Specification forMeasurement of Linear Vibration on Gear Units.

ANSI/AGMA 6025--D98 Sound for Enclosed Helical,Herringbone, and Spiral Bevel Gear Drives. Refer topage 15.

Design - Spur and Helical

AGMA 901--A92 A Rational Procedure for thePreliminary Design of Minimum Volume Gears.

AGMA 913--A98Method for Specifying the Geometryof Spur and Helical Gears.

Design - Wormgear

ANSI/AGMA 6022--C93 Design of General IndustrialCoarse--Pitch Cylindrical Wormgearing.

Drive Components

ANSI/AGMA 6001--D97 Design and Selection ofComponents for Enclosed Gear Drives.

Enclosed Drives

AGMA ISO 14179--1 Gear Reducers -- ThermalCapacity Based on ISO/TR 14179--1

ANSI/AGMA 6013--A06 Standard for IndustrialEnclosed Gear Drives

ANSI/AGMA 6113--A06 Standard for IndustrialEnclosed Gear Drives (Metric)

ANSI/AGMA 6023--A88 Design Manual for EnclosedEpicyclic Gear Drives.

ANSI/AGMA 6123--A88 Design Manual for EnclosedEpicyclic Metric Module Gear Drives.

Failure Modes

AGMA 912--A04, Mechanisms of Gear Tooth Failure.

ANSI/AGMA 1010--E95 Appearance of Gear Teeth --Terminology of Wear and Failure.

High Speed Units

ANSI/AGMA 6011--I03 Specification for High SpeedHelical Gear Units.


Inspection and Tolerances

AGMA 915--1--A02 Inspection Practices -- Part 1:Cylindrical Gears -- Tangential Measurements.

AGMA 915--2--A05 Inspection Practices -- Part 2:Cylindrical Gears -- Radial Measurements.

AGMA 915--3--A99 Inspection Practices -- GearBlanks, Shaft Center Distance and Parallelism.

ANSI/AGMA 1102--A03, Tolerance Specification forGear Hobs.

ANSI/AGMA ISO 1328--1 Cylindrical Gears -- ISOSystem of Accuracy -- Part 1: Definitions andAllowable Values of Deviations Relevant toCorresponding Flanks of Gear Teeth.

ANSI/AGMA ISO 1328--2 Cylindrical Gears -- ISOSystem of Accuracy -- Part 2: Definitions andAllowable Values of Deviations Relevant to RadialComposite Deviations and Runout Information.

ANSI/AGMA 2002--B88 Tooth ThicknessSpecification and Measurement.

ANSI/AGMA 2007--C00 Surface Temper EtchInspection After Grinding.

ANSI/AGMA 2009--B01 Bevel Gear Classification,Tolerances, and Measuring Methods.

ANSI/AGMA 2011--A98 Cylindrical WormgearingTolerance and Inspection Methods.

ANSI/AGMA 2015--1--A01 Accuracy ClassificationSystem -- Tangential Measurements for CylindricalGears.

ANSI/AGMA 2015--2--A06 Accuracy ClassificationSystem -- Radial Measurements for Cylindrical Gears.

Supplemental Tables for AGMA 2015/915--1--A02Accuracy Classification System -- TangentialMeasurement Tolerance Tables for Cylindrical Gears.

AGMA ISO 10064--1 Cylindrical Gears -- Code ofInspection Practice -- Part 1: Inspection ofCorresponding Flanks of Gear Teeth.

AGMA ISO 10064--2 Cylindrical Gears -- Code ofInspection Practice -- Part 2: Inspection Related toRadial Composite Deviations, Runout, ToothThickness and Backlash.

Lubrication

ANSI/AGMA 9005--E02 Industrial Gear Lubrication.

Materials

AGMA 920--A01 Materials for Plastic Gears.

AGMA 923--B05Metallurgical Specifications for SteelGearing.

AGMA 938--A05, Shot Peening of Gears.

ANSI/AGMA 2004--B89 Gear Materials and HeatTreatment Manual.

ANSI/AGMA 6033--B98 Materials for MarinePropulsion Gearing.

ANSI/AGMA 6133--B98 Materials for MarinePropulsion Gearing (Metric).

Metric Usage

AGMA 904--C96 Metric Usage.

Nomenclature

AGMA 933--A03 Basic Gear Geometry.

ANSI/AGMA 1012--G05 Gear Nomenclature,Definitions of Terms with Symbols.

Plastics Gears

AGMA 920--A01 Materials for Plastic Gears.

ANSI/AGMA 1006--A97 Tooth Proportions for PlasticGears.


Powder Metallurgy Gears

AGMA930--A05CalculatedBendingLoadCapacity ofPowder Metallurgy (P/M) External Spur Gears.

ANSI/AGMA 6008--A98 Specifications for PowderMetallurgy Gears.

Proportions

ANSI/AGMA 1003--G93 Tooth Proportions forFine--Pitch Spur and Helical Gears.


ANSI/AGMA 1106--A97 Tooth Proportions for PlasticGears (Metric Edition).

Rating: Spur, Helical and Bevel Gears

AGMA 908--B89 Information Sheet--GeometryFactors for Determining the Pitting Resistance andBending Strength of Spur, Helical and HerringboneGear Teeth.

AGMA 918--A93 A Summary of Numerical ExamplesDemonstrating the Procedures for CalculatingGeometry Factors for Spur and Helical Gears.

AGMA925--A03Effect of Lubrication onGear SurfaceDistress.

AGMA 927--A01 Load Distribution Factors --Analytical Methods for Cylindrical Gears.

AGMA 932--A05 Rating the Pitting Resistance andBending Strength of Hypoid Gears.

ANSI/AGMA 2001--D04 Fundamental Rating Factorsand Calculation Methods for Involute Spur and HelicalGear Teeth.


ANSI/AGMA 2003--B97 Rating the Pitting Resistanceand Bending Strength of Generated Straight Bevel,ZEROL Bevel, and Spiral Bevel Gear Teeth.

ANSI/AGMA 2101--D04 Fundamental Rating Factorsand Calculation Methods for Involute Spur and HelicalGear Teeth (Metric Edition).

ANSI/AGMA 6032--A94 Standard for Marine GearUnits: Rating.

Sound and Noise

AGMA 914--B04 Gear Sound Manual -- Part I:Fundamentals of Sound as Related to Gears; Part II:Sources, Specifications and Levels of Gear Sound;Part III: Gear Noise Control.

Style Manual

AGMA 900--G00 Style Manual for the Preparation ofStandards and Editorial Manuals.

Thermal

AGMA ISO 14179--1 Gear Reducers -- ThermalCapacity Based on ISO/TR 14179--1.

Vehicle

ANSI/AGMA 6002--B93 Design Guide for VehicleSpur and Helical Gears.

Wind Turbine Units

ANSI/AGMA/AWEA 6006--A03 Standard for Designand Specification of Gearboxes for Wind Turbines.

Wormgears

ANSI/AGMA 6034--B92 Practice for EnclosedCylindrical Wormgear Speed Reducers andGearmotors.

ANSI/AGMA 6035--A02 Design, Rating andApplication of Industrial Globoidal Wormgearing.

ANSI/AGMA 6135--A02 Design, Rating andApplication of Industrial Globoidal Wormgearing(Metric).


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AGMA Standards and Information Sheets

Many standards require additional documents for their proper use. A list of these standards are normallysupplied after the scope, in the normative references section of a document. Be sure to inquire whether thestandard you need requires other documents listed herewith.

AGMA 900--G00 Style Manual for the Preparationof Standards, Information Sheets and EditorialManuals

Presents the requirements for preparing AGMAstandards, editorial manuals, and other technicalliterature. A new annex ”ISO symbols used in metricdocuments”, has been added, which includes acomprehensive listing of the symbols used in ISOgear rating standards. Revision of AGMA 900--F96.ISBN: 1--55589--775--4 Pages: 38

AGMA 901--A92 (R1997) A Rational Procedure forthe Preliminary Design of Minimum Volume Gears

Presents a simple, closed--form procedure as a firststep in the minimum volume spur and helical gearsetdesign. Includesmethods for selecting geometry anddimensions, considering maximum pitting resistance,bending strength, and scuffing resistance, andmethods for selecting profile shift.ISBN: 1--55589--579--4 Pages: 37

AGMA 904--C96 Metric UsageServes as a guide in preparing AGMA metricstandards.ISBN: 1--55589--681--2 Pages: 20

AGMA 908--B89 (R1999) Information Sheet -Geometry Factors for Determining the PittingResistance and Bending Strength of Spur, Helicaland Herringbone Gear Teeth

Gives the equations for calculating the pittingresistance geometry factor, I, for external and internalspur and helical gears, and the bending strengthgeometry factor, J, for external spur and helical gearsthat are generated by rack--type tools (hobs, rackcutters or generating grinding wheels) or pinion--typetools (shaper cutters). Includes charts which providegeometry factors, I and J, for a range of typical gearsets and tooth forms.ISBN: 1--55589--525--5 Pages: 78

AGMA 910--C90 (R2003) Formats for Fine-PitchGear Specification Data

Consists of a series of printed forms for gear drawingsthat contain the appropriate data the gear designermust tabulate for the gear manufacturer. Includes a

series of definitions of the various tabulated items.Appendix contains blank, pre--printed forms that caneasily be copied for the user’s drawings.ISBN: 1--55589--571--9 Pages: 29

AGMA 911--A94 (R2000) Guidelines for AerospaceGearing

Covers current gear design practices as they areapplied to air vehicles and spacecraft. Goes beyondthe design of gear meshes. Presents the broadspectrum of factors which combine to produce aworking gear system, whether it be a powertransmission or special purpose mechanism. Coversonly spur, helical and bevel gears. (Does not coverwormgears, face gears, and various proprietary toothforms). Replaces AGMA 411.02.ISBN: 1--55589--629--4 Pages: 97

AGMA 912--A04, Mechanisms of Gear ToothFailure

This information sheet describes many of the ways inwhich gear teeth can fail and recommends methodsfor reducing gear failure. It provides guidance forthose attempting to analyze gear failures. It should beused in conjunction with ANSI/AGMA 1010--E95 inwhich the gear tooth failure modes are defined. Theyare described in detail to help investigatorsunderstand failures and investigate remedies. Thisinformation sheet does not discuss the details ofdisciplines such as dynamics, material science,corrosion or tribology. It is hoped that the materialpresented will facilitate communication in theinvestigation of gear operating problems.Supplement to ANSI/AGMA 1010--E95.ISBN: 1--55589--838--6 Pages: 22

AGMA 913--A98 Method for Specifying theGeometry of Spur and Helical Gears

Provides information to translate tooth thicknessspecifications which are expressed in terms of tooththickness, center distance or diameter into profile shiftcoefficients. It describes the effect that profile shifthas on the geometry and performance of gears.Annexes are provided which contain practicalexamples on the calculation of tool proportions andprofile shift.ISBN: 1--55589--714--2 Pages: 25



AGMA 914--B04, Gear Sound Manual - Part I:Fundamentals of Sound as Related to Gears; PartII: Sources, Specifications and Levels of GearSound; Part III: Gear Noise Control

This information sheet discusses how noisemeasurement and control depend upon the individualcharacteristics of the prime mover, gear unit, anddriven machine, as well as their combined effects in aparticular acoustical environment. It indicates certainareas that might require special attention. Thisdocument is a revision of AGMA 299.01 to includeupdated references and a discussion of Fast FourierTransform analysis. Replaces AGMA 299.01.ISBN: 1--55589--820--3 Pages: 37

AGMA 915--1--A02 Inspection Practices - Part 1:Cylindrical Gears - Tangential Measurements

Provides a code of practice and measuring methodsdealing with inspection relevant to tangential elementand composite deviations of cylindrical involute gears(measurements referred to single flank contact).Replaces elemental measurement section ofAGMA 2000--A88.ISBN: 1--55589--798--3 Pages: 39

AGMA 915--2--A05 Inspection Practices - Part 2:Cylindrical Gears - Radial Measurements

This information sheet discusses inspection ofcylindrical involute gears using the radial (doubleflank) composite method, with recommendedpractices detailed. Also included is a clause on runoutand eccentricity measurement methods. Thisinformation sheet is a supplement to the standardANSI/AGMA 2015--2--A06. It replaced AGMA ISO10064--2 and replaces double flank compositemeasurement section of AGMA 2000--A88.ISBN: 1--55589--843--2 Pages: 24

AGMA 915--3--A99 Inspection Practices - GearBlanks, Shaft Center Distance and Parallelism

Provides recommended numerical values relating tothe inspection of gear blanks, shaft center distanceand parallelism of shaft axes. Discussions includesuch topics as methods for defining datum axes oncomponents; the use of center holes and mountingsurfaces during manufacturing and inspection; and,recommended values of in--plane and out--of--planedeviations of shaft parallelism. Modified adoption ofISO/TR 10064--3:1996.ISBN: 1--55589--738--X Pages: 9

AGMA917--B97 (R2003)DesignManual forParallelShaft Fine-Pitch Gearing

Provides guidance for the design of spur and helicalgearing of 20 through 120 diametral pitch includinginternal and rack forms. Manual contains suchspecialized subjects as inspection, lubrication, gearload calculation methods, materials, including a widevariety of plastics. Replaces AGMA 370.01.ISBN: 1--55589--694--4 Pages: 84

AGMA 918--A93 (R1998) A Summary of NumericalExamples Demonstrating the Procedures forCalculatingGeometry Factors for Spur andHelicalGears

Provides numerical examples for calculating thepitting resistance geometry factor, I, and bendingstrength geometry factor, J, for typical gearsets thatare generated by rack-- type tools (hobs, rack cuttersor generating grinding wheels) or pinion--type tools(disk--type shaper cutters). Supplement to AGMA908--B89.ISBN: 1--55589--617--0 Pages: 42

AGMA 920--A01 Materials for Plastic GearsThis document serves to aid the gear designer inunderstanding the unique physical, mechanical andthermal behavior of plastic materials. Topics coveredinclude general plastic material behavior, gearoperating conditions, plastic gear manufacturing,tests for gear related material properties, and typicalplastic gear materials.ISBN: 1--55589--778--9 Pages: 40

AGMA 922--A96 Load Classification and ServiceFactors for Flexible Couplings

This Information Sheet provides load classificationsand related service factors that are frequently used forvarious flexible coupling applications. Typicalapplications using smooth prime movers and specialconsiderations involving unusual or more severeloading are discussed. Replaces AGMA 514.02.ISBN: 1--55589--680--4 Pages: 6

AGMA 923--B05 Metallurgical Specifications forSteel Gearing

This document identifies metallurgical qualitycharacteristics which are important to theperformance of steel gearing. The AGMA gear ratingstandards identify performance levels of gearing byheat treatment method and grade number. For eachheat treatment method and AGMA grade number,acceptance criteria are given for various metallurgicalcharacteristics identified in this document. Revisionof AGMA 923--A00.ISBN: 1--55589--848--3 Pages: 31



AGMA 925--A03 Effect of Lubrication on GearSurface Distress

This document provides currently availableinformation pertaining to oil lubrication of industrialgears for power transmission applications. It isintended to serve as a general guideline and source ofinformation about gear oils, their properties, and theirtribological behavior in gear contacts. Equationsprovided allow the calculation of specific filmthickness and instantaneous contact (flash)temperature for gears in service, and to help assessthe potential risk of surface distress (scuffing,micropitting and macropitting, and scoring) involvedwith a given lubricant choice. Supplement toANSI/AGMA 2001--D04.ISBN: 1--55589--815--7 Pages: 51

AGMA 926--C99 Recommended Practice forCarburized Aerospace Gearing

Establishes recommended practices for materialcase and core properties, microstructure andprocessing procedures for carburized AISI 9310aerospace gears. This document is not intended to bea practice for any gears other than those applied toaerospace. Replaces AGMA 246.02a.ISBN: 1--55589--758--4 Pages: 9

AGMA 927--A01 Load Distribution Factors -Analytical Methods for Cylindrical Gears

Describes an analytical procedure for the calculationof face load distribution factor. The iterative solutionthat is described is compatible with the definitions ofthe term face loaddistribution of AGMAstandards andlongitudinal load distribution of the ISO standards.The procedure is easily programmable and flowcharts of the calculation scheme, as well as examplesfrom typical software are presented. Supplement toANSI/AGMA 2001--D04.ISBN: 1--55589--779--7 Pages: 31

AGMA 930--A05, Calculated Bending LoadCapacity of PowderMetallurgy (P/M) External SpurGears

This information sheet describes a procedure forcalculating the load capacity of a pair of powdermetallurgy external spur gears based on toothbending strength. Two types of loading areconsidered: 1) repeated loading over many cycles;and 2) occasional peak loading. It also describes anessentially reverse procedure for establishing aninitial design from specified applied loads. As part ofthe load capacity calculations, there is a detailedanalysis of the gear teeth geometry, including toothprofiles and various fillets.ISBN: 1--55589--845--9 Pages: 78

AGMA 931--A02 Calibration of Gear MeasuringInstruments and Their Application to theInspection of Product Gears

Provides guidelines for the alignment of suchinstrument elements as centers, ways and probesystems. The instrument accuracy requirementsneeded to meet the accuracy of product gears isdiscussed. It also covers the application of gearartifacts to determine instrument accuracy. Thisinvolved the calculation of U95 uncertainty at all stepsfrom the artifact to the final product gears. Thisdocument serves tosupplement current calibrationstandards ANSI/AGMA 2110--A94, ANSI/AGMA2113--A97, and ANSI/AGMA 2114--A98ISBN: 1--55589--799--1 Pages: 29

!! NEW !!

AGMA 932--A05 Rating the Pitting Resistance andBending Strength of Hypoid Gears

This information sheet provides a method by whichdifferent hypoid gear designs can be compared. Theformulas are intended to establish a uniformlyacceptable method for calculating the pittingresistance and bending strength capacity of bothcurved and skewed tooth hypoid gears. They applyequally to tapered depth and uniform depth teeth.Annexes contain graphs for geometry factors and asample calculation to assist the user. Supplement toANSI/AGMA 2003--B97.ISBN: 1--55589--869--6 Pages: 18

AGMA 933--B03 Basic Gear GeometryThis information sheet illustrates importantgeometrical relationships which provide a soundbasis for a thoroughly logical and comprehensivesystem of gear geometry. Replaces AGMA 115.01.ISBN: 1--55589--814--9 Pages: 18

AGMA 935--A05, Recommendations Relative tothe Evaluation of Radial Composite Gear DoubleFlank Testers

The condition and alignment of gear measuringinstruments can greatly influence themeasurement ofproduct gears. This information sheet providesqualification procedures for double flank testers thatare used for the evaluation of radial compositedeviations of gears. It discusses guidelines foralignment of double flank tester elements such ascenters, ways, probe systems, etc. It also covers theapplication of artifacts to determine instrumentaccuracy. This information sheet is a supplement tostandard ANSI/AGMA 2116--A05.ISBN: 1--55589--872--6 Pages: 11



!! NEW !!

AGMA 938--A05, Shot Peening of GearsThis information sheet provides a tool for geardesigners interested in the residual compressivestress properties produced by shot peening and itsrelationship to gearing. It also discusses shot mediamaterials, delivery methods and process controls.ISBN: 1--55589--847--5 Pages: 14

ANSI/AGMA 1003--G93 (R1999) Tooth Proportionsfor Fine-Pitch Spur and Helical Gears

Includes spur and helical gearing of 20 through 120diametral pitch with tooth proportions of 20 degreepressure angle and having 7 or more teeth. Toothproportions shown may also be suitable for geardesigns of finer than 120 diametral pitch.ISBN: 1--55589--015--6 Pages: 24

ANSI/AGMA 1006--A97 (R2003) Tooth Proportionsfor Plastic Gears

Presents a new basic rack, AGMA PT, which, with itsfull round fillet, may be preferred in many applicationsof gears made from plastic materials. It contains adescription, with equations and sample calculations,of how the proportions of a spur or helical gearmay bederived from the design tooth thickness and the basicrack data. In several annexes, there are discussionsof possible variations from the basic rack and also aprocedure for defining tooth proportions without usingthe basic rack concept.ISBN: 1--55589--684--7 Pages: 47

ANSI/AGMA 1010--E95 (R2000) Appearance ofGear Teeth -Terminology of Wear and Failure

This standard provides nomenclature for generalmodes of gear tooth wear and failure. It classifies,identifies and describes the most common types offailure and provides information which will, in manycases, enable the user to identify failure modes andevaluate the degree or progression of wear.Replaces AGMA 110.04.ISBN: 1--55589--665--0 Pages: 40

ANSI/AGMA 1012--G05, Gear Nomenclature,Definitions of Terms with Symbols

This standard establishes the definitions of terms,symbols and abbreviations which may be used tocommunicate the technology and specifications ofexternal and internal gear teeth. it provides definitivemeanings by the use of words and illustrations, forcommonly used gearing terms. Revision ofANSI/AGMA 1012--F90.ISBN: 1--55589--846--7 Pages: 72

ANSI/AGMA 1102--A03, Tolerance Specificationfor Gear Hobs

Provides specifications for nomenclature,dimensions, equation based tolerances, andinspection practices for gear hobs. Defines aclassification system for accuracy grades D throughAAA, in order of increasing precision. The standarddescribes hob identification practices, manufacturingand purchasing considerations, and hob designparameters. An informative annex is included whichprovides the reader with a basic understanding of howthe different elements of a hob can affect the accuracyof the gear being machined. Replaces AGMA120.01.ISBN: 1--55589--816--5 Pages: 49

ANSI/AGMA 1106--A97 (R2003) Tooth Proportionsfor Plastic Gears

Presents a new basic rack, AGMA PT, which, with itsfull round fillet, may be preferred in many applicationsof gears made from plastic materials. It contains adescription, with equations and sample calculations,of how the proportions of a spur or helical gearmay bederived from the design tooth thickness and the basicrack data. In several annexes, there are discussionsof possible variations from the basic rack and also aprocedure for defining tooth proportions without usingthe basic rack concept. Metric edition ofANSI/AGMA 1006--A97.ISBN: 1--55589--685--5 Pages: 47

ANSI/AGMA ISO 1328--1 Cylindrical Gears - ISOSystem of Accuracy - Part 1: Definitions andAllowable Values of Deviations Relevant toCorresponding Flanks of Gear Teeth

Contains the ISO system of accuracy relevant tocorresponding flanks of individual cylindrical gears. Itprovides definitions for gear tooth accuracy terms, thestructure of the gear accuracy system and theallowable values of pitch, profile and helix deviations.A normative annex for tangential compositetolerances and an informative annex for allowablevalues of profile form, profile slope, helix form andhelix slope deviations are provided. Identicaladoption of ISO 1328--1:1995.ISBN: 1--55589--733--9 Pages: 28

ANSI/AGMA ISO 1328--2 Cylindrical Gears - ISOSystem of Accuracy - Part 2: Definitions andAllowable Values of Deviations Relevant to RadialComposite Deviations and Runout Information

Contains the ISO system of accuracy relevant toradial (double flank) composite deviations ofindividual cylindrical gears. It provides definitions forgear tooth accuracy terms, the structure of the gearaccuracy system and the allowable values of radialcomposite deviations. An informative annex isincluded that provides equations for determiningallowable values of runout. Identical adoption ofISO 1328--2:1997.ISBN: 1--55589--734--7 Pages: 11



ANSI/AGMA 2001--D04 Fundamental RatingFactors andCalculationMethods for InvoluteSpurand Helical Gear Teeth

Presents a comprehensive method for rating thepitting resistance and bending strength of spur andhelical involute gear pairs. Contains detaileddiscussions of factors influencing gear survival andcalculation methods. Revisions reflected in thisversion include incorporating the latest AGMAaccuracy standard (ANSI/AGMA --A01) into thedetermination of dynamic factor, and change to therelationship between service factor and stress cyclefactor. Revision of ANSI/AGMA 2001--C95.ISBN: 1--55589--839--4 Pages: 56

ANSI/AGMA 2002--B88 (R1996) Tooth ThicknessSpecification and Measurement

Presents procedures for determining tooth thicknessmeasurements of external and internal cylindricalinvolute gearing. Includes equations and calculationprocedures for commonly used measuring methods.ISBN: 1--55589--503--4 Pages: 47

ANSI/AGMA 2003--B97 (R2003) Rating the PittingResistance and Bending Strength of GeneratedStraight Bevel, Zerol Bevel, and Spiral Bevel GearTeeth

Presents amethod for rating the pitting resistance andbending strength of generated straight bevel, zerolbevel, and spiral bevel gear teeth. Includes a detaileddiscussion of factors influencing gear survival and acalculation method. Revision of ANSI/AGMA2003--A86.ISBN: 1--55589--692--8 Pages: 75

ANSI/AGMA 2004--B89 (R2000)Gear Materials andHeat Treatment Manual

Provides information pertaining to engineeringmaterials and material treatment used in gearmanufacture. Includes definitions, selectionguidelines, heat treatment, quality control, lifeconsiderations and a bibliography. Material selectionincludes ferrous, nonferrous and nonmetallicmaterials. Examines wrought, cast, and fabricatedgear blanks. Includes heat treatment sections onthrough hardened, flame hardened, inductionhardened, carburized, carbonitrided, and nitridedgears. Discusses quenching, distortion and shotpeening. Also discusses quality control as related togear blanks, process control, andmetallurgical testingon the final products.ISBN: 1--55589--524--7 Pages: 78

ANSI/AGMA 2005--D03 Design Manual for BevelGears

Provides the standards for designing straight bevel,zerol bevel, spiral bevel and hypoid gears along withinformation on fabrication, inspection and mounting.Covers preliminary gear design parameters, blankdesign including standard taper, uniform depth,duplex taper and tilted root. Also includes drawingformat, inspection, materials, lubrication, mountingsand assembly. An Annex contains examples for easeof understanding. Revision of ANSI/AGMA2005--C96.ISBN: 1--55589--667--7 Pages: 94

ANSI/AGMA 2007--C00 Surface Temper EtchInspection After Grinding [Same as New ISO14104]

Explains the materials and procedures to determineand evaluate localized overheating on groundsurfaces. Includes a system to describe and classifythe indications produced during this inspection.However, does not provide specific acceptance orrejection criteria. Revision of ANSI/AGMA2007--B92.ISBN: 1--55589--761--4 Pages: 6

ANSI/AGMA 2008--C01 Assembling Bevel GearsPrepared expressly for the assembly man in thefactory and the service man in the field. Eachdefinition, explanation, and instruction is directedtoward the physical appearance of the gears as theyare inspected and assembled by these personnel.Revision of ANSI/AGMA 2008--B90.ISBN: 1--55589--795--9 Pages: 30

ANSI/AGMA 2009--B01 Bevel Gear Classification,Tolerances, and Measuring Methods

Establishes a classification system which may beused to communicate geometrical accuracyspecifications of unassembled bevel gearing. It alsoprovides information on measuring methods andpractices to promote uniform measurementprocedures. Eight accuracy grades are defined,numbered B3 through B10, in order of DECREASINGprecision. Equations for the tolerances are providedinmetric terms. RevisionofANSI/AGMA2009--A98.ISBN: 1--55589--794--0 Pages: 68

ANSI/AGMA 2010--A94 (R2000) MeasuringInstrument Calibration - Part I, InvoluteMeasurement

Applies solely to the qualification of gear tooth profileinspection instruments. Provides procedures for thedesign, calibration and traceability of involute, pin andplane (flank) masters. Also covers conditionevaluation of involutemeasuring instruments, such asprobe location, gain, hysteresis, etc.ISBN: 1--55589--630--8 Pages: 39

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ANSI/AGMA 2011--A98 Cylindrical WormgearingTolerance and Inspection Methods

Establishes a classification system for thegeometrical accuracy specification of wormgearing. Italso provides uniform measurement proceduresincluding discussions on single and double flankcomposite testing and tooth thicknessmeasurements. The standard establishes tenaccuracy grades, W3 through W12, based on therelative effect of geometrical errors on conjugateaction for wormgear sets.ISBN: 1--55589--716--9 Pages: 43

ANSI/AGMA 2015--1--A01 Accuracy ClassificationSystem - TangentialMeasurements forCylindricalGears

This standard, for spur and helical gearing, correlatesgear accuracy grades with gear tooth tolerances andgeometry. It provides information on minimumrequirements for accuracy by elementalmeasurement methods. Annex material providesguidance on measurement filtering influences andinformation on comparison of gear inspectionmethods. Users of this standard should have a copyof the companion information sheet, AGMA915--1--A02. Replaceselemental tolerancesectionof AGMA 2000--A88.ISBN: 1--55589--797--5 Pages: 37

!! NEW !!

ANSI/AGMA 2015--2--A06 Accuracy ClassificationSystem - Radial Measurements for CylindricalGears

This standard establishes a classification systemrelevant to radial (double flank) composite deviationsof individual cylindrical involute gears. It serves as aconcise means of specifying gear accuracy withoutthe needof supplying individual element tolerances. Itsimplifies discussions of gear accuracy between gearmanufacturer and purchaser. It specifies theappropriate definitions of gear tooth accuracy terms,the structure of the gear accuracy system, and thetolerances (allowable values of deviations). Annex Aprovides information on the accuracy ofmaster gears.Annex B provides information on runout tolerancevalues. Replaces double flank compositetolerance section of AGMA 2000--A88.ISBN: 1--55589--874--2 Pages: 13

Supplemental Tables for AGMA 2015/915--1--A02Accuracy Classification System - TangentialMeasurement Tolerance Tables for CylindricalGears

Only provides tolerance tables as a supplement toAGMA 2015--1--A01, Accuracy Classification System-- Tangential Measurements for Cylindrical Gears.ISBN: 1--55589--813--0 Pages: 101

ANSI/AGMA 2101--D04 Fundamental RatingFactors andCalculationMethods for InvoluteSpurand Helical Gear Teeth (Metric Edition)

Presents a comprehensive method for rating thepitting resistance and bending strength of spur andhelical involute gear pairs. Contains detaileddiscussions of factors influencing gear survival andcalculation methods. Revisions reflected in thisversion include incorporating the latest AGMAaccuracy standard (ANSI/AGMA 2015--1--A01) intothe determination of dynamic factor, and change tothe relationship between service factor and stresscycle factor. Revision of ANSI/AGMA 2101--C95.ISBN: 1--55589--840--8 Pages: 56

ANSI/AGMA 2110--A94 (R2000) MeasuringInstrument Calibration - - Part I, InvoluteMeasurement (Metric)

Applies solely to the qualification of gear tooth profileinspection instruments. Provides procedures for thedesign, calibration, and traceability of involute, pin,and plane (flank) masters. Also covers conditionevaluation of involute measuring instruments such asprobe location, gain, hysteresis, etc. Metric editionof ANSI/AGMA 2010--A94.ISBN: 1--55589--631--6 Pages: 39

ANSI/AGMA 2111--A98 Cylindrical WormgearingTolerance and Inspection Methods

Establishes a classification system for thegeometrical accuracy specification of wormgearing. Italso provides uniform measurement proceduresincluding discussions on single and double flankcomposite testing and tooth thicknessmeasurements. The standard establishes tenaccuracy grades, W3 through W12, based on therelative effect of geometrical errors on conjugateaction for wormgear sets. Metric edition ofANSI/AGMA 2011--A98.ISBN: 1--55589--717--7 Pages: 43

ANSI/AGMA 2113--A97 Measuring InstrumentCalibration, Gear Tooth Alignment Measurement

Provides procedures for the design, calibration andtraceability of involute, pin and plane (flank) masters.It covers the condition evaluation of involutemeasuring instruments such as probe location, gain,hysteresis, etc. Recommendations are included forestablishment of a proper environment and forstatistical data evaluation procedures. This standardis applicable solely to the qualification of gear toothprofile inspection instruments.ISBN: 1--55589--687--1 Pages: 33



ANSI/AGMA 2114--A98 Measuring InstrumentCalibration,Gear Pitch andRunoutMeasurements

Provides qualification procedures for gear measuringinstruments that are used for evaluation of pitch andrunoutmeasurements. This includes instruments thatmeasure runout directly, or compute it from indexmeasurements. It also covers condition evaluation ofthe measuring instrument. Recommendations areincluded for establishment of a proper environmentand for statistical data evaluation procedures.ISBN: 1--55589--732--0 Pages: 33

!! NEW !!

ANSI/AGMA2116--A05,Evaluation ofDoubleFlankTesters for Radial Composite Measurement ofGears

This standard provides the evaluation criteria fordouble flank testers. Recommended artifact sizesand geometry are provided along with measurementsystem conditions. Annexes contain methods forestimating calibration uncertainty and specifyingartifact.ISBN: 1--55589--871--8 Pages: 9

ANSI/AGMA 6000--B96 (R2002) Specification forMeasurement of Linear Vibration on Gear Units

Presents amethod for measuring linear vibration on agear unit. Recommends instrumentation, measuringmethods, test procedures and discrete frequencyvibration limits for acceptance testing. Annexes listsystem effects on gear unit vibration and systemresponsibility. The ISO vibration rating curves fromISO 8579--2, Acceptance code for gears -- Part 2:Determination of mechanical vibrations of gear unitsduring acceptance testing are introduced.ISBN: 1--55589--666--9 Pages: 21

ANSI/AGMA 6001--D97 (R2003) Design andSelection of Components for Enclosed GearDrives

Outlines the basic practices for the design andselection of components (other than gearing) whichare used in commercial and industrial enclosed geardrives. Discusses bearings, bolting, keys and themost recent theories on shafting among othercomponents. Revision of ANSI/AGMA 6001--C88.ISBN: 1--55589--683--9 Pages: 41

ANSI/AGMA 6002--B93 (R2001) Design Guide forVehicle Spur and Helical Gears

A guide to the design, fabrication, and inspection ofspur and helical gears for vehicles and for powertransmission on vehicles.ISBN: 1--55589--616--2 Pages: 38

ANSI/AGMA/AWEA 6006--A03, Standard forDesign and Specification of Gearboxes for WindTurbines

This standard is intended to apply to wind turbinegearboxes. It provides information for specifying,selecting, designing, manufacturing, procuringoperating and manufacturing reliable speedincreasing gearboxes for wind turbine generatorsystem service.Annex information is supplied on: wind turbinearchitecture, wind turbine load description, qualityassurance, operation and maintenance, minimumpurchaser gearbox manufacturing ordering data,lubrication selection and monitoring, determination ofan application factor from a load spectrum usingequivalent torque, and bearing stress calculations.Replaces AGMA 921--A97.ISBN: 1--55589--817--3 Pages: 94

ANSI/AGMA 6008--A98 Specifications for PowderMetallurgy Gears

Defines the minimum detailed information to beincluded in the powder metallurgy gear specificationssubmitted by the gear purchaser to the gear producer.Specifications on gear tooth geometry are describedin detail for external spur and helical gears and forstraight bevel gears. In addition, there arediscussions on specifications for gear drawings andgear material data. The standard applies to gearsmade by the conventional P/M process consisting ofcompaction followed by sintering and, in some cases,by post sintering treatments.ISBN: 1--55589--713--4 Pages: 17

ANSI/AGMA 6011--I03 Specification for HighSpeed Helical Gear Units

This standard includes information on design,lubrication, bearings, testing and rating for single anddouble helical external tooth, parallel shaft speedreducers and increasers. Units covered include thoseoperating with at least one stage having a pitch linevelocity equal to or greater than 35meters per secondor rotational speeds greater than 4500 rpm and otherstages having pitch line velocities equal to or greaterthan 8 meters per second. Annex material includesdiscussions on service factors, rotor dynamics,efficiency and newly configured purchaser’s datasheets. Revision of ANSI/AGMA 6011--H98.ISBN: 1--55589--819--X Pages: 51



!! NEW !!

ANSI/AGMA 6013--A06 Standard for IndustrialEnclosed Gear Drives

This standard includes design, rating, lubrication,testing and selection information for enclosed geardrives, including foot mounted, shaft mounted, screwconveyor drives and gearmotors. These drivesinclude spur, helical, herringbone, double helical, orbevel gearing in single or multistage arrangements,and wormgearing in multistage drives, as eitherparallel, concentric or right angle configurations. Thisstandard combines and replaces the informationpreviously found in ANSI/AGMA 6009--A00 andANSI/AGMA 6010--F97.ISBN: 1--55589--822--X Pages: 60

ANSI/AGMA 6022--C93 (R2000) Design Manual forCylindrical Wormgearing

Covers the design of general industrial coarse--pitchcylindrical worms and throated gears mounted withaxes at a 90 degree angle and having axial pitches of3/16 inch and larger.ISBN: 1--55589--041--5 Pages: 10

ANSI/AGMA 6023--A88 (R2000) Design Manual forEnclosed Epicyclic Gear Drives

Covers designs for drives employing epicyclic geararrangements. Includes descriptions of epicyclicdrives, nomenclature, application information, anddesign guidelines with reference to other AGMAStandards. See ANSI/AGMA 6123--A88.ISBN: 1--55589--504--2 Pages: 50

ANSI/AGMA 6025--D98 Sound for EnclosedHelical, Herringbone and Spiral Bevel Gear Drives

Describes a recommended method of acceptancetesting and reporting of the sound pressure levelsgenerated by a gear speed reducer or increaser whentested at the manufacturer’s facility. The resultsobtained through the use of this standard shouldrepresent only the sound of the gear unit, as othersystem influences, such as prime mover or drivenequipment are minimized. Annexes to the standardpresent sound power measurement methods for usewhen required by specific contract provisionsbetween the manufacturer and purchaser. Revisionof ANSI/AGMA 6025--C90.ISBN: 1--55589--718--5 Pages: 21

ANSI/AGMA 6032--A94 (R2000) Standard forMarine Gear Units: Rating

Considers rating practices for marine mainpropulsion, power take--off and auxiliary propulsionservice. Allowable contact stress numbers andallowable bending stress numbers for materials areincluded. Also addresses bearings, clutches,lubricating oil systems, shafts and certain aspects ofvibration.ISBN: 1--55589--633--2 Pages: 57

ANSI/AGMA 6033--B98 Materials for MarinePropulsion Gearing

Identifies commonly used alloy steels, heattreatments and material inspection requirements formain propulsion marine service through hardened,case hardened and surface hardened gearing for over1500 horsepower. Forged and hot rolled alloy steelbar stock are specified to three metallurgical qualitygrades (I, II and III) according to cleanliness and testrequirements. Cast steel gearing is specified to asingle metallurgical quality level. Mechanical,metallurgical and nondestructive test requirementsare provided for various heat treat processes andmetallurgical quality grades of gearing. Revision ofANSI/AGMA 6033--A88.ISBN: 1--55589--711--8 Pages: 48

ANSI/AGMA 6034--B92 (R1999) Practice forEnclosed Cylindrical Wormgear Speed Reducersand Gearmotors

Covers the design and rating of cylindrical-- wormgearspeed reducers, having either solid or hollow outputshafts of the following specific types: single reduction;double reduction incorporating cylindricalwormgearing for each reduction; and doublereduction incorporating cylindrical wormgearing asfinal and helical gearing as initial reduction.ISBN: 1--55589--494--1 Pages: 37

ANSI/AGMA 6035--A02 Design, Rating andApplication of Industrial Globoidal Wormgearing

This standard provides guidelines for the design,rating and application of globoidal wormgearingmounted at a 90 degree angle. Specific definitions forgloboidal wormgearing terms are presented, alongwith formulas for determining the geometric sizes ofthe major features for the worm and gear. Designconsiderations, design procedures, gear blanks andself--locking conditions are also discussed.Procedures for rating the load capacity of globoidalwormgearing are included. Replaces ANSI/AGMA6017--E86 and ANSI/AGMA 6030--C87.ISBN: 1--55589--792--4 Pages: 45



!! NEW !!

ANSI/AGMA 6113--A06, Standard for IndustrialEnclosed Gear Drives (Metric Edition)

This standard includes design, rating, lubrication,testing and selection information for enclosed geardrives, including foot mounted, shaft mounted, screwconveyor drives and gearmotors. These drivesinclude spur, helical, herringbone, double helical orbevel gearing in single or multistage arrangements,and wormgearing in multistage drives, as eitherparallel, concentric or right angle configurations. Thisstandard combines and replaces the informationpreviously found in ANSI/AGMA 6109--A00 andANSI/AGMA 6110--F97. Metric version ofANSI/AGMA 6013--A06.ISBN: 1--55589--823--8 Pages: 60

ANSI/AGMA 6123--A88 (R2000) Design Manual forEnclosed Epicyclic Metric Module Gear Drives

Provides guidelines for designing drives employingepicyclic gear arrangements. Includes descriptions ofepicyclic drives, nomenclature, applicationinformation and design guidelines, with reference toother AGMAStandards. SeeANSI/AGMA6023--A88.ISBN: 1--55589--505--0 Pages: 50

ANSI/AGMA 6133--B98 Materials for MarinePropulsion Gearing

Identifies commonly used alloy steels, heattreatments and material inspection requirements formain propulsion marine service through hardened,case hardened and surface hardened gearing for over1500 horsepower. Forged and hot rolled alloy steelbar stock are specified to three metallurgical qualitygrades (I, II and III) according to cleanliness and testrequirements. Cast steel gearing is specified to asingle metallurgical quality level. Mechanical,metallurgical and nondestructive test requirementsare provided for various heat treat processes andmetallurgical quality grades of gearing. Metricedition of ANSI/AGMA 6033--B98.ISBN: 1--55589--712--6 Pages: 48

ANSI/AGMA 6135--A02 Design, Rating andApplication of Industrial Globoidal Wormgearing(Metric Version)

This standard provides guidelines for the design,rating and application of globoidal wormgearingmounted at a 90 degree angle. Specific definitions forgloboidal wormgearing terms are presented, alongwith formulas for determining the geometric sizes ofthe major features for the worm and gear. Designconsiderations, design procedures, gear blanks andself--locking conditions are also discussed.Procedures for rating the load capacity of globoidalwormgearing are included. Replaces ANSI/AGMA

6017--E86 and ANSI/AGMA 6030--C87. Metricedition of ANSI/AGMA 6035--E02.ISBN: 1--55589--793--2 Pages: 45

ANSI/AGMA 9000--C90 (R2001) Flexible Couplings- Potential Unbalance Classification

Offers standard criteria for the unbalanceclassification of flexible couplings. Considers theeffects of hardware and eccentricity to give a moreaccurate value. Presents revised examples in theappendices that illustrate the calculation methods.Replaces AGMA 515.02.ISBN: 1--55589--549--2 Pages: 41

ANSI/AGMA 9001--B97 (R2003) Flexible Couplings- Lubrication

Examines proper lubrication and why it is an essentialelement for satisfactory performance and long life.Looks at the requisites for proper lubrication,including: selection of proper lubricant, awell--designed lubrication system, and an adequatemaintenance program, are discussed in this standard.Revision of ANSI/AGMA 9001--A86.ISBN: 1--55589--686--3 Pages: 6

ANSI/AGMA 9002--B04 Bores and Keyways forFlexible Couplings (Inch Series)

This standard describes sizes and tolerances forstraight and tapered bores and the associated keysand keyways, as furnished in flexible couplings. Thedata in the standard considers commercially standardcoupling bores and keyways, not special couplingbores and keyways that may require specialtolerances. Annexes provide material on inspectionmethods and design practices for tapered shafts.Revision of ANSI/AGMA 9002--A86.ISBN: 1--55589--841--6 Pages: 22

ANSI/AGMA 9003--A91 (R1999) Flexible Couplings- Keyless Fits

Presents information on design, dimensions,tolerances, inspection, mounting, removal andequipment that is in commonusewith keyless taperedand keyless straight (cylindrical) bore hubs for flexiblecouplings.ISBN: 1--55589--572--7 Pages: 21

ANSI/AGMA 9004--A99 Flexible Couplings - MassElastic Properties and Other Characteristics

Provides information and calculation methods tosystem designers for the selection of systemcomponents and natural frequency calculations.Mass elastic properties discussed include couplingweight, WR2, center of gravity, axial stiffness, axialnatural frequency, lateral stiffness, lateral naturalfrequency and torsional stiffness.ISBN: 1--55589--715--0 Pages: 39



ANSI/AGMA 9005--E02 Industrial Gear LubricationThis standard provides the end user, originalequipment builder, gear manufacturer and lubricantsupplier with guidelines for minimum performancecharacteristics for lubricants suitable for use withenclosed and open gearing which is installed ingeneral industrial power transmission applications. Itprovides recommendations for selecting lubricantsbased on current theory and practice in the industry,and attempts to align with current ISO standards. It isnot intended to supplant specific instructions from thegear manufacturer. Replaces ANSI/AGMA9005--D94.ISBN: 1--55589--800--9 Pages: 31

ANSI/AGMA 9008--B00 Flexible Couplings – GearType – Flange Dimensions, Inch Series

Defines the North American industry practice for theinterface dimensions of the sleeve and rigid hubs ofboth shrouded and exposed bole, inch series, geartype couplings.ISBN: 1--55589--736--3 Pages: 3

ANSI/AGMA 9009--D02 Flexible Couplings -Nomenclature for Flexible Couplings

Presents the nomenclature common to flexiblecouplings as used in mechanical power transmissiondrives. It was prepared to reduce the languagebarriers that arise between designers, manufacturersand userswhen attempting to designate various typesof flexible couplings and their elements. It does notaddress nomenclature for flexible shafts, quill shafts,universal joints or devices which exhibit slip such asclutches, fluid couplings, magnetic couplings ortorque converters.ISBN: 1--55589--796--7 Pages: 17

ANSI/AGMA 9112--A04 Bores and Keyways forFlexible Couplings (Metric Series)

This standard describes sizes and tolerances forstraight and tapered bores and the associated keysand keyways, as furnished in flexible couplings. Thedata in the standard considers commercially standardcoupling bores and keyways, not special couplingbores and keyways that may require specialtolerances. Annexes provide material on inspection

methods and design practices for tapered shafts.Metric edition of ANSI/AGMA 9002--B04.ISBN: 1--55589--842--4 Pages: 35

AGMA ISO 10064--1 Cylindrical Gears - Code ofInspection Practice - Part 1: Inspection ofCorresponding Flanks of Gear Teeth

Provides a code of practice dealing with the tangentialmeasurements of cylindrical involute gear tooth flanks(pitch deviations, profile deviations, helix deviationsand tangential composite deviations), and serves as asupplement to ANSI/AGMA ISO 1328--1, CylindricalGears -- ISO System of Accuracy -- Part 1: Definitionsand Allowable Values of Deviations Relevant toCorresponding Flanks of Gear Teeth. Identicaladoption of ISO/TR 10064--1.ISBN: 1--55589--735--5 Pages: 26

AGMA ISO 10064--2 Cylindrical Gears - Code ofInspection Practice - Part 2: Inspection Related toRadial Composite Deviations, Runout, ToothThickness and Backlash

Provides a code of practice dealing with inspectionrelevant to radial composite deviations, runout, tooththickness and backlash of cylindrical involute gear(measurements referred to double flank contact), andserves as a supplement to ANSI/AGMA ISO 1328--2,Cylindrical Gears -- ISO System of Accuracy -- Part 2:Definitions and Allowable Values of DeviationsRelevant to Radial Composite Deviations and RunoutInformation. Identical adoption of ISO/TR10064--2.ISBN: 1--55589--737--1 Pages: 25

AGMA ISO 14179--1, Gear Reducers - ThermalCapacity Based on ISO/TR 14179-1

This information sheet utilizes an analytical heatbalance model to provide a means of calculating thethermal transmittable power for a single-- ormulti--stage gear drive lubricatedwithmineral oil. Thecalculation is based on standard conditions of 25Cmaximumambient temperature and 95Cmaximumoilsump temperature in a large indoor space, butprovides modifiers for other conditions. Differencesfrom ISO/TR 14179--1 are: a) errors were identifiedand corrected, b) text was added to clarify thecalculation methods, and c) an illustrative examplewas added to assist the reader. Modified adoptionof ISO/TR 14179--1.ISBN: 1--55589--821--1 Pages: 26


ISO Standards by Technical Committee 60

Technical Committee 60 is responsible for the development of all international gear--related standards.

Many standards require additional documents for their proper use. A list of these standards are normally supplied after thescope, in the normative references section of a document. Be sure to inquire whether the standard you need requiresother documents listed herein.

53:1998 Cylindrical gears for general and heavyengineering – Standard basic rack tooth profile

54:1996Cylindrical gears for general engineering and forheavy engineering -- Modules

677:1976 Straight bevel gears for general engineeringand heavy engineering -- Basic rack

678:1976 (1996) Straight bevel gears for generalengineering and heavy engineering -- Modules anddiametral pitches

701:1998 International gear notation -- Symbols forgeometric data

1122--1:1998Glossary of gear terms -- Part 1: Definitionsrelated to geometry

1122--2:1999 Vocabulary of gear terms -- Part 2:Definitions related to worm gear geometry

1328--1:1995Cylindrical gears -- ISO system of accuracy-- Part 1: Definitions and allowable values of deviationsrelevant to corresponding flanks of gear teeth (SeeANSI/AGMA ISO 1328--1)

1328--2:1997Cylindrical gears -- ISO system of accuracy-- Part 2: Definitions and allowable values of deviationsrelevant to radial composite deviations and runoutinformation (See ANSI/AGMA ISO 1328--2)

1340:1976 Cylindrical gears -- Information to be given tothe manufacturer by the purchaser in order to obtain thegears required

1341:1976 Straight bevel gears -- Information to be givento themanufacturer by the purchaser in order to obtain thegears required

2490:1996Single--start solid (monoblock) gear hobs withtenon drive or axial keyway, 1 to 40 module -- Nominaldimensions

4468:1982 Gear hobs -- Single start -- Accuracyrequirements

6336--1:1996 Calculation of load capacity of spur andhelical gears -- Part 1: Basic principles, introduction andgeneral influence factors

6336--2:1996 Calculation of load capacity of spur andhelical gears -- Part 2: Calculation of surface durability(pitting)

6336--3:1996 Calculation of load capacity of spur andhelical gears -- Part 3: Calculation of tooth bendingstrength

6336--5:2003 Calculation of load capacity of spur andhelical gears -- Part 5: Strength and quality of materials

8579--1:2002 Acceptance code for gears -- Part 1:Determination of airborne sound power levels emitted bygear units

8579--2:1993 Acceptance code for gears -- Part 2:Determination ofmechanical vibration of gear units duringacceptance testing

9083:2001 Calculation of load capacity of spur andhelical gears -- Application to marine gears

9085:2002 Calculation of load capacity of spur andhelical gears -- Application for industrial gears

TR10064--1:1992 Cylindrical gears -- Code of inspectionpractice -- Part 1: Inspection of corresponding flanks ofgear teeth (See AGMA ISO 10064--1)

TR10064--2:1996 Cylindrical gears -- Code of inspectionpractice -- Part 2: Inspection related to radial compositedeviations, runout, tooth thickness and backlash (SeeAGMA ISO 10064--2)

TR10064--3:1996 Cylindrical gears -- Code of inspectionpractice -- Part 3: Recommendations relative to gearblanks, shaft centre distance and parallelism of axes

TR10064--4:1998 Cylindrical gears -- Code of inspectionpractice -- Part 4: Recommendations relative to surfacetexture and tooth contact pattern checking

10300--1:2001 Calculation of load capacity of bevelgears -- Part 1: Introduction and general influence factors

10300--2:2001 Calculation of load capacity of bevelgears -- Part 2: Calculation of surface durability (pitting)

10300--3:2001 Calculation of load capacity of bevelgears -- Part 3: Calculation of tooth root strength

TR10495:1997 Cylindrical gears-- Calculation of servicelife under variable loads -- Conditions for cylindrical gearsaccording to ISO 6336

10825:1995 Gears -- Wear and damage to gear teeth --Terminology

TR10828:1997Wormgears -- Geometry of worm profiles

TR 13593:1999 Enclosed gear drives for industrialapplications

13691:2001 Petroleum and natural gas industries -- Highspeed special--purpose gear units

TR 13989--1:2000Calculation of scuffing load capacity ofcylindrical, bevel and hypoid gears – Part 1: Flashtemperature method

TR 13989--2:2000Calculation of scuffing load capacity ofcylindrical, bevel and hypoid gears – Part 2: Integraltemperature method


14104:1995 Gears -- Surface temper etch inspectionafter grinding

TR 14179--1:2001 Gears -- Thermal capacity -- Part 1:Rating gear drives with thermal equilibrium at 95°C sumptemperature

TR 14179--2:2001 Gears -- Thermal capacity -- Part 2:Thermal load--carrying capacity

14635--1:2000 Gears – FZG test procedures – Part 1:FZG method A/8, 3/90 for relative scuffing load carryingcapacity of oils

14635--3:2005 Gears -- FZG test procedures -- Part 3:FZG test method A/2,8/50 for relative scuffingload--carrying capacity and wear characteristics ofsemifluid gear greases

ISO 17485:2006 Bevel gears -- ISO system of accuracy

Gear Software

AGMA’s Gear Rating Suite

Beginning with AGMA’s ISO6336 Software , which wasdeveloped and tested over several years by a group ofAGMA men and women working closely with thedevelopers of the international standard, the softwareaddresses ISO 6336method B, themost comprehensive,analytical calculation method. It has gained internationalacceptance since its release in 1998 and enables you to:

D determine gear capacity in accordance with the ISO6336 standard quickly and accurately;

D compare your own design and practices with ISO6336 results;

D understand your competitor’s ratings.

The manual alone is worth the price! In addition toexplaining the software, this handy document is a greattool for learning how to use ISO6336, guiding you throughthe complexities and teaching you the correct inputs,especially in the exacting areas of tooth geometry andtooling.

Two of the most recognized standards in the world todayfor determining the rating of spur and helical gears areANSI/AGMA 2001--C95 and ISO 6336. Now for the firsttime, software to calculate ratings in accordance witheach standard is available in one package from AGMA.Entitled the Gear Rating Suite, the software allows theuser to input data once for each gearset, and obtainratings to both standards. Among the many features ofthe software package are:

D An in--depth User’s Manual, and all required AGMAand ISO standards.

D User friendly I/O that provides an intuitive userinterface, with drop--down boxes, look--up tables,and graphical guides used to assist in data entry.

D Dual input units which allow the user to switchbetween SI and inch units.

D Error and warning messages are provided withinboth the input and rating routines to help identifyproblems.

D A help program is incorporated within the software.

D Long and short form outputs are provided.

In addition to the gear rating routines and aids, thepackage also provides:

D A Geometry Checker for checking input data toensure they are within allowable ranges. TheGeometry Checker will help identify data entry errorsand unusual gear designs.

D Tolerance worksheets which allow the user tocalculate tooth tolerances from quality numbers,convert quality numbers between AGMA and ISO,and to display tolerances for adjacent grades.

The potential of the Gear Rating Suite to improve yourefficiency and save you time in performing these rigorouscalculations makes this a “must have” tool for all gearengineers.



Fall Technical Meeting Papers: 1990 -- 2005

2005 PAPERS

05FTM01. Fine Pitch, Plastic Face Gears: Design andManufactureAuthors: I. Laskin and E. Reiter

Face gear technology has attracted attention.Products benefiting include those which usemolded plastic gears. More applications couldbenefit, justifying the need for more information onthe special features of face gears, their design andmanufacture, in comparison to othernon--parallel--shaft gears. A description ofmanufacturing methods, particularly in plasticmolding is given with inter--related design and gearperformance issues. New methods of graphicmodeling are included with descriptions of facegear configurations and applications.ISBN: 1--55589--849--1 Pages: 11

05FTM02. The Effects of Pre Rough MachineProcessing on Dimensional Distortion DuringCarburizingAuthor: G. Blake

A study to isolate the influence of pre--roughmachine processing on final dimensional distortion.Methods are discussed to aid process developmentand minimize dimensional change duringcarburizing. The study examined the distortionduring carburizing between five possible rawmaterial starting conditions. Coupons were usedandmanufactured from each population of materialprocessing. Dimensions were made before andafter carburizing using a scanning coordinatemeasurement machine. The results show thatdimensional distortion during carburizing increaseswith mechanical and thermal processing.ISBN: 1--55589--850--5 Pages: 18

05FTM03. Modelling Gear DistortionAuthor: P.C. Clarke

Dealing with carburize case hardened geardistortion and growth is a challenge for the globalgear industry. Attempts started in 1978 withcomputer programs to calculate distortion andgrowth, plus residual stress distributions for a gearand evolved by gathering distortion data for a widerange of sizes, shapes, grinding allowances withtrends for different geometries. A spread sheetprogramwith gear dimensional input, calculates thedistortions and growths, and then calculates themodified dimensions for required protuberance andtheminimum carburized case depth. Case historiesillustrate the consequences of various geometriesand future developments are discussed.ISBN: 1--55589--851--3 Pages: 12

05FTM04. Tooth Meshing Stiffness OptimisationBased on Gear Tooth Form Determination for aProduction Process Using Different ToolsAuthors: U. Kissling, M. Raabe, M. Fish

The variation of the tooth meshing stiffness is asource of noise and the exact calculation of toothform is important for the stiffness determination. Forthis purpose, software was written with the conceptof an unlimited number of tools such as hobs,grinding disk, and honing defining a manufacturingsequence. Stiffness variation can be improved byoptimization of final gear geometry with acalculation of the contact path under load. Themeshing stiffness is derived making it possible tostudy the effect of a proposed profile correction of agear under different loads. Calculations withAGMA2001 or ISO6336 check the point with thehighest root stress. Effect of a grinding notch is alsoincluded.ISBN: 1--55589--852--1 Pages: 11

05FTM05. Computerized Design of Face HobbedHypoid Gears: Tooth Surface Generation, ContactAnalysis and Stress CalculationAuthors: M. Vimercati and A. Piazza

Facemilled hypoid gears have beenwidely studied.Aim of this paper is just to propose an accurate toolfor computerized design of face hobbed hypoidgears. A mathematical model able to computedetailed gear tooth surface is presented. Then, theobtained surfaces will be employed as input for anadvanced contact solver that, using a hybridmethod combining finite element technique withsemianalytical solutions, is able to efficiently carryout contact analysis under light and heavy loadsand stress calculation of these gears.ISBN: 1--55589--853--X Pages: 13

05FTM06. A Model to Predict Friction Losses ofHypoid GearsAuthors: H. Xu, A. Kahraman and D.R. Houser

A model to predict friction--related mechanicalefficiency losses of hypoid gear pairs is proposed,which combines a commercial available finiteelement based gear contact analysis model and afriction coefficient model with a mechanicalefficiency formulation. The contact analysis modelis used to provide contact pressures and othercontact parameters required by the frictioncoefficientmodel. The instantaneous frictioncoefficient is computed by using a validated formulathat is developed based on a thermalelastohydrodynamic lubrication (EHL) model.Computed friction coefficient distributions are thenused to calculate the friction forces and theresultant instantaneous mechanical efficiencylosses of the hypoid gear pair at a given meshangle. Themodel is applied to study the influence of



speed, load, surface roughness, and lubricanttemperature as well as assembly errors on themechanical efficiency of an example face--hobbedhypoid gear pair.ISBN: 1--55589--854--8 Pages: 15

05FTM07. Spiral Bevel and Hypoid Gear CuttingTechnology UpdateAuthor: T.J. Maiuri

Spiral bevel and hypoid gear cutting technology haschanged significantly over the years. Themachines, tools, materials, coatings and processeshave steadily advanced to the current state of theart. This paper will cover the progression frommechanical machines with complex drive trainsusing the five cut method of cutting gears withcoolant, to machines with direct drive CNCtechnology dry cutting gears by the completingmethod with carbide and high speed steel tools.The latest cutting tool materials and tool coatingswill be discussed. Production examples from theautomotive and truck industries will be provided, aswell as examples from the gear jobbing industry.ISBN: 1--55589--855--6 Pages: 20

05FTM08. New Developments in Tooth ContactAnalysis (TCA) and Loaded TCA for Spiral Bevel andHypoid Gear DrivesAuthors: Q. Fan and L. Wilcox

Tooth Contact Analysis (TCA) and Loaded ToothContact Analysis (LTCA) are two powerful tools forthe design and analysis of spiral bevel and hypoidgear drives. TCA and LTCA respectively simulategear meshing contact characteristics under lightload and under significant load. Application of CNChypoid gear generators has brought new conceptsin design of spiral bevel and hypoid gears withsophisticated modifications. This paper presentsnew developments in TCA and LTCA of spiral beveland hypoid gears. The first part of the paperdescribes a new universal tooth surface generationmodel with consideration of capabilities of CNCbevel gear generators. The universal model isbased on the kinematical modeling of the basicmachine settings andmotions of a virtual bevel geargenerator which simulates the hypoid geargenerator and integrates both face milling and facehobbing processes. Mathematical descriptions ofgear tooth surfaces are represented by a series ofcoordinate transformations in terms of surface pointposition vector, unit normal, and unit tangent.Accordingly, a generalized TCA algorithm andprogram are developed. In the second part of thispaper the development of a finite element analysis(FEA) based LTCA is presented. The LTCA contactmodel is formulated using TCA generated toothsurface and fillet geometries. The FEA modelsaccommodate multiple pairs of meshing teeth toconsider a realistic load distribution among theadjacent teeth. An improved flexibility matrix

algorithm is formulated by introducing specializedgap elements with considerations of deflection anddeformation due to tooth bending, shearing, localHertzian contact, and axle stiffness. Two numericalexamples, a face--hobbing design anda facemillingdesign, are illustrated to verify the developedmathematical models and programs.ISBN: 1--55589--856--4 Pages: 12

05FTM09.Hypoid Gear LappingWear Coefficient andSimulationAuthors: C. Gosselin, Q. Jiang, K. Jenski andJ. Masseth

Hypoid gears are usually hard finished after heattreatment using lapping. Because of the rolling andsliding motion inherent to hypoid gears, the lappingcompound abrades and refines the tooth surface toachieve smoothness in rolling action and producehigh quality gear sets. The pinions and gears arelapped in pairs and must therefore remain ascoordinated pairs for the rest of their lives.However,heat treatment distortion can vary significantly.Thus, developing a lapping sequence formanufacturing requires both time and experiencedtechnicians who can establish lapping operatingpositions and sequence times to produce qualitygear sets both in terms of performance and cost.This development is generally trial and error. In thispaper, the lapping process is simulated usingadvanced modelling tools such as gear vectorialsimulation for the tooth surfaces and path of contactand reverse engineering to analyze the toothcontact pattern of existing gear sets under load(static LTCA). Test gear sets are measured using aCMM prior to a special lapping cycle where theposition of the gear sets on the lapper does notchange, and then re--measured after lapping inorder to establish how much, and where, materialwas removed. A wear constant named ”wearcoefficient” specific to the lapping compoundcomposition is then calculated. Based on theobtained wear coefficient value, an algorithm forsimulating the lapping process is presented. Gearsets lapped on the production line are used forsimulation case studies. Results show that it ispossible to predict how much and where materialwill be removed, thereby opening the door to betterunderstanding of the lapping process.ISBN: 1--55589--857--2 Pages: 16

05FTM10. Finite Element Study of the Ikona GearTooth ProfileAuthors: J.R. Colbourne and S. Liu

The Ikona gear tooth profile is a patentednon--involute tooth profile for internal gear pairs.Gearswith this profile have the following properties:the teeth are conjugate; the contact ratio is veryhigh; there is no tip interference, even when only aone--tooth difference between the pinion andinternal gear; there is minimal backlash; and the



gears can be cut on conventional gear--cuttingmachines. Large reduction ratios can be achievedby a single gear pair and a high contact ratio resultsin lower tooth stresses than for a similar involutegear. Plus, minimal backlash makes the Ikonaprofile ideal for many applications, such asservo--drives, medical prostheses, and robots.Stress analysis of these gears assumes that thecontact force is equal at each contacting tooth pair.Finite element results demonstrate how the numberof tooth pairs in contact may increase under load.Finally, an estimate will be presented, showing thevariation of tooth force between the contactingteeth.ISBN: 1--55589--858--0 Pages: 9

05FTM11. Low Loss GearsAuthors: B.--R. Höhn, K. Michaelis and A. Wimmer

In most transmission systems one power losssources is the loaded gear mesh. High losses leadto high energy consumption, high temperatures,early oil ageing, increased failure risk and highcooling requirements. In many cases highefficiency is not the main focus and design criteriaas load capacity or vibration excitation predominatethe gear shape design. Those design criteria cancounteract high efficiency. The influences of geargeometry parameters on gear efficiency, loadcapacity, and excitation are shown. Designpreference guidelines can be followed to a varyingextent which leads to more or less unconventional,but more efficient gear design. Low loss gears cansave substantial energy in comparison toconventional gears. The power loss reduction isdependent on the operating conditions and can addup to 70% of the power loss of conventional gears.Such low loss gears have significant advantages interms of energy consumption, heat development,and cooling requirements.ISBN: 1--55589--859--9 Pages: 11

05FTM12.Modal Failure Analysis of a Gear and DriveRing AssemblyAuthor: D.D. Behlke

After years of successful reliable applications, acomponent failure on a new application cannot beexplained with static stress analyses,modal failureanalyses may be required. Finite element modalanalyses was used to identify the mode and itsfrequency that cause a high range gear and drivering assembly to fail prematurely. A CampbellDiagram was used to identify modes in theoperating range of a six--speed transmission thatcould cause the drive ring to fail. Redesigning theassembly to move the critical modes out of theoperating range is described.ISBN: 1--55589--860--2 Pages: 8

05FTM13. Evaluation of the Scuffing Resistance ofIsotropic Superfinished Precision GearsAuthors: P.W. Niskanen, B. Hansen andL. Winkelmann

Aerospace gears are often engineered to operatenear the upper bounds of their theoretical designallowables. Due to this, scuffing is a primary failuremode for aerospace gears. Isotropic superfinishingimprovedRolling/Sliding Contact Fatigue up to ninetimes that of baseline test specimens. Testsdemonstrated the ability to successfully carry 30percent higher loads for at least three times the lifeof the baseline samples. A study was conducted onactual gears having an isotropic superfinish. Thisstudy showed superfinishing technology increaseda gear’s resistance to contact fatigue by a factor ofthree, and increased bending fatigue resistance byat least 10 percent. The paper discusses anadditional studywhich is underway to determine thescuffing resistance of isotropic superfinishedaerospace gears to that of baseline ground gears.These tests were conducted using a method thatprogressively increases lubricant temperature untilscuffing occurs, rather than the traditional loadincreasing method used in FZG testing rigs. Theresults of the current testing reveals that isotropicsuperfinished SAE 9310 specimens show at least a40 F higher lubricant temperature at the point ofscuffing compared to as--ground baseline gears.ISBN: 1--55589--861--0 Pages: 10

05FTM14. Determining the Shaper Cut Helical GearFillet ProfileAuthor: G. Lian

This paper describes a root fillet form calculatingmethod for a helical gear generated with a shapercutter. The shaper cutter considered has aninvolute main profile and elliptical cutter edge in thetransverse plane. Since the fillet profile cannot bedetermined with closed form equations, a Newton’sapproximation method was used in the calculationprocedure. The paper will also explore thefeasibility of using a shaper tool algorithm forapproximating a hobbed fillet form. Finally, thepaper will also discuss some of the applications offillet form calculation procedures such as formdiameter (start of involute) calculation and finishingstock analysis.ISBN: 1--55589--862--9 Pages: 16

05FTM15. Repair of Helicopter GearsAuthors: S. Rao, D. McPherson and G. Sroka,

In order to reduce costs by extending theoperational life of the sun and input pinion gears of ahelicopter transmission, scraped gears weresubject to a superfinishing process. This processwas found to remove minor foreign object damageby uniformly removing aminimal amount ofmaterialon the gear teeth, while meeting originalmanufacturing specifications for geometry. The



process also resulted in enhanced surface qualityand did not exhibit detrimental metallurgical effectson the surface or sub--surface of the teeth. Theprocess was also found to eliminate gray staining,an early precursor to pitting. This paper describesthe results of the helicopter gear repair project andincludes the geometry and metallurgicalevaluations on the repaired gear. Further effort tocharacterize the durability and strengthcharacteristics of the repaired gear is ongoing.ISBN: 1--55589--863--7 Pages: 9

05FTM16. CH47D Engine Transmission Input PinionSeeded Fault TestAuthors: J.P. Petrella, J.S. Kachelries and S.M. Holder,and T.E. Neupert

This paper summarizes an Engine TransmissionInput Pinion Seeded Fault Test that wasaccomplished as a portion of the validation processfor the Transmission Vibration Diagnostic System(TVDS) Analyzer. The test specimen was a highspeed engine transmission input pinion with aknown defect (i.e., seeded fault) machined into ahigh stress area of a gear tooth root. During thetesting, the TVDS analyzer monitored the testpinion real time to provide a sufficient warning timeof the impending failure. The TVDS data wasevaluated along with a post--test evaluation of thefatigue crack. During the post--test fractographicevaluation, arrest lines and fatigue striations wereanalyzed to develop crack propagation data as afunction of the number of applied load cycles. Thisdata was then correlated to better understand thepotential warning signals the TVDS system couldprovide that would allow the pilot enough time tounload the suspect engine transmission.ISBN: 1--55589--864--5 Pages: 11

05FTM17. Influences of Bearing Life Considerationson Gear Drive DesignAuthor: F.C. Uherek

Historically, catalog gear drives have beendesigned with 5000 hours of L10 bearing life atservice factor 1.0 power. Advances in bearinganalysismethods have brought new considerationsto the design and selection process. The impact ofnew modeling techniques, additionalconsiderations, and various extensions to thetraditional bearing fatigue calculations areexplored. The modeling of these various additionsto a traditional catalog L10 calculation is illustratedby bearing selections for cases of single, double,and triple reduction gear drives. A roadmap ispresented listing critical considerations whenapplying various bearing manufacturerrecommendations.ISBN: 1--55589--865--3 Pages: 13

05FTM18. Planet Pac: Increasing Epicyclic PowerDensity and Performance through IntegrationAuthor: D.R. Lucas

Epicyclical gear systems are typically equippedwith straddle--mounted planetary idlers and aresupported by pins on the input and output sides of acarrier. These carriers can be either one--piece ortwo--piece carrier designs. Traditionallymany of thehigher power rated epicyclic gear systems usecylindrical roller bearings to support the planetarygears. This paper will demonstrate that using apreloaded taper roller bearing in an integratedpackage should be the preferred choice for thisapplication to increase the bearing capacity, powerdensity, and fatigue life performance. Based onDIN281--4 calculations, this patented [1], fullyintegrated solution allows for calculated bearingfatigue lives to be 5 times greater than anon--integrated solution and more than 1.5 timesgreater than a semi--integrated solution, withoutchanging the planet gear envelope.ISBN: 1--55589--866--1 Pages: 7

05FTM19. The Application of Very Large, WeldFabricated, Carburized, Hardened & Hard FinishedAdvanced Technology Gears in Steel Mill Gear DrivesAuthors: R.J. Drago, R. Cunningham and S. Cymbala

In the 1980’s, Advanced Technology Gear (ATG)steel rollingmill gear drives consisting of carburizedpinions in mesh with very large, weld fabricated,high through hardened gears were introduced toimprove capacity. Recently, even theimprovements obtained from these ATG gear setswere not sufficient to meet higher production ratesand rolling loads. For greater load capacity ATGsets have been developed consisting of carburized,hardened pinions in mesh with very large, weldfabricated, carburized and hard finished gears.Single and double helical gears of this type, rangingin size from 80 to 136 inches pitch diameter havebeen implemented in several steel rollingapplications. This paper describes the conditionsthat require the use of these gears and thetechnology required to design, manufacture, and,especially, heat treat, these very special, very largegear sets.ISBN: 1--55589--867--X Pages: 16

05FTM20. Dual Drive Conveyor Speed ReducerFailure AnalysisAuthor: M. Konruff

With increasing requirements, many conveyorsystems utilize dual drive arrangements to increaseoutput. Dual drives can provide an economicalsolution by utilizing smaller, more efficient,systemdesigns. However, multiple drive conveyorsmust proportion the load between drives and loadsharing without some type of control is difficult toachieve. This paper presents a case study on a



failure analysis of a coal mine dual drive conveyorsystem that experienced gear reducer failuresbetween 2 to 18months. Physical and metallurgicalinspection of failed gearing did not indicate materialor workmanship defects, but indicated overload. Inorder to determine the cause of the failures, straingage load testing was performed. The testing of theconveyor drives revealed load sharing problemswhich that will be reviewed.ISBN: 1--55589--868--8 Pages: 9

2004 PAPERS

04FTM1.Gear Noise -- Challenge and Success Basedon Optimized Gear GeometriesAuthors: F. Hoppe and B. Pinnekamp

Airborne and structure borne noise behaviourbecomes more and more an important feature forindustrial applications. Noise excitationrequirementsmay differ with applications. Industrialconveyor belts or cement mills are less sensitivewith respect to noise emission than militaryapplications, such as navy ship propulsion. Thispaper describes requirements and solutions withregard to noise behaviour focussing on examplestaken from wind turbine gear transmissions andnavy applications. The individual approaches haveto be a suitable compromise to meet the challengeof noise requirement and cost optimization withoutrestrictions on gear load carrying capacity.Therefore, the paper shows requirements andmeasurements examples from shop and field testsin comparison to gear micro geometry andcalculation results.ISBN: 1--55589--824--6 Pages: 15

04FTM2. Noise Optimized Modifications:Renaissance of the Generating Grinders?Author: H. Geiser

While load and stress optimized toothmodificationsmay be normal in production, noise and vibrationoptimized tooth modifications need higherproduction accuracies and more complexmodifications than with crowning and root or tiprelief. Topological modifications show advantagesfor low noise and vibration behavior due to thehigher variability in direction of contact pattern.Unfortunately, a load optimized tooth flankmodification is not always a noise optimizedmodification -- a compromise between optimizedload distribution and low noise has to be found. In apractical example the calculation possibilities willbe demonstrated on how an optimized toothmodification can be found. To satisfy the newrequirements the gear grinder manufacturersneeded to improve their machines. Thisimprovement was possible with the substitution forthemechanical transmissions in the grinderwith the

modern CNC controls. By introducing a torquemotor as the main table drive of a grinder, togetherwith the direct mounted encoder, an advantage isoffered in comparison to the mechanical drive.Problems like worm gear wear, backlash anddeviations are eliminated. This, and the possibilityof topological modifications, could now lead to arenascence of the generating grinders.ISBN: 1--55589--825--4 Pages: 9

04FTM3. A Method to Define Profile Modification ofSpur Gear and Minimize the Transmission ErrorAuthors: M. Beghini, F. Presicce, C. Santus

The object of this presentation is to propose asimple method to reduce the transmission error fora given spur gear set, at a nominal torque, bymeansof profile modification parameters. Iterativesimulations with advanced software are needed. Ahybrid method has been used, combining the finiteelement technique with semi analytical solutions. Atwo dimensional analysis is thought to be adequatefor this kind of work; in fact, the resulting softwaredoes not require much time for model definition andsimulations, with very high precision in the results.The starting configuration is presented. At eachsubsequent step, little alteration of one parameter isintroduced, and the best improvement in terms ofstatic transmission error is followed, until aminimum peak--to--peak value is achieved. At theend a check is needed to verify that the tip relief isenough to avoid the non--conjugate contact on thetip corner for a smooth transfer load.ISBN: 1--55589--826--2 Pages: 11

04FTM4. Influence of Surface Roughness on GearPitting BehaviorAuthors: T.C. Jao, M.T. Devlin, J.L. Milner, R.N. Iyer,and M.R. Hoeprich

In earlier studies, surface roughness had beenshown to have a significant influence on gear pittinglife. Within a relatively small range of surfaceroughness (Ra = 0.1 -- 0.3 micron), gear pitting lifeas measured by the FZG pitting test decreases asthe gear surface roughness increases. This inverserelationship between gear surface roughness andpitting life is well understood in the field. Todetermine whether this inverse relationship isapplicable to a wider range of surface roughnessvalues, a pitting study was conducted using gearswhose surface roughness ranges from 0.1 -- 0.6micron. The results were not completely expected.The study showed that the micropitting area isradically expanded when the gear surfaceroughness is close to the upper limit of the rangestudied. At the same time, the formation ofmacropitting is also greatly delayed. Not only is thepitting life significantly longer, but the initiation ofmacropitting can occur near or slightly beyond thepitch line. The paper discusses how high surface



roughness introduces a wear mechanism thatdelays the formation of macropits.ISBN: 1--55589--827--0 Pages: 12

04FTM5. Investigations on the Micropitting LoadCapacity of Case Carburized GearsAuthors: B.--R. Höhn, P. Oster, U. Schrade and T. Tobie

Micropitting is fatigue damage that is frequentlyobserved on case carburized gears. It is controlledby conditions of the tribological system of toothflank surface and lubricant. The oil film thicknesshas been found to be a dominant parameter.Lubricant base oil and additive, operatingconditions, surface roughness and gear geometryare known as important influence factors onmicropitting load capacity. In continuous work overseveral research projects major influences on themicropitting load capacity of gears weresystematically investigated. Based on the results ofinvestigations a calculation method to evaluate therisk of micropitting respectively to determine asafety factor for micropitting on case carburizedgears was developed. The calculation method isbased on the result of the micropitting test as alubricant tribological parameter, but enables thegear designer to take major influences such asoperating conditions, gear geometry and gear sizeof the actual application into consideration. Thepaper summarizes important results of thecontinuous experimental investigations andintroduces the proposed calculation method forrating the micropitting load capacity of casecarburized gears.ISBN: 1--55589--828--9 Pages: 15

04FTM6. The Effect of a A ZnDTP Anti--wear AdditiveonMicropitting Resistance of Carburised Steel RollersAuthors: Chi--Na Benyajati and Andrew V. Olver

Zinc di--alkyl dithio--phosphate (ZnDTP)compounds are widely used in engine andtransmission oils both as anti--oxidants and asanti--wear additives. However, recent work hasshown that many anti--wear additives appear tohave a detrimental effect on the resistance of gearsand other contacting components to various typesof rolling contact fatigue, includingmicropitting. Thepaper examines the effect of a secondary C6ZnDTP presence in low viscosity synthetic base oilon the resistance to micropitting and wear ofcarburized steel rollers, using a triple--contact disktester. It was found that the additive caused severemicropitting and associatedwear, whereas the purebase oil did not give rise to any micropitting. It wasfurther found that the additive was not detrimentalunless it was present during the first 100 000 cyclesof the test when it was found to exert a strong effecton the development of roughness on thecounter--rollers. It is concluded that the additive isdetrimental to micropitting resistance because it

retards wear--in of the contact surfaces, favoringthe development of damaging fatigue cracks. Thiscontrasts with some earlier speculation thatsuggested a direct chemical effect could beresponsible.ISBN: 1--55589--829--7 Pages: 10

04FTM7. A Short Procedure to Evaluate MicropittingUsing the New AGMA Designed GearsAuthors: Kevin J. Buzdygon and Angeline B. Cardis

At the 1998 AGMA Fall Technical Meeting,encouraging results of a prototype micropitting testusing specially designed gears on the standardFZG test rig were reported. Additional gear setsbecame available from AGMA in 2000.Subsequently, several sets of these experimentalAGMA test gears were used in an attempt todevelop a relatively short test procedure to evaluatemicropitting. The detailed results of these tests arediscussed in the paper. The procedure involvedrunning the test gears on the standard FZG test rigwith oil circulation for 168 hours. At the end of test,the gears are rated for micropitting, weight loss,pitting, and scuffing. Five commercially availableISO VG 320 gear oils, with performance in the FVAProcedure 54 micropitting test ranging from FLS9--low to FLS >10--high, were evaluated using thisprocedure. The degree of micropitting coverageranged from 34% to 7% in the new test procedure.Micropitting generally originated in themiddle of thegear tooth, instead of the root or tip. Overall, therewas excellent correlation of the degree ofmicropitting damage between the new testprocedure and FVA Procedure 54.ISBN: 1--55589--830--0 Pages: 8

04FTM8. Generalized Excitation of Traveling WaveVibration in GearsAuthor: Paul B. Talbert

Rotation of gears under load creates dynamicloading between the gears at tooth mesh frequencyand its harmonics. The dynamic loading can excitetraveling wave vibration in the gears. The strainassociated with the traveling wave vibration can beexcessive and result in high cycle fatigue of thegears. Prior investigations have examined travelingwave excitation for specific configurations, such asa sequential star system with a fixed planetarycarrier. Gear mesh excitation of traveling wavevibration can be generalized to include thefollowing: (1) any number of gears surrounding thecenter gear, (2) non--symmetric spacing of thesurrounding gears, (3) non--equal power transfer ofthe surrounding gears, and (4) the effect of periodicfeatures in the center gear. A closed formexpression is developed to quantify the relativeexcitation of traveling wave vibration for each nodaldiameter. This expression for the relative excitationis verified using analytical finite element examples.ISBN: 1--55589--831--9 Pages: 13



04FTM9. Design of a High Ratio, Ultra Safe, HighContact Ratio, Double Helical Compound PlanetaryTransmission for Helicopter ApplicationsAuthors: Frederick W. Brown, Mark J. Robuck,G. Keith Roddis and Timothy E. Beck

An ultra--safe, high ratio planetary transmission, forapplication as a helicopter main rotor drive, hasbeen designed under the sponsorship ofNRTC--RITA. It is anticipated that this newplanetary transmission offers improvementsrelative to the current state--of--the--art including,reduced weight, reduced transmitted noise andimproved fail--safety. This paper discusses theanalysis and design results for the subject planetarytransmission. Fabrication and testing of thetransmission will be conducted in subsequentphases of the project. Typically, the final stage inhelicopter main rotor transmission is the mostcritical and usually the heaviest assembly in thedrive system for any rotary wing aircraft. The newultra--safe, high ratio planetary transmission designutilizes a compound planetary configuration with a17.5:1 reduction ratio which would replace aconventional two stage simple planetarytransmission. The new design uses split--torquepaths and high combined contact ratio gearing.ISBN: 1--55589--832--7 Pages: 12

04FTM10.The Failure Investigation andReplacementof a Large Marine GearAuthors: Peter Hopkins, Brian Shaw, J. Varo, andA. Kennedy

The paper presents details of a recent gearboxproblem encountered on a Naval ship and the finalsolution bringing the ship back to full ability. Theproblemoccurred on themainwheel of a large, highpower Naval gearbox. The investigation showedthat pitting damage had developed as a result ofloose side plate bolts, which led on to bendingfatigue cracking. Additional investigations andmonitoring established that the damage had beenassisted by increased usage at high power levels,as well as a small number of significant overloads.Assessment of the gearbox design was that it hadbeen running very close to original design limits.Repairs were then carried out to remove and arrestany damage present, and monitoring procedureswere put in place to ensure no further damagedeveloped. Risk assessments were performed toallow the ship to continue to meet its demands. Fullrepair options were then considered andreplacement gear elements designed andproduced to increase future abilities and safetyfactors. The paper covers the discovery of theproblem, failure investigation, the in--situ repair, risk

assessment of continued running, prevention offurther damage, damage monitoring, thepermanent repair assessment, design,manufacture and installation of replacement gears,and trials.ISBN: 1--55589--833--5 Pages: 11

04FTM11. Gear Lubrication as a Reliability PartnerAuthor: Michael Holloway

Performance lubrication is quickly becoming acomponent of preventive, predictive, proactive andreliability based maintenance programs. Using thebest gear lubricant, coupled with system condition,monitoring and analysis, actually reduces overalloperating expenses dramatically. Varioustechniques such as system conditioning, oil andequipment analysis, along with product selectionand management are valuable tools which convertmany maintenance departments into reliabilitycenters. These concepts and others are discussedin this informative, hands on discussion which willreview best maintenance practices from variouscompanies and review how to implement similarprograms.ISBN: 1--55589--834--3 Pages: 8

04FTM12. Improved Tooth Load Distribution in anInvolute Spline Joint Using Lead Modifications Basedon Finite Element AnalysisAuthors: Frederick W. Brown, Jeffrey D. Hayes andG. Keith Roddis

Involute splines are prone to non--uniform contactloading along their length, especially in lightweight,flexible applications such as a helicopter main rotorshaft--to--rotor hub joint. In such applications, in theabsence of lead corrections, the torque istransferred non--uniformly along the length of thespline, resulting in a concentration of the toothcontact load at one end. A significantly improvedtooth load distribution is achieved by applying, tothe internally splined member, complex leadcorrections which vary continuously along thelength of the spline. Rotor hub splines withanalytically determined lead corrections weremanufactured and tested under design loadconditions. A standard rotor shaft--to--hub joint,which uses a step lead correction between splines,was also tested as a baseline. Test data indicatedthat the complex lead corrections resulted in anearly uniform contact load distribution along thelength of the spline at the design torque load. Thedata also showed that the load distribution for thesplines with the complex lead corrections wassignificantly improved relative to the baselinesplines.ISBN: 1--55589--835--1 Pages: 16



04FTM13. Superfinishing Motor Vehicle Ring andPinion GearsAuthors: Lane Winkelmann, Jerry Holland andRussell Nanning

Today, the automotive market is focusing on ”lubedfor life” differentials requiring no service for the life ofthe vehicle. Premature differential failure can becausedby bearing failures aswell as ring andpinionfailure. By super finishing the lapped ring and piniongear sets to a surface roughness less than 10microinch, lubricant, bearing and gear lives can besignificantly increased because of the concomitantelimination of wear and the temperature spikeassociated with break--in. Just a few years ago,super finishingmated, high production rate ring andpinion gear sets were considered impractical due totime and cost constraints. It was also assumed thatsuper finishing technology could not preserve thecontact pattern of the lapped andmatched gear set.This paper discusses a mass finishing operationwhich overcomes these obstacles and meets theneeds of a manufacturing facility. Gear metrology,contact patterns, transmission error and actualperformance data for super finished gear sets willbe presented along with the super finishingprocess.ISBN: 1--55589--836--X Pages: 16

04FTMS1. Stress Analysis of Gear Drives Based onBoundary Element MethodAuthor: Daniele Vecchiato

The stress analysis is performed as a part of TCA(Tooth Contact Analysis) for a gear drive. Unlike theexisting approaches, the proposed one does notrequire application of commercial codes (likeANSYS or ABAQUS) for derivation of contactmodel and determination of contact and bendingstresses. The contacting model is derived directlyby using the equations of tooth surfacesdeterminedanalytically. The boundary element approachallows to reduce substantially the number of nodesof the model. Determination of stresses caused byapplied load is obtained directly for the appliedcontacting model for any position of meshing. Thedeveloped approach is illustrated by stress analysisof helical gears with modified geometry.ISBN: 1--55589--837--8 Pages: 16

2002 PAPERS

02FTM1. The Effect of Chemically AcceleratedVibratory Finishing on Gear MetrologyAuthors: Lane Winklemann, Mark Michaud, GarySroka, Joseph Arvin and Ali Manesh

Chemically accelerated vibratory finishing is a

commercially proven process that is capable ofisotropically superfinishingmetals to an Ra < 1.0 in.Gears have less friction, run significantly cooler andhave lower noise and vibration when thistechnology is applied. Scuffing, contact fatigue(pitting), and bending fatigue are also reduced oreliminated both in laboratory testing and field trials.This paper presents studies done on aerospaceQ13 spiral bevel gears showing that the amount ofmetal removed to superfinish the surface is bothnegligible and controllable. Media selection andmetal removal monitoring procedures aredescribed ensuring uniform surface finishing,controllability and preservation of gear metrology.ISBN: 1--55589--801--7 Pages: 18

02FTM2. Development and Application ofComputer--Aided Design and Tooth Contact Analysisof Spiral--Type Gears with Cylindrical WormAuthors: V.I. Goldfarb and E.S. Trubachov

This paper presents the method of step--by--stepcomputer--aided design of spiroid--type gears,which involves gear scheme design, geometriccalculation of gearing, drive design, calculation ofmachine settings and tooth--contact analysis.Models of operating and generating gearing havebeen developed, including models of manufactureand assembly errors, force and temperaturedeformations acting in real gearing, and driveelement wear. Possibilities of CAD--techniqueapplication are shown to solve design andmanufacture tasks for gearboxes and gear--motorswith spiroid--type gears.ISBN: 1--55589--802--5 Pages: 15

02FTM3. The Application of Statistical Stability andCapability for Gear Cutting Machine AcceptanceCriteriaAuthor: T.J. (Buzz) Maiuri

Over the years the criteria for gear cutting machineacceptance has changed. In the past, cutting astandard test gear or cutting a customer gear totheir specification was all that was expected formachine acceptance. Today, statistical processcontrol (SPC) is required for virtually everymachinerunoff. This paper will cover the basic theory ofstability and capability and its application to beveland cylindrical gear cutting machine acceptancecriteria. Actual case studies will be presented todemonstrate the utilization of these SPCtechniques.ISBN: 1--55589--803--3 Pages: 26



02FTM4. Multibody--System--Simulation of DriveTrains of Wind TurbinesAuthor: Berthold Schlecht

During the last years a multitude of wind turbineshave been put into operation with continuouslyincreased power output. Wind turbines with 6 MWoutput are in the stage of development, a simpleextrapolation to larger dimensions of wind turbineson the basis of existing plants and operationalexperiences is questionable. This paper deals withthe simulation of the dynamic behavior of thecomplete drive train of a wind turbine by using adetailed Multi--System--Model with special respectof the gear box internals. Starting with the modelcreation and the analysis of the natural frequencies,various load cases in the time domain will bediscussed.ISBN: 1--55589--804--1 Pages: 13

02FTM5.Crack Length andDepth Determination in anIntegrated Carburized Gear/BearingAuthors: Raymond Drago and James Kachelries

In an effort to determine if processing cracks poseda safety of flight concern, several gears thatcontained cracks were designated to undergo arigorous bench test. Prior to the start of the test, itwas necessary to document, nondestructively, all ofthe crack dimensions. This paper will present aspecially modified magnetic rubber inspectiontechnique to determine crack lengths as short as0.006 inch, and a unique, highly sensitive,laboratory eddy current inspection technique toestimate crack depths up to +/-- 0.003 inch.ISBN: 1--55589--805--X Pages: 9

02FTM6. Contemporary Gear Hobbing -- Tools andProcess StrategiesAuthor: Claus Kobialka

Gear manufacturing without coolant lubrication isgetting more and more important. Modern hobbingmachines are designed to cope with dry hobbing. Inthe last years, carbide hobs were prevailing inhigh--speed hobbing due to their excellent thermalstability. Today, this high performance rate isconfronted with rather high tool costs and criticaltool handling. Powder metallurgical HSS combinedwith extremelywear resistant coating on the base of(Ti, Al)N offer interesting alternatives for dryhobbing. It is evident that existing conventional hobgeometries can be optimized respecting limitingfactors like maximum chip thickness and maximumdepth of scallops.ISBN: 1--55589--806--8 Pages: 11

02FTM7. Selecting the Best Carburizing Method forthe Heat Treatment of GearsAuthors: Daniel Herring, Gerald Lindell, David Breuerand Beth Madlock

Vacuum carburizing has proven itself a robust heattreatment process and a viable alternative toatmosphere carburizing. This paper will presentscientific data in support of this choice. Acomparison of atmosphere carburized gearsrequiring press quenching to achieve dimensionaltolerances in a “one piece at a time” heat treatingoperation, with a vacuum carburized processing afull load of gears that have been high gas pressurequenched within required tolerances.ISBN: 1--55589--807--6 Pages: 13

02FTM8. Compliant Spindle in Lapping and TestingMachinesAuthor: Bill McGlasson

This paper presents theory, analysis and results ofa novel spindle designwith application to bevel gearlapping and testing machines. The spindle designincludes a rotationally compliant element which cansubstantially reduce the dynamic forces inducedbetween the gearmemberswhile rolling under load.The theory of this spindle concept is presentedusing simplified models, providing the explanationfor the process benefits it brings. Analysis andsimulations give additional insight into thedynamics of the system. Finally, actual lapping andtesting machine results are presented.ISBN: 1--55589--808--4 Pages: 11

02FTM9. Gear RollScan for High Speed GearMeasurementAuthor: Andreas Pommer

This presentation features a revolutionary newmethod for the complete topographicalmeasurement of gears. The Gear RollScan systemis similar to one--flank gear rolling inspection.However, the master gear has measuring tracks onselected flanks. With two master gears in rollcontact, both the left and right flanks of thespecimen can be inspected simultaneously. After aspecified number of rotations, every measuringtrack on the master gears will contact every flank ofthe specimen this measuring device will always findthe worst tooth.ISBN: 1--55589--809--2 Pages: 10

02FTM10. Comparing the Gear Ratings from ISO andAGMAAuthor: Octave LaBath

In the early 1980’s several technical papers weregiven comparing gear ratings from ISO and AGMAshowing some interesting and diverse differencesin the trends when the gear geometry was changedslightly. These changes included addendummodification coefficients and helix angle.Differences also existed when the hardness andhardening methods were changed. This paper will



use rating programs developed by an AGMAcommittee to compareAGMAand ISO ratingswhilehaving the same gear geometry for both ratings.This will allow consistent trend analysis by onlychanging one gear geometry parameter whileholding other geometry items constant.ISBN: 1--55589--810--6 Pages: 17

02FTM11. Gear Design Optimization Procedure thatIdentifies Robust, Minimum Stress and MinimumNoise Gear Pair DesignsAuthor: Donald Houser

Typical gear design procedures are based on aniterative process that uses rather basic formulas topredict stresses. Modifications such as tip relief andlead crowning are based on experience and thesemodifications are usually selected after the designhas been considered. In this process, noise isusually an after thought left to be chosen by thedesigner after the geometric design has beenestablished. This paper starts withmicro--topographies in the form of profile and leadmodifications. Then, evaluations are made on theload distribution, bending and contact stresses,transmission error, film thickness, flashtemperature, etc. for a large number of designs.The key to this analysis is the rapid evaluation of theload distribution.ISBN: 1--55589--811--4 Pages: 15

02FTMS1Design and Stress Analysis of New Versionof Novikov--Wildhaber Helical GearsAuthor: Ignacio Gonzalez--Perez

This paper covers design, generation, tooth contactanalysis and stress analysis of a new type ofNovikov--Wildhaber helical gear drive. Greatadvantages of the developed gear drive incomparison with the previous ones will bediscussed, including: reduction of noise andvibration caused by errors of alignment, thepossibility of grinding, and application of hardenedmaterials and reduction of stresses. Theseachievements are obtained by application of: newgeometry based on application of parabolicrack--cutters, double--crowning of pinion andparabolic type of transmission errors.ISBN: 1--55589--812--2 Pages: 25

2001 PAPERS

01FTM1. Carbide Hobbing Case StudyAuthor: Yefim Kotlyar

Carbide hobbing improves productivity and cost,howevermany questions remain regarding the bestapplication, carbide material, hob sharpening,coating and re--coating, hob handling, consistencyand optimum hobwear, best cutting conditions, andconcerns for the initial cutting tool investment. This

paper is a case study of a successfulimplementation of carbide hobbing for an annualoutput of 250,000 gears, average lot size of about200--300 gears, producing gears of about 150different sizes and pitches, with 4 setups per day onaverage.ISBN: 1--55589--780--0 Pages: 16

01FTM2. The Ultimate Motion Graph for “Noiseless”GearsAuthors: Hermann J. Stadtfeld and Uwe Gaiser

Gear noise is a common problem in all bevel andhypoid gear drives. A variety of expensive geargeometry optimizations are applied daily in allhypoid gear manufacturing plants, to reduce gearnoise. In many cases those efforts have littlesuccess. This paper will present ”The UltimateMotion Graph”, a concept for modulating the toothsurfaces that uses modifications to canceloperating dynamic disturbances that are typicallygenerated by any gear types.ISBN: 1--55589--781--9 Pages: 16

01FTM3. Automated Spiral Bevel Gear PatternInspectionAuthors: S.T. Nguyen, A. Manesh, K. Duckworth andS. Wiener

Manufacturing processes for precision spiral bevelgears are operator intensive, making themparticularly costly in today’s small lot productionenvironment. This problem is compounded byproduction requirements for replacement parts thathave not been produced for many years. The paperwill introduce a new closed loop system capable ofreducing development costs by 90%andbevel geargrinder setup time by 80%. In addition, a capabilityto produce non--standard designs without part datasummaries is reviewed. Advancements will also bepresented for accepting precision gears using anelectronic digital master in lieu of a physical master.ISBN: 1--55589--782--7 Pages: 15

01FTM4. How to Inspect Large Cylindrical Gears withan Outside Diameter of More Than 40 InchesAuthor: Güenter Mikoleizig

This paper discusses the design and function of therelevant machines used for individual errormeasurements such as lead andprofile formaswellas gear pitch and runout. The author will coverdifferent types of inspection machines such as:stationary, CNC--controlled gear measuringcenters, and transportable equipment for checkingindividual parameters directly on the gear cutting orgear grinding machine.ISBN: 1--55589--783--5 Pages: 20

01FTM5. Traceability of Gears -- New Ideas, RecentDevelopmentsAuthors: Frank Härtig and Franz Wäldele

Some national standard tolerances for cylindricalgears lie in, and evenbelow, the rangeof instrumentmeasurement uncertainties. This paper presents a



concept based on three fundamental goals:reduction of measurement uncertainty,construction of workpiece--like standards, andshortening of the traceability chain. One of the focalpoints is the development of a standard measuringdevice as an additional metrological frameintegrated into a coordinate measuring machine.ISBN: 1--55589--784--3 Pages: 6

01FTM6.Performance--BasedGear--Error Inspection,Specification, andManufacturing--Source DiagnosticsAuthors: William D. Mark and Cameron P. Reagor

This paper will show that a frequency--domainapproach for the specification of gear toothtolerance limits is related to gear performance andtransmission errors. In addition, it is shown that onecan compute, from detailed tooth measurements,the specific tooth error contributions that cause anyparticularly troublesome rotational harmoniccontributions to transmission error, therebypermitting manufacturing source identification oftroublesome operation.ISBN: 1--55589--785--1 Pages: 15

01FTM7. Chemically Accelerated Vibratory Finishingfor the Elimination of Wear and Pitting of Alloy SteelGearsAuthors: Mark Michaud, Gary Sroka and LaneWinkelmann

Chemically accelerated vibratory finishingeliminates wear and contact fatigue, resulting ingears surviving higher power densities for a longerlife compared to traditional finishes. Studies haveconfirmed this process is metallurgically safe forboth through hardened and case carburized alloysteels. The superfinish can achieve an Ra < 1.5minch, while maintaining tolerance levels.Metrology, topography, scanning electronmicroscopy, hydrogen embrittlement, contactfatigue and lubrication results are presented.ISBN: 1--55589--786--X Pages: 16

01FTM8. The Effect of Spacing Errors and Runout onTransverse Load Sharing and the Dynamic Factor ofSpur and Helical GearsAuthors: Husny Wijaya, Donald R. Houser and JonnyHarianto

This paper addresses the effect of two commonmanufacturing errors on the performance of spurand helical gears; spacing error and gear runout. Inspacing error analysis, load sharing for twoworst--case scenarios are treated, one where a

tooth is out of position and the second wherestepped index errors are applied. The analyzedresults are then used as inputs to predict geardynamic loads, dynamic tooth stresses anddynamic factors for gear rating.ISBN: 1--55589--787--8 Pages: 16

01FTM9. New Opportunities with Molded GearsAuthors: Roderick E. Kleiss, Alexander L. Kapelevichand N. Jack Kleiss Jr.

Unique tooth geometry that might be difficult oreven impossible to achieve with cut gears can beapplied to molded gears. This paper will investigatetwo types of gears that have been designed,molded and tested in plastic. The first is anasymmetric mesh with dissimilar 23 and 35 degreepressure angles. The second is an orbitingtransmission with a 65 degree pressure angle. Bothtransmissions have higher load potential thantraditional design approaches.ISBN: 1--55589--788--6 Pages: 11

01FTM10. Design Technologies of High Speed GearTransmissionAuthor: Jeff Wang

This paper discusses a few critical factors and theireffects on high speed gear transmissions. The firstfactor is centrifugal force and its effect on tooth rootstrength, tooth expansion and backlash and theinterference fit between gear and shaft. The secondis system dynamics, including critical speed,dynamic balancing and the torsional effects offlexible couplings. The third is the windage loss withdifferent combinations of helix and rotationdirection, lubricant flow rate, flow distribution andtheir effects on tooth bulk temperature field andtooth thermal expansion.ISBN: 1--55589--789--4 Pages: 8

01FTM11. Kinematic and Force Analysis of a SpurGear System with Separation of Sliding and Rollingbetween Meshing ProfilesAuthor: D. E. Tananko

This paper describes a comprehensive study of thenovel gear designwith physical separation betweensliding and rolling motions of themesh gear contactpoint. The sliding motion is accommodated byshear deformation of a thin--layered rubber--metallaminate allowing very high compression loads.Several important advantages will be presentedwhen comparing the composite gear design to theconventional involute profile.ISBN: 1--55589--790--8 Pages: 50



01FTMS1. Optical Technique for Gear ContouringAuthor: Federico Sciammarella

This paper presents an optical technique(projectionmoiré) that is compact and can provide aquick full field analysis of high precision gears.Comparisons are made between mechanical andoptical profiles obtained of a gear tooth.ISBN: 1--55589--791--6 Pages: 12

2000 PAPERS

2000FTM1. Minimization of In--Process Corrosion ofAerospace GearsAuthors: S.T. Nguyen, A. Manesh, and J. Reeves

This paper discusses problems and root causesassociated with the corrosion of aerospace gearsduring the manufacturing process.

Specimens of common base materials used inprecision gearing were subjected to processconditions that contribute to corrosion initiationincluding: different coolant types andconcentrations, material heat treat conditions, basematerial magnetism, surface finish and ironparticles in coolant.ISBN: 1--55589--762--2 Pages: 7

2000FTM2. The Calculation of Optimum SurfaceCarbon Content for CarburizedCaseHardenedGearsAuthor: P.C. Clarke

At present, there is not a method to calculateeutectoid carbon from chemical analysis and theeutectoid carbon is not the best element uponwhichto base surface carbon requirements. This paperwill define the conditions and propose a method tocalculate an optimum carbon level to minimize thepossibilities of retained austenite, cementite andbainite.ISBN: 1--55589--763--0 Pages: 8

2000FTM3. Comparison of New Gear MetallurgyDocuments, ISO 6336--5 and AGMA 923 with GearRating Standards AGMA 2001 and 2003Author: A.A. Swiglo

This paper will compare and contrast these fourdocuments.What’s new,what’s different andwhat’shidden in the footnotes. Knowing the differenceswill be important to the users of these documents.ISBN: 1--55589--764--9 Pages: 110

2000FTM4. Parametric Influences in the ISO ProjectConcerning Worm Gear RatingAuthor: M. Octrue

This paper analyzes the influence of differentparameters in CD ISO 14561 Load Capacity

Calculation of Worm Gears such as; efficiency,wear load capacity, pitting, deflection and tooth rootstress. The influencing parameters are divided intodifferent categories such as external parameters ofloading conditions, environmental parameters oflubricant temperature and driving and drivenmachines.ISBN: 1--55589--765--7 Pages: 10

2000FTM5. Systematic Investigations on theInfluence of Viscosity Index Improvers on EHL--FilmThicknessAuthors: B.--R. Hohn, K. Michaelis and F. Kopatsch

This paper compares film thickness calculations tomeasurements taken using polymer containing oilsin a twin diskmachine. Results will show all polymercontaining oils form lower film thicknesses thanstraight mineral oils of the same viscosity aftershearing. A polymer correction factor is derivedfrom test results improving the accuracy of filmthickness calculation.ISBN: 1--55589--766--5 Pages: 11

2000FTM6. Did the Natural Convection Exist inMechanical Power Transmissions? Theoretical andExperimental ResultsAuthor: M. Pasquier

ISOTR14179parts 1 and2, give values of total heatexchange coefficients in the case of naturalconvection and forced convection. This paper willcompare the values of total heat exchangeobtainedfrom a theoretical study to the values given in theISO Technical Reports.ISBN: 1--55589--767--3 Pages: 10

2000FTM7. An Analytical -- FEM Tool for the Designand Optimization of Aerospace Gleason Spiral BevelGearsAuthor: C. Gorla, F. Rosa, and P.G. Schiannini

To save time and money during the design processa tool based on analytical algorithms and on FEMmodels is introduced. As a first step, the conjugatesurfaces theory is applied to a bevel set. Ananalytical tooth contact analysis is performed todetermine the theoretical contact points on flanksurfaces versus the meshing points. Information isthen derived by the contact analysis and used togenerate Finite Element models of the gear pair onthe basis of the theoretical contact pattern. A finalsimulation by means of FEM models takes intoaccount load sharing between tooth pairs.ISBN: 1--55589--768--1 Pages: 12



2000FTM8. Stock Distribution Optimization in FixedSetting Hypoid PinionsAuthor: C. Gosselin and J. Masseth

This paper presents an algorithm used to optimizethe stock distribution between the roughing andfinishing cuts for fixed setting spiral bevel andhypoid members. The optimization is based on theSurface Match algorithm, where differencesbetween the roughing and finishing spiral angle,pressure angle and tooth taper are minimized inorder to obtain rough and finished tooth flanks thatare parallel.ISBN: 1--55589--769--X Pages: 8

2000FTM9. Cylindrical Gear Inspection and BevelGear Inspection -- A Simple Task by Means ofDedicated CNC--Controlled Gear InspectionMachinesAuthor: G. Mikoleizig

This paper will discuss the design, function,software management and probe systems of theinspection machines. Analytical tooth contactanalysis of a cylindrical gear set by means of thecombined effects of gear and pinion is shown on thebasis of individual profile and alignmentmeasurements. A fully automatic correction systemwill be introduced for checking the flank form onspiral bevel gears.ISBN: 1--55589--770--3 Pages: 25

2000FTM10. Bending Fatigue Investigation underVariable Load Conditions on Case Carburized GearsAuthors: B.--R. Hohn, P. Oster, K. Michaelis,Th. Suchandt and K. Stahl

Variable load spectrum tests are carried out atdifferent load levels in a step program and atrandom loading. The results of step programmedtests show a substantial influence of the period ofthe programmed subsequence of fatigue life.Fatigue life decreases when the subsequenceperiod is shortened. With substantially shortenedsubsequences in step programmed test nearly thesame fatigue life is reached as in random load tests.ISBN: 1--55589--771--1 Pages: 14

2000FTM11. UltraSafe Gear Systems -- Single ToothBending Fatigue Test ResultsAuthors: R.J. Drago, A. Isaacson and N. Sonti

This paperwill discuss a system fromapoint of viewof ”what happens when a failure occurs”. Gearswere manufactured with seeded faults to simulateunexpected defects in various portions of the highlyloaded gear tooth and rim sections. Crackpropagation was monitored by measuring effectivemesh stiffness and applied loading to provide bothwarning of an impending failure and a reasonableperiod operation after initiation of a failure for a safelanding.ISBN: 1--55589--772--X Pages: 9

2000FTM12. The Finite Strips Method as anAlternative to the Finite Elements in Gear Tooth Stressand Strain AnalysisAuthors: C. Gosselin and P. Gagnon

The Finite Strip Method (FSM), which may beconsidered a subset of the Finite Element Method(FEM), is presented as an alternative to (FEM) thatrequires very little meshing effort and can beapplied to virtually any tooth geometry whileoffering precision comparable to that of FiniteElements. This paperwill cover the (FSM)model forspur and helical gears, plates of variable thicknesssuch as the teeth of face gear members and forspiral bevel and hypoid gears.ISBN: 1--55589--773--8 Pages: 11

2000FTMS1. Effects of Helix Slope and FormDeviation on the Contact and Fillet Stresses of HelicalGearsAuthors: R. Guilbault

An investigation is conducted on the effects of helixslope and form deviation tolerances specified forgrades 5 and 7 of the ANSI/AGMA ISO 1328--1 forcylindrical gears. The results show and almostlinear correspondence between deviationamplitude and tooth load and fillet stress increases:using grade 7 instead of grade 5 can double thetooth flank load increase and associated fillet stressincrease. Results also show that effects are evenmore significant on themaximum contact pressure.ISBN: 1--55589--774--6 Pages: 21

1999 PAPERS

99FTM1. The Barkhausen Noise Inspection Methodfor Detecting Grinding Damage in GearsAuthors: J.S. Ceurter, C. Smith and R. Ott

When grinding hardened steel there is always thepossibility for surface damage in the form ofresidual stress and microstructural changes.Methods for detecting this sort of damagemay havedrawbacks, such as production time, complexity,subjectivity and use of hazardous chemicals. Theauthors present a relatively new method, known asthe Barkhausen noise analysis, that may meet thedemand for measuring defects in ground steels.ISBN: 1--55589--739--8 Pages: 10



99FTM2. Traceability Strategies for the Calibration ofSpline and Serration GaugesAuthor: W. Beyer

Form and shape of running gears are oftentoleranced. The same features of splines andserration gauges may need to have the samepermissible geometrical tolerances as those forrunning gears. Examples are given in the paperwhich prove that, in view of often small requiredtolerances, it will often be necessary to calibratesplines and serration gauges with the smallestpossible uncertainty.ISBN: 1--55589--740--1 Pages: 5

99FTM3. Measurement Uncertainty for Pitch andRunout ArtifactsAuthor: B. Cox

Primary--level calibration of pitch and runoutartifacts require quantifying the measurementuncertainty on the artifact being calibrated by amethod that does not rely on a transfer comparison.The measurement decompo--sition method,developed jointly by (NIST) and (ORMC)personnel, is used to determine the uncertainty ofeach component of the measurement task.ISBN: 1--55589--741--X Pages: 14

99FTM4. Gear Oil Micropitting EvaluationAuthors: A.B. Cardis and M.N. Webster

Besides operating conditions such as load, speed,sliding and specific film thickness, the chemicalcomposition of a lubricant has been found toinfluence micropitting of case hardened gears. Thedevelopment ofmicropitting resistant lubricants hasbeen limited both by a lack of mechanismunderstanding and a lack of a readily availablelubricantmicropitting test. This paper reports effortsto develop alternate methods to study micropittingperformance of individual additives andcombinations of additives with a roller discmachine. Concurrently, a full--scale gear test using”real world” gearing is covered.ISBN: 1--55589--742--8 Pages: 16

99FTM5. Analysis of Micropitting on PrototypeSurface Fatigue Test GearsAuthor: M.R. Hoeprich

Experimental gears designed for surface fatiguestudies by the AGMA Helical Gear RatingCommittee and tested in a FZG test rig wereevaluated by the author. This paper presentsresults obtained through optical profilometry, SEMand metallographic examinations.ISBN: 1--55589--743--6 Pages: 11

99FTM6. The Submerged Induction Hardening ofGearsAuthor: D.W. Ingham

With examples of field failures directly attributableto the Tooth by Tooth Induction Hardening, therehas been a negative feeling against the use of this

process. This paper shows successes of theprocess founded on Process Development andQuality Control. The author presents a case for andagainst Tooth by Tooth Induction Hardening.ISBN: 1--55589--744--4 Pages: 12

99FTM7. Ductile Iron as a Material for Open GearingAuthor: P. Graham

This paper covers an outline of ductile iron and thephysical properties that can be expected fromdifferent grades. The types of heat treatment,properties that can be expected and also hardnessvalues are provided for typical gear blanks.ISBN: 1--55589--745--2 Pages: 15

99FTM8. Power--Dry--Cutting of Bevel GearsAuthor: H.J. Stadtfeld

High speed machining using carbides has beenknown for some decades for milling and turningoperations. Improvements in carbide grades andsintering processes in combination with newcoatingmethods and the use of CNCmachines haslead to a significantly new trend in cutting bevelgears. This paper discusses bevel gear dry cuttingmethods with surface cutting speeds of 1000ft./min. for continuous face hobbing and plungecutting single index face milling.ISBN: 1--55589--746--0 Pages: 10

99FTM9.DryHobbing Process Technology RoadMapAuthors: G. Schlarb and K. Switzer

Technology in today’s gear cutting industrymakes itimpossible to assume that there is one processcapable of meeting the requirements of eachapplication. This paper discusses extensive tooldevelopments that have taken place in recent yearsaswell as the explosion of new technologywith bothcoatings as well as new materials. The authordiscusses how to determine the best combinationpossible for a given application.ISBN: 1--55589--747--9 Pages: 10

99FTM10. Design and Testing of a Marine GearboxAuthor: J. Bos

This paper gives an overview of design andback--to--back testing results for gearboxes that aredesigned for low noise and vibration levels. Designaspects such as tooth corrections, tooth loading,gear lay--out, balancing, lubricating systems and aresilient mounting system will be discussed.Specific attention for the design was given tominimize the number of rotating elements underload, to have optimal corrections for loadedconditions and to optimize the tooth loading.ISBN: 1--55589--748--7 Pages: 13

99FTM11. Performance Study of Nitrided Gears inHigh Speed Epicyclic Gearbox Used in GasTurbogenerators -- A Case StudyAuthor: A.K. Rakhit

Nitrided gears are preferred in some designs due totheir low heat treat distortion characteristics and



resistance to scuffing under low oil--film thickness,an inherent phenomenon at sun gear mesh--planetmesh in epicyclics. This paper discusses andverifies these properties plus the tendency of thesegears to fail under heavy shock loads.ISBN: 1--55589--749--5 Pages: 4

99FTM12. Gearbox Field Performance from aRebuilder’s PerspectiveAuthor: C. Schultz

The focus of this paper is the actual fieldperformance of a variety of over 2000 differentgearboxes that have been repaired over the last 15years. The information presented consists of astatistical review of the types of gearboxes repairedand the typical failure modes. Among the problemsdescribed in detail are tooth breakage, tooth wear,housing bore damage, seal wear and lube systemfailure.ISBN: 1--55589--751--7 Pages: 6

99FTM13. Failures of Bevel--Helical Gear Units onTraveling Bridge CranesAuthor: J.M. Escanaverino

Frequent failures of bevel gear units in travelingdrives of bridge cranes pose a difficult problem formaintenance and discussions on the necessarygear unit Service or Application Factor selection.This paper focuses on the origin of the troubles,withan insight on the dynamics of the drive train.ISBN: 1--55589--750--9 Pages: 6

99FTM14. The Effect of Material Defects on GearPerformance -- A Case StudyAuthors: R.J. Drago and A.F. Filax

The mechanism by which failures occur due tomaterial defects is often circuitous and not readilyapparent. In this case study, the authors examinethe failure of a medium--sized pinion used in amining application. The mode of failure was rathercatastrophic in nature but did not follow any of thetypically understood mechanisms such as toothbending, surface distress, wear, etc. This paperpresents a summary of the failure, its investigationand the methods proposed for its resolution.ISBN: 1--55589--752--5 Page 7

99FTM15. Theoretical Model for Load Distribution onCylindrical Gears: Application to Contact StressAnalysisAuthors: J.I. Pedrero, M. Pleguezuelos, M. Artés, A.Fuentes, and C. García--Masiá

The elastic models of gear tooth behavior areusually based on the hypothesis of uniform loaddistribution along the line of contact. The calculationmethods of ISO and AGMA assume that the loadper unit of length is equal to the total load divided bythe length of contact. In this paper, the load sharingalong the line of contact is determined from thehypothesis of minimum elastic potential. From thisnonuniform load distribution andHertz’s equation, a

method for determining both the value and thelocation of the critical contact stress is described.ISBN: 1--55589--753--3 Pages: 13

99FTM16. The Multi--Objective Optimization ofNonstandard Gears Including RobustnessAuthors: D.R. Houser, A.F. Luscher, I.C. Regalado

The design of gears involves the optimization ofdifferent objectives, and the presence of errors inthe manufacturing and operating conditions affectsthe performance of the gears; therefore, a robustoptimization procedure applying Taguchi methodswas used as a tool in the design of nonstandardcylindrical gears. This paper presents an outline ofthe procedure and discusses some of the results.ISBN: 1--55589--754--1 Pages: 14

99FTM17. Synthetic Oils for Worm Gear LubricationAuthor: U. Mann

This paper shows several synthetic gear oils andtheir influence on wear and efficiency of highlyloaded worm gears. The results are based onmeasurements carried out on the Kluber worm geartest rig. This test rig allows the measurement ofinput speed, input torque, output torque, bulk andsump temperature. The measured results arecompared with other investigations such asmeasurements of friction coefficients and DIN3996.ISBN: 1--55589--755--X Pages: 9

99FTM18. Effects of Wear on the Meshing Contact ofWorm GearingAuthors: D. Houser, M. Vaishya and X. Su

Worm gear contact stresses are the majorcontributor to worm gear wear and durabilityfailures. In this paper, a combination of loaded tests,coordinate measurements, surface reverseengineering and a special finite element method isemployed to study the effect of break--in wear onmeshing contact between the mating surfaces ofworm gearing parts. Three different wheel toothgeometries are investigated in this paper.ISBN: 1--55589--756--8 Pages: 11

99FTMS1. Modeling and Measurement of SlidingFriction for Gear AnalysisAuthors: M. Vaishya and D.R. Houser

This student paper discusses background studiesneeded for the prediction of sliding resistance ongear teeth. Various elastohydrodynamic and mixedlubrication theories for coefficient of traction areexamined. These theories are evaluated withrespect to experimental results from two--disk testsfor several parameters that simulate thecontinuously varying properties during gearengagement. Based on the comparison oftheoretical predictions and test results on a spurgear pair, the lubricationmodels are evaluated, withspecial emphasis being placed on the dynamicmodeling of friction.ISBN: 1--55589--757--6 Pages: 12



1998 PAPERS

98FTM1. A Method for Predicting the Dynamic RootStresses of Helical Gear TeethAuthors: D.R. Houser and J. Harianto

The AGMA dynamic factor has traditionally beentreated as a ”dynamic” load factor where tooth loadis the sum of all the tooth forces that are appliedalong the plane of action at any instant of time.Knowing the total load, however, says little aboutthe degree of load sharing or the load position on atooth where the dynamic load is a maximum. Thepaper describes a method that merges thecapabilities of sophisticated load distribution anddynamic excitation routineswith a timedomain geardynamics simulation. The effects of tooth surfacemodifications, misalignments and spacing errorsmay be analyzed.ISBN: 1--55589--719--3 Pages: 10

98FTM2. Mesh Friction in GearingAuthor: C.M. Denny

Plastic gears are often run dry in their applications.The subsequent tooth sliding friction forces have asizable effect on the magnitude of tooth rootbending in both the driving and driven gears and thepoint of tooth--load application. A calculationmethod is given for the solution of these frictionaleffects.ISBN: 1--55589--720--7 Pages: 11

98FTM3. Basic Studies on Fatigue Strength ofCase--Hardened Steel Gear -- Effects of Shot Peeningand/or Barrelling ProcessesAuthors: S. Hoyashita, M. Hashimoto and K. Seto

The paper presents testing results on the effects ofa barrelling finishing process on the fatigue strengthof shot peened, carburized and carbo--nitridedgears. The enhancement of surface durability ratingespecially after performing post--peeningoperations to improve the surface finish wasextensively evaluated and is discussed, along withshot peened bending fatigue.ISBN: 1--55589--721--5 Pages: 9

98FTM4. Effect of Uncontrolled Heat Treat Distortionon the Pitting Life of Ground, Carburized andHardened GearsAuthor: A.K. Rakhit

The amount of grinding to correct uncontrolleddistortion produced during the carburizing andhardening process can result in a reduction of thesurface hardness of the tooth flanks and ultimatelydecreased pitting life of the gear teeth. The resultspresent an evaluation that yields pitting life deratingfactors as a function of hardness versus case depthgradient and severity of distortion for a number ofmaterials.ISBN: 1--55589--722--3 Pages: 5

98FTM5. Low Vibration Design of a Helical Gear PairAuthor: K. Umezawa

The paper presents recent findings dealing withtooth surface modifications that can beimplemented to realize quiet running, low vibrationhelical gear sets. The investigation looked at theeffects of tooth deviations and modifications onperformance that are based upon bias--in andbias--out observations. Experimental resultsindicate that there is an asymmetrical feature in therelation between vibration magnitude and directionof each deviation of a gear pair in mesh.ISBN: 1--55589--723--1 Pages: 13

98FTM6. Calibration of Master Gears on CoordinateMeasurement MachinesAuthors: B. Cox, B. Rasnick, B. Adkins and E. Walker

Primary--level calibration of master gears requiresquantifying the measurement uncertainty of a threedimensional surface in space by amethod that doesnot rely on a transfer comparison. The paperdescribes a measurement composition methoddeveloped at NIST and ORMC that is used todetermine the uncertainty of each component of themeasurement task.ISBN: 1--55589--724--X Pages: 18

98FTM7. Checker of 3D Form Accuracy of Hypoid &Bevel Gear Teeth for the New Generation of QualityControlAuthors: A. Kubo, Y. Saito, S. Kato, N. Kondo, and N.Aoyama

Knowing the three dimensional geometry of bevelgear teeth is critical to evaluating manufacturingprocesses and ultimately performance. The paperdiscusses advancements made to design andproduce a practical and reliable gear checker thatcan measure parameters such as the tooth profilecurve and tooth lead curve.ISBN: 1--55589--725--8 Pages: 13

98FTM8. Evaluation of Wear, Scuffing and PittingCapacity of Gear LubricantsAuthors: K. Michaelis, B.--R. Höhn and P. Oster

For maximum energy savings, low viscositylubricants are frequently used. The trend towardincreased transmitted power has lead to higheroperating temperatures, resulting in thinnerlubricating films. New test methods are describedthat have been developed which use modified FZGtest rigs to evaluate low speed wear, scuffing andpitting. Test results on various lubricants arediscussed.ISBN: 1--55589--726--6 Pages: 10

98FTM9. Studies on Improvement of SurfaceDurability of Case--Carburized Steel Gear -- Effects ofSurface Finish Processes upon Oil Film FormationAuthors: M. Hashimoto, S. Hoyashita and J. Iwata

The results of an extensive test program conductedto analyze the effects of surface finishenhancements on the formation of gear mesh oil



films of surface hardened gears are discussed. Theuse of an electric resistancemethod for determiningconditions of oil film formation relative to changes intooth profile, crowning and surface roughness areevaluated.ISBN: 1--55589--727--4 Pages: 9

98FTM10. Local Coefficients of Friction inWormGearContactsAuthors: K. Steingröver and B.--R. Höhn

Because the friction conditions of worm gearscannot be determined directly, a special three disktest rig was designed to simulate the contactconditions for discrete points along the contact linesof a worm gear. The results are presented of testsemploying various lubricant types and materialcombinations.ISBN: 1--55589--728--2 Pages: 8

98FTM11. Improving Pump Gear Geometry ThroughSecondary Gear Tooth FinishingAuthors: S. Haye

The direction of the hydraulic gear pump industry ishigher--pressure pumps that run quieter and moreefficiently. In light of this, there is great importance indeveloping improved pump gears that will satisfythe demands of tomorrow’s hydraulic industry. Theobjective of improved geometry for reduced noiseand contact stresses falls in step with the entiregear industry. Following is a discussion of threegears that have been developed for their strengthand quality. One of the gears is a fuel pump gearwith stringent controls placed on tooth alignmentvariation. Another gear was developed for highfatigue strength and improved gear geometry forhigh--pressure oil pumping applications. The thirdgear is not a pump gear but was developed forbetter gear geometry to reduce noise in a copierapplication.ISBN: 1--55589--729--0 Pages: 9

98FTM12. Gear Refurbishment, An EconomicalApproach for Aerospace Overhaul and RepairAuthors: A. Meyer and T. Johnson

The paper describes a successful program that isbeing deployed to re--work power reduction andaccessory gears used in Coast Guard helicoptertransmissions. The development andimplementation of the critical stages of this process-- incoming inspection and evaluation, specialmachining techniques, qualification testing andfinal certification -- are discussed.ISBN: 1--55589--730--4 Pages: 19

1997 PAPERS

97FTM1. Calibration of Gear Measuring Instrumentsand Their Application to the Inspection of ProductGearsAuthors: B.L. Cox and R.E. Smith

Discusses the instrument conditions, alignmentand calibration requirements for measurement tomeet accuracy specifications of today’s productgears. Also offers guidelines for the alignment ofinstrument elements such as centers, ways andprobe systems; and the application of gear artifactsto determine instrument calibration, including thedetermination of measurement uncertainty.ISBN: 1--55589--695--2 Pages: 67

97FTM2. Determining Sound Power Levels ofEnclosed Gear Drives Using the Sound IntensityMethodAuthor: C. Burriss

Presents highlights of a practical case studyillustrating how sound power level data was used tovalidate a design improvement of an encloseddrive. The practical use of sound intensitymeasurements for the determination of encloseddrive sound power under full load is compared withANSI/AGMA 6025--C90 methods. Also reviewsimportant characteristics of the measurementenvironment.ISBN: 1--55589--696--0 Pages: 7

97FTM3. Detection of Fatigue Cracks in Gears withthe Continuous Wavelet TransformAuthors: D. Boulahbal, M.F. Golnaraghi and F. Ismail

In the past, traditional machinery conditionmonitoring and gear fault detection focused eitheron time or frequency domain vibration analysis. Thesensitivity of the newly developed wavelettransform technique allows the user to look at theevolution in time of a vibration signal’s frequencycontent for fatigue crack detection. Papercompares this new technique against moreconventional methods.ISBN: 1--55589--697--9 Pages: 6



97FTM4. Measurement and Predictions of PlasticGear Transmission Errors with Comparison to theMeasured Noise of Plastic and Steel GearsAuthors: L. Liauwnardi, D.R. Houser and A. Luscher

This paper takes transmission error and soundpressure level measurements of plastic gear sets,and compares them to experimental statictransmission measurements and computerpredictions. Also compares transmission error andsound pressure levels of plastic gears with largedeflections and steel gears of similar geometries.ISBN: 1--55589--698--7 Pages: 11

97FTM5. Improved Finite Element Model forCalculating Stresses in Bevel and Hypoid Gear TeethAuthors: L.E. Wilcox, T.D. Chimner and G.C. Nowell

When spiral bevel and hypoid gear results arecompared with the predicted fillet strain of a threedimensional tooth model with experimental straingage data using H--adaptive and P--adaptive finiteelement theory, preliminary results indicateagreement within 10%. This paper discussesrefinement in tooth support regions, and a precisemodel that correctly predicts the range of strainfrom tensile to compressive values as the gearteeth roll through mesh.ISBN: 1--55589--699--5 Pages: 11

97FTM6.On the Location of the Tooth Critical Sectionfor the Determination of the AGMA J--FactorAuthors: J.I. Pedrero, C.García--Masiá andA. Fuentes

Describes a modification to the AGMA J--factordefinition for determining the point of maximum rootbending stress. The condition where the Navier’sstress is maximum, defined by the point ofintersection of the root trochoid and the thinnestparabola containing a point of the trochoid, is used.The occurrence on its involute as well as in the roottrochoid with a non--iterative calculation is alsocovered.ISBN: 1--55589--700--2 Pages: 7

97FTM7.Bending Load on Internal Gears of PlanetaryGear SetsAuthors: H. Linke and C. Jahn

This paper presents the results of investigationsregarding a more precise determination of bendingstress in the tooth root of internal gear rims used inplanetary drives. This method includes the effectsof the gear rime design and mounting, which isessential in almost all cases. Also proposes apractical calculation method using generalizedstress concentration factors, which has been testedby actual measurements on planetary gearing.ISBN: 1--55589--701--0 Pages: 10

97FTM8.NewGuidelines forWind TurbineGearboxesAuthors: R.L. Errichello and B. McNiff

Collectively, mush has been learned about theunique operation and gear unit loading in windturbine applications. This paper will present an

overview of AGMA/AWEA 921--A97,Recommended Practices for Design andSpecification of Gearboxes for Wind TurbineGenerator Systems. This Information Sheet isdedicated to procurement specifications, qualityassurance, design, manufacturing, lubrication,maintenance and other subjects related to reliablewind turbine gear unit applications.ISBN: 1--55589--702--9 Pages: 5

97FTM9. Relations Between Wear and PittingPhenomena in Worm GearsAuthor: M. Octrue

Describes the influence of different parameters(geometry, contact pattern, contact pressure,sliding velocity, etc.) on thewear and pitting of wormgearing. The paper proposes new criteria forcomparing capacity of different worm geargeometries to predict performance. In addition, itdiscusses the prediction of wear and pittingbehavior based on experimental results with longendurance test measurements.ISBN: 1--55589--703--7 Pages: 8

97FTM10. UltraSafe Gear Systems for CriticalApplications -- Initial DevelopmentAuthors: R.J. Drago, A.D. Sane, F.W. Brown

This paper presents a basic paradigm shift requiredto design and develop ultra--safe powertransmission gears. It also describes the initialresults of a new program that developed a set ofguidelines to improve the fail--safe operation ofhelicopter transmissions, while not affecting eitherthe required performance or weight characteristics.ISBN: 1--55589--704--5 Pages: 22

97FTM11.Non--Dimensional Characterization ofGearGeometry, Mesh Loss and WindageAuthor: J.P. Barnes

New relationships for involute spur gear geometryare introduced and integrated with new methods ofcorrelating lubricant traction and windage test data.Compact math models for lubricant density andviscosity under contact pressure are proposed. Amodern approach to dimensional analysis isintroduced to characterize lubricant traction dataand gear windage data with dimensionless termswhich apply to gear systems which may have aconfiguration and/or size different from thosetested. Finally, system considerations for optimalgearbox efficiency are proposed.ISBN: 1--55589--705--3 Pages: 12

97FTM12. Introduction of a Jobbing System for Beveland Hypoid GearsAuthor: H.J. Stadtfeld

The paper describes a new manufacturing systemthat enables the flexibility to produce bevel andhypoid gears of any size and specification,including gear sets produced on old equipment withdifferent cutting methods, with an extremely lowinvestment. This system includes a new PC



program that performs calculations of tooth contactanalysis, ease off and machine settings, and anewly developed carbide tool skiving process.ISBN: 1--55589--706--1 Pages: 13

97FTM13. Three Innovations Advance the Science ofShot PeeningAuthors: J.S. Eckersley and T.J. Meister

Three recent innovations have been developed toextend the effective shot peening state of the art toprolong the fatigue life of gears: 1) a process thatprovides a smooth surface after peening toincrease the resistance to surface fatigue; 2) acomputer program that makes a reasonableprediction of residual stress curves, and 3) acoupon system that makes actual x--ray diffractioncurves tomonitor production shot peeningpossible.ISBN: 1--55589--707--X Pages: 10

97FTM14. Refinements in Root Stress Predictions orEdges of Helical Gear TeethAuthors: A. Dziech and D.R. Houser

Presents an analysismethod for high power densitygear units, where load distribution is critical.Compares this method with the combination ofWellauer--Seireg moment image with twodimensional boundary element analysis, threedimensional finite element analysis, andexperimental results for tooth root bendingstresses. This new predictionmethod considers thechanges in stiffness in the normal plane and edgeeffects of helical gear teeth.ISBN: 1--55589--708--8 Pages: 9

97FTM15. Design, Generation, Stress Analysis andTest of Low--Noise, Increased Strength Face--MilledSpiral Bevel GearsAuthors: F.L. Litvin, A.G. Wang, Z. Henry,R.F. Handschuh and D.G. Lewicki

This paper discusses the design of modifiedgeometry face milled spiral bevel gears withuniform and tapered teeth, based on the applicationof specially developed machine tool settings.Optimization of the geometry to reducetransmission errors and produce the desiredcontact ellipse was developed and tested, whichreduced noise level by 18 decibels, reducedvibration 50% and increase operated torquecapacity.ISBN: 1--55589--709--6 Pages: 15

97FTMS1. Coordinate Measurement and ReverseEngineering of ZK Type Worm GearingAuthors: X. Su and D.R. Houser

A comprehensive model for the measurement,inspection, performance prediction and reverseengineering of ZK type of worm gearing isdeveloped. The measurements and the best fitprocesses both for theworm thread and for the geartooth flank are discussed in detail. A CMMmeasurement strategy free of tip compensation

which applies tomany types of tools and parts in thegear industry is proposed. A real case of ZK type ofworm gearing with the parabolic profilemodificationon the hob is studied to illustrate the reverseengineering process.ISBN: 1--55589--710--X Pages: 14

1996 PAPERS

96FTM1. A Computer Based Approach Aimed atReproducing Master Spiral Bevel and Hypoid Pinionsand GearsAuthors: C. Gosselin, Y. Shiono, T. Nonaka andA. Kubo

In the spiral bevel and hypoid gear manufacturingindustry, master pinions and gears are usuallydeveloped from initial machine settings obtainedfrom computer software, which are then developedfrom initial machine settings obtained fromcomputer software, which are then modified until asatisfactory bearing pattern is obtained, as ”thetarget tooth flank form” to compensate for heattreatment distortions and to consider lappingcannot be accounted for by existing computersoftware.

Once a satisfactory combination of master pinionand gear is obtained, their actual tooth surfacesmay not correspond to those of the theoreticalmodel. In this case, corrective machine settingscalculated from the measurement of the productiontooth flanks by a Coordinate Measuring Machineare applicable only in relation to the actual targettooth flank measurement data, as the theoreticaltooth flank definition is unknown.

This paper presents a computer based approachused to find the machine settings producing atheoretical tooth surface closest to that of ameasured surface, which incidentally can be thetarget tooth flank, in order to effectively usecorrective machine settings in reference to thetheoretical surface.ISBN: 1--55589--668--5 Pages: 10

96FTM2. The New Way of Manufacturing Bevel andHypoid Gears in a Continuous ProcessAuthor: H. Stadtfeld

Much attention has been paid to face hobbing in thelast decade. The CNC technologymade a quantumstep in this period which was beneficial especiallyfor the continuous bevel gear cutting process.Parallel to the CNC technology a new method offace hobbing was subsequently developed and isintroduced today as the different and new way offace hobbing. The basis is a new gear theoreticalapproach to design the blank geometry, the ease offand the tooth contact. The tools are different indesign than regular cutting blades and enable a



high economical procedure of roughing andfinishing in one chucking. The process kinematicwas completely redesigned, benefitting from thefree form concept of today’s cutting machines. Allthe aspects of precision, flexibility and economymake the new face hobbing also popular for thegearbox manufacturer and jobber.ISBN 1--55589--669--3 Pages: 11

96FTM3. Noise Reduction Through GeneratedEngagement Relief ModificationAuthors: W. Kieß and S. Price

For years, the international gear manufacturingindustry has been pushing machine manufacturersto develop an economical realizable tooth flankmodification that is made in contact direction, with asoft transfer from the modified to unmodifiedsections of the tooth.

Tomeet these demands, Höfler has developed, andis already implementing, Generated EngagementRelief Modifications. The tooth flank is modified atthe areas of engagement only as apposed to theentire tooth flank as is the case with conventionalmodifications. The paper discusses theadvantagesof this new technology over conventionalmodifications and discusses how to producegenerated engagement relief modifications.ISBN: 1--55589--670--7 Pages: 9

96FTM4. Traceable Calibration of Master Gears atPTBAuthor:W. Beyer

The PTB (Physikalisch--TechnischeBundesanstalt) is able to measure (calibrate)master gears for industry traceable to national gearstandards and in compliance with the InternationalSystem of Units (SI).

For this purpose primary gear standards andstandard measuring devices for the referencevalues F, Fß, Fó (total profile deviation, total helixdeviation, total cumulative pitch deviation) areavailable.

To calibrate the master gears of industry, PTB usescoordinate measuring machines which aretraceable by instrument--specific calibrationmethods. With the aid of the PTB’s primarystandards, a task specific uncertainty ofmeasurement is determined for all gearingcalibrations carried out for industry, which is takeninto account as a correction valuewhen the transfermeasurement uncertainty is stated.ISBN: 1--55589--671--5 Pages: 6

96FTM5. Differential Crowning: A New WeaponAgainst Gear Noise and Dynamic LoadAuthors: M. Wyeth and W. Rouverol

As the power density of gear sets increases, meshdeflections increase, and the variations in thosedeflections, which result primarily from meshstiffness variation, become increasingly significant.

Tominimize these undesirable effects, designers ofpower train gear pairs have traditionally specifiedvarious forms of profile modification, the mostcommon of which is tip and/or root relief.

A new system of modifications has been devisedthat substantially eliminates mesh stiffnessvariations throughout the entire engagement angleregardless of what torque load is being transmitted.By substantially eliminating gear noise anddynamic increment, the new modifications make itpossible to replace costly helical gear sets withbetter performing spur sets in many applications.This new system of modifications is described andconfirmatory test results are reported.ISBN: 1--55589--672--3 Pages: 4

96FTM6. The F--22 AMAD Gear Drive Optimization ofResonance Characteristics by Detuning, CoulombDamping & Damped Force Response AnalysesAuthor: R. Drago, F. Brown, A. Sane, and D. Stremick

Finite element analyses were performed duringdesign and development of the F22 AMAD gearboxto ensure a design free of damaging resonantresponses within its operating speed range. Ideally,design with respect to resonance characteristicswould have no natural frequencies within theoperating speed range. However, the wide speedrange (from 1445 to 17931 rpm) combined with theweight and geometric constraints imposed by theapplication (the F--22 is an advanced technology,next generation, fighter aircraft) made it impossibleto attain this goal directly in the F--22 AMADdesign.

This paper discusses the overall analyticalapproach, analytical methods and evaluation ofgear response to achieve acceptable accessorygear designs. Design modifications, includingdevelopments in the modeling techniques requiredto accommodate the unique characteristics of theserelatively small (compared to the usual helicoptermain power gear) gears are also discussed. Testand analytical results are also presented andcompared.ISBN: 1--55589--673--1 Pages: 16



96FTM7. Dynamic Distribution of Load and Stress onExternal Involute GearingsAuthors: J. Börner and D. Houser

The influence of additional dynamic loads on thedistributions of load, flank pressure and tooth rootstress are shown. The additional dynamic loadsexcited by the variations of mesh stiffness andinfluenced by tooth deviations and modificationsare calculated and used as input for the calculationof the distributions of load and stresses in the planeof action. Very efficient calculations are obtained byusing specially developed calculation algorithms.Anextensive graphic presentation of the calculationresults is included. The same connection of thecalculation of load distributionwith the calculation ofdynamic loads is also possible in principle on thebasis of very similar programs (LDP & DYTEM)developed at the Ohio State University.

The calculation results are compared with dynamicloads and transmission errors measured on testrigs in the gear lab at the Ohio State University.ISBN: 1--55589--674--X Pages: 12

96FTM8. Thermal Rating of Gear Drives BalanceBetween Power Loss and Heat DissipationAuthors: B. Höhn, K. Michaelis, and T. Vollmer

From the balance between the generated heat in agear box and the dissipated heat from the gear casesurface the mean value for the expected lubricanttemperature can be evaluated. The maximum oiltemperature in a splash lubricated enclosed geardrive limits the transmittable power. High oiltemperatures influence wear, scuffing, micropittingand pitting load capacity of the gears as well as thegear oils’ service life.

Experimental investigations of no--load and loaddependent gear losses in cylindrical and bevelgears as a function of lubricant type and viscosity,load, speed and temperature are reported. Themean value for the coefficient of friction in a gearmesh is evaluated and compared tomeasurementsin twin disk machines. A rating method for gearmesh power loss is derived.

Investigations, using model and actual gear boxes,show the influence of radiation, free and forcedconnection as well as conduction to the foundationon the heat dissipation from the gear case surface.The influence of design, size, air velocity, surfacefinish of the housing, etc., is reported.

The results of such investigations together withaccepted rating methods for bearing and sealpower loss are introduced into a calculationmethodfor the evaluation of the oil temperature in the sumpof a gear box. In sample calculations the

possibilities as well as the limits of this thermalrating method is shown.ISBN: 1--55589--675--8 Pages: 12

96FTM9. The Development of a Practical ThermalRating Method for Enclosed Gear DrivesAuthor: A. Phillips

This thermal rating method balances the sum of theload--independent losses and the load--dependentlosses against the heat dissipation capability of thegear case. Empirical factors are determined whichcalibrate the calculations against the test results forassembled gear reducers. The results of thiscalculation method are compared to the test resultsfrom 251 gear reducer tests. In addition, sincelosses are calculated, this method can be used tocalculate the efficiency of the gear drive for theoperating conditions.ISBN: 1--55589--676--6 Pages: 8

96FTM10. Scuffing Resistance of VehicleTransmission GearsAuthors: F. Joachim and H. Collenberg

In many transmission types, the lubricant fulfillsother functions apart from lubricating the gearing,for example in friction elements (synchronizer unit,clutch) in vehicle transmissions, or as a hydraulicfluid (torque converter, retarder, steering system).The modern trends are now high contact ratiogearing aswell as the use of low viscosity lubricantsto reduce churning losses. Therefore, at the geardesign and lubricant additive stages, compromisesare now necessary which require the most preciseinformation possible on scuffing resistance of thegearing and lubricant.

It will be demonstrated that the normal testprocedures for determining scuffing resistance arenot suitable for lubricant classification for vehicletransmissions (GL 4 and GL 5). By reducing thetooth width as well as doubling the speed, thescuffing test to DIN 51354 standards was increasedin severity to such an extent, that the parametersnecessary for transmission dimensioning could bedetermined for even higher scuffing resistant oils.The oil data necessary for sufficient scuffingresistance will be shown for different transmissiondesign types.

A process is presented, in which scuffing resistanceis calculated for every point on the tooth flank,based on the ”flash temperature method”, andtaking all variations and corrections into account. Itwill be demonstrated with practical examples, that,as early as the design stage, this method can beused to detect flank areas at risk, and to eliminatethem with a specific correction design.ISBN: 1--55589--677--4 Pages: 8



96FTM11. DIN 3996: A New Standard for Calculatingthe Load Capacity of Worm GearsAuthors: B Höhn and K. Steingröver

During the last years the load capacity of wormgears was raised about 30%. The reasons for thisare the introduction of synthetic oils, optimization ofthe worm gear geometry and manufacturingimprovements. The forthcoming new standard DIN3996 ”Calculation of load capacity of cylindricalworm gear pairs” takes into account thesedevelopments. This standard contains the followingload capacity limits: wear, pitting, tooth breakage,temperature and worm deflection. Also, efficiencywas taken into consideration. In most cases thecalculation methods are based on results of recentinvestigations,whichwere performedonwormgeartest rigs at the FZG. In the case of wear, pitting andtooth breakage test results and their influence onDIN 3996 are shown.

The calculation method for wear resistance isbased on the fact that the wear intensity of amaterial/lubricant combination is a function of thelubricant film thickness and the lubricant structure.The main influence parameter on pitting resistanceis the Hertzian stress. For tooth root strength thecalculation method is based on a nominal shearstress theory, in case of worm deflection on thedeflection curve of a cylindrical shaft.

The application of this new standard for gears inpractice is discussed by recalculating someexamples.ISBN: 1--55589--678--2 Pages: 14

96FTM12. An Investigation of Globoidal WormgearDrivesAuthor: N. Chen

This paper investigates the following presentgloboidal wormgear drives: (1) original andmodified Hindley wormgear drives; (2) Wildhaberwormgear drive with inclined plane teeth ofwormgear; (3) inclined plane and cone envelopinggloboidal wormgear drives; (4) plane, cone andinverted cone enveloping globoidal wormgeardrives based on Sakai’s theory. Meanwhile, a newapproach for generation of Hindley wormgearing,and plane and cone enveloping globoidalwormgear drives is developed in this paper. Contactlines, dual and single contact ratios, relativecurvature radii, meshing angles between tangentsof contact lines and relative velocities, and slidingratios of wormgear tooth surfaces of the abovegloboidal wormgear drives are studied bycomputerized simulation for numerical examples.ISBN: 1--55589--679--0 Pages: 15

1995 PAPERS

95FTM1. Detection of Hidden RunoutAuthors: Robert Smith, Irving Laskin and Dan Bailey

There is a gear geometry variation, called “hiddenrunout”, which resembles runout in it’s effect ontransmission error and the resulting vibration, noiseand positional accuracy of a drive train, but which isnot revealed in the standard runout measurementsby ball--check or double flank composite testing.This paper describes this often unrecognizedinspection methods than can be used to illustratethe manufacturing and inspection issues.ISBN: 1--55589--649--9 Pages: 10

95FTM2. Separation of Runout from ElementalInspection DataAuthors: Irving Laskin and Ed Lawson

Runout due to eccentricity influences index, pitchand profile inspection data for spur and helical andprofile inspection data for spur and helical gearsand tooth alignment inspection data for helicalgears. This paper reviews the numerical procedureused with index and pitch data to determine themagnitude and direction of the runout. It re--plotsthe inspection data with runout influence removed.This new numerical procedure is effective in thepresence of such tooth geometry features as slopevariation (e.g., pressure angle variation in profileand helix angle variation in tooth alignment),non--linearity (e.g., tip relief in profile and crown intooth alignment), and waviness. The numericalprocedure is shown for index, pitch and profileinspection data taken from a test gear (also seeAGMA 93FTM6).ISBN: 1--55589--650--2 Pages: 15

95FTM3. The Effect of Manufacturing Errors on thePredicted Dynamic Factors of Spur GearsAuthors: Jonny Harianto and Donald Houser

This paper studies the effect of manufacturingerrors on predicted dynamic factors of spur gears.Three dynamic factors are defined and studied:dynamic load factors, dynamic tooth force factors,and dynamic bending moment factors. Threecomputer programs for predicting dynamics arediscussed; a forced vibration analysis using sixdegrees of freedom, a multi--degree DynamicTransmission Error Program (DYTEM) using a sixdegree of freedom model, and a Geared RotorDynamics Program that uses a finite elementmethod. Using experimental data provided byNational Aeronautics and Space Administration theDYTEM program is used for dynamic factorsprediction. The effects of AGMA 10, 12 and 14profile tolerances are shown.ISBN: 1--55589--651--0 Pages: 12



95FTM4. An Experimental Test Stand to MeasureLoaded Transmission Error in Fine--Pitch PlasticGearsAuthors: Sivakumar Sundaresan, David Castor andKenneth Price

This paper describes an experimental test stand tomeasure transmission error in fine--pitch gears. Itcovers the importance of transmission error controlin office equipment. Transmission error iscomputed by measuring the phase differencebetween the driver shaft and the driven shaft usingoptical encoders. The test stand has a variableoperating center distance and shaft alignment inboth parallel and skew directions. Results show theeffects of gear elemental errors, transmitted load,and shaft misalignment on transmission error infine--pitch plastic gears.ISBN: 1--55589--652--9 Pages: 9

95FTM5. The Surface Fatigue Life of ContourInduction Hardened AISI 1552 GearsAuthors: Dennis Townsend, Alan Turza, and MikeChaplin

Two groups of spur gears manufactured from twodifferent materials and heat treatment wereendurance tested for surface fatigue life. One groupwasmanufactured fromAISI 1552 andwas finishedground then dual frequency contour hardened andthe second was CEVM AISI 9310 carburizedhardened then finished ground. The gear pitchdiameterwas 8.89 cm (3.5 in.). Test conditionswereat maximum Hertz stress of 1.71 GPa (248 ksi) anda speed of 10 000 RPM. The lubricant used for thetests was a synthetic paraffinic oil with an additivepackage. The results showed that surface fatiguelife of the contour hardened AISI 1552 was 1.7times that of AISI 9310 gears.ISBN: 1--55589--654--5 Pages: 9

95FTM6. Development of an Epicyclic Gearbox forReduced Sub--Synchronous Vibrations in GasTurbo--Generator SetsAuthor: A. Rakhit

In star epicyclic gearboxes, low frequencysubsynchronous (below turbine speed) vibrationscan be predominant. Turbo--generator gear unittesting shows that these low frequency vibrationsmay occur even when the rotating components arebalanced precisely. In star epicyclic gearboxes ofStoeckicht design, splined couplings between thering gears and output shaft are used to float the ringgears for load sharing. The sub--synchronousvibrations that arise from such components aretransmitted along with the mesh frequencyvibrations to the turbine rotor bearings. When theamplitude levels of these vibrations and theirharmonics exceed a certain limit, the life of thesebearings is significantly reduced. To reduce the

vibrations from the dynamic eccentricity of ringgears and splined couplings the design is changed.ISBN: 1--55589--655--3 Pages: 7

95FTM7. Experimental and Analytical Assessment ofthe Thermal Behavior of Spiral Bevel GearsAuthors: Robert Handschuh and Thomas Kicher

An experimental and analytical study of spiral bevelgears operating in an aerospace environment hasbeen performed. Tests were conducted within aclosed loop test stand at 537 kW (720 hp) and14400 rpm. The effects of various operatingconditions on spiral bevel gear steady state andtransient temperature are presented. Athree--dimensional analysis of the thermal behaviorwas conducted using a nonlinear finite elementanalysis computer code. The analysis wascompared to the experimental results. The resultsagreed within 10 percent.ISBN: 1--55589--656--1 Pages: 19

95FTM8. Miner’s Rule -- A More Definitive ApproachAuthor: Al Meyer

ANSI/AGMA 2001--B88, Appendix B presents thefundamentalmethod for evaluatingMiner’sRule. Toanalyze the load spectrum, stress values arecalculated for a given load and then modified using“K” or “C” factors. When computing the stresses forother points, the stress values are usually simplyratioed rather than recomputing the stresses usingnew “K” and “C” for each point. In this paper, theeffect of using a dynamic and load distribution factorfor each load point is evaluated and compared withthe simple ratioing approach. Comparisons aremade for various applications.ISBN: 1--55589--657--X Pages: 6

95FTM9. Bending and Compressive Stress Analysisof External Helical Gearsets of Varying Contact RatiosAuthor: David Wenthen

In an attempt to better understand how thedurability of a helical gearset is affected by changesin profile (mP) and face contact ratio (mF), ananalytical investigation was done in which mP wasvaried. Thirty--two combinations were studied intotal. The gears were modeled using the hybridfinite element computational method ContactAnalysis Programming Package (CAPP), ofAdvanced Numerical Solutions. The results of thisanalysis suggest that for a given level of facecontact ratio, an advantage in bending andcompressive stress exists at the mP=2.1 level overall of the others considered. Increasing bothmP andmF had the effect of smoothing out the bending andcompressive stresses when viewed as a function ofroll angle.ISBN: 1--55589--658--8 Pages: 10



95FTM10. Efficiency of High Contact Ratio PlanetaryGear TrainsAuthor: John Colbourne

A new method is described for calculating theefficiency of planetary gear trains. An example,showing how themethod can be applied to the caseof a fixed differential gear train is given.ISBN: 1--55589--659--6 Pages: 8

95FTM11. Feature--Based Definition of Bevel GearsAuthor: Robert E. Brown

The complex shape of a bevel gear tooth surfacemust be defined mathematically for the CMM, butthe mathematical definition tends to be difficult fordirect use in gear design and manufacture. Themathematical definition may be condensed into a“feature--based” definition which is moreconvenient for gear design and manufacture. Thefeature--based definition may easily be describedon the engineering drawings and toleranced.Development and application of the feature--baseddefinition is described.ISBN: 1--55589--660--X Pages: 10

95FTM12. Flank Modifications in Bevel Gears Using aUniversal Motion ConceptAuthor: Hermann Stadtfeld

The use of free form bevel gear generators waslimited by the processes currently available to cutbevel and hypoid gears with face cutter heads.Since a free form cutting or grinding machine hasthree rotational and three linear freedoms it ispossible to perform all possible relativemovementsbetween the cutter and the work during thegeneration process. The universal motion conceptis applied to axes of the basic gear generationmodel only. It allows each of them to change thesetting during the generation process according ahigher order function. This approach enables a freeform gear machine to produce an entire variety ofmodifications to the flank surfaces.ISBN: 1--55589--661--8 Pages: 10

95FTM13. Powder Metallurgy Gears -- ExpandingOpportunitiesAuthors: W. Brian James and Howard Sanderow

Powder metallurgy (P/M) is a precision metalforming technology for producing simple orcomplex parts to net shape or near net shape withlittle, if any machining. The mechanical propertiesof P/M materials are a direct function of density,composition, and microstructure. A systemsapproach to material and process selection permitsthe development of amicrostructure suitable for theintended application. The technology as related togear design and applications is reviewed. Newmaterials and process technologies are reviewedfor the comparability of P/M steel gears with cast orwrought steel. The strengths and weaknesses of

the powder metallurgy process are examined,along with the challenges facing the industry.ISBN: 1--55589--662--6 Pages: 12

95FTM14.Study of Effect ofMachining Parameters onPerformance of Worm GearsAuthors: Anand Narayan, Donald Houser andSandeep Vijayakar

This paper studies the effect of machiningparameters on the performance of worm gearsusing a special purpose finite element technique.Algorithms are presented to determine the wormand gear geometries by simulating the grindingaction of the grindingwheel and cutting action of thehob. Results are presented delineating the effect ofmachining parameter such as the hoboversize, hobswivel angle, profile modification etc., onperformance parameters such as the contactlocation and size, stresses and transmission errorof worm gears.ISBN: 1--55589--663--4 Pages: 9

95FTMS1. Determination of the Dynamic GearMeshing Stiffness of an Acetal CopolymerAuthor: Connie P. Marchek

The objective of this work was to determine thedynamic gear meshing stiffness of an acetalcopolymer (plastic). The torsional resonant speedof an operating gear pair was determinedexperimentally. Using the theoretical model, it waspossible to determine the dynamic gear meshingstiffness from the experimental resonant speed andcompare it to the values calculated from availableempirical formulas.ISBN: 1--55589--653--7 Pages: 34

1994 PAPERS

94FTM1. Fatigue Analysis of Shafts for MarineGearboxesAuthor: E.William Jones, Anying Shen and Robert E.Brown

Designs are presented for the design of shafts formarine gearboxes, whichmay include the effects oftorsional vibration. The influence of the vibratorytorque on the values of shaft diameter and safetyfactor is discussed. Use of the Finite ElementMethod to evaluate unknown stress concentrationfactors is illustrated. A program for the design ofshafts, which are subjected to fatigue, has beendeveloped.ISBN: 1--55589--635--9 Pages: 14



94FTM2. An Analytical Method for the Calculation ofthe Efficiency of Planetary GearsAuthor: Michel Pasquier and Pierre Foucher

Presents a synthesis of an analytical method for thecalculation of the efficiency of simple or compoundplanetary gear trains based on fundamentalformulae. It is intended to improve the accuracy ofthe rating of the efficiency of planetary gears to beincluded in a calculation of the thermal capacity.ISBN: 1--55589--636--7 Pages: 6

94FTM3. Application of Ausforming to Gear Finishing-- Process, Design and Manufacturability IssuesAuthor: N. Sonti, A.J. Lemanski and S.B. Rao

Discusses the potential applications of ausformfinishing of spur and helical gears, includingprocess design and related manufacturabilityissues. Examples are presented describing theflexible tooling arrangements possible to process avariety of gear geometries. Machine design,controls and material handling features of theproduction--capable double die gear ausformfinishing machine currently being built are brieflydescribed.ISBN: 1--55589--637--5 Pages: 7

94FTM4. Load Carrying Capacity of Nitrided GearsAuthor: L. Albertin, R.L. Frolich, H.Winter, B.--R. Höhnand K. Michaelis

Investigates the pitting and bending strength of gasnitrided steel gearsmadeofmodified 39CrMoV13.9(a 3% CrMoV type alloy). Characteristics of thecompound layer and the diffusion zone areexamined. Residual stresses in the nitrided caseare shown after long nitriding times. For bendingstrength, additional damage line investigationswere performed. The load carrying capacity of themodified 39CrMoV13.9 steel is discussed andcompared with other carburized, gas, and ionnitrided gears.ISBN: 1--55589--638--3 Pages: 10

94FTM5. A Special CVT for a New Power TrainConceptAuthor: B.--R. Höhn and B. Pinnekamp

Describes the Autark Hybrid power train vehiclecapable of inner city drivingwith zero emissions andalso suited to long distance driving. Combinesinternal combustion engine (IC engine) and smallelectric engine. Enables significant reductions offuel consumption at constant power by avoiding thepartial load operation areas with high specific fuelconsumption and reducing the engine speed. Thenew power transmission has a wide range andcontinuously variable ratio. The requirements,principle function and the progress in developmentof the i2--CVT is described, as well as theapplication in the hybrid power train.ISBN: 1--55589--639--1 Pages: 7

94FTM6. A Boundary Element Procedure forPredicting Helical Gear Root Stresses and LoadDistribution FactorsAuthor: M. L. Clapper and D. Houser

Explores a method to accurately predict gear rootstress for parallel axis gears using a combination ofthree analysis techniques: boundary elements,elastic body contact analysis, and themoment--image method. The three techniques arecombined to predict the stresses through the meshcycle for both spur and helical gears. Predictionsare compared with strain gage results and finiteelementmodeling. Results present the prediction ofload distribution factors as a function ofmisalignment, comparing with AGMA factors.ISBN: 1--55589--640--5 Pages: 8

94FTM7. Allowable Surface Compressive Stresses ofGear Teeth Made of Cast Iron, Tempered CarbonSteels and Tempered Alloy SteelsAuthor: Hirofumi Kotorii

Load endurance tests were conducted to obtainallowable surface compressive stresses for variousmaterials: spheric graphite cast iron, G5502;carbon steel, G4051 and steel G4502. Loadendurance tests were conducted, and dataconcerning tooth damage was accumulated. Theresults of these tests and comparison of thedurability of the materials are presented.ISBN: 1--55589--619--7 Pages: 13

94FTM8. Reference Point, Mesh Stiffness andDynamic Behavior of Solid, Semi--Solid andThin--Rimmed Spur GearsAuthor: Jean Brousseau, Claude Gosselin and LouisClotier

Manymodels for predicting the dynamic behavior ofgears do not take into account the blank flexibilityand modes of vibration. The paper presents resultsfor solid, semi--solid and thin rimmed spur gears.The analysis is made for the natural frequencies,when finite element models of meshing spur gearsare referenced. Results show that a reference pointinside the gear blank yields excellent correlationbetween the natural frequencies extracted from theRD--FT and F.E.A. models.ISBN: 1--55589--643--X Pages: 8

94FTM9. Analytical and Experimental VibrationAnalysis of a Damaged GearAuthor: F. Choy, M. Braun, and V. Polyshchuk, J.Zakrajsek, D. Townsend and R. Handschuh

Develops a comprehensive analytical procedure forpredicting faults in gear transmission systems. Amodel is developed to simulate the effects of pittingand wear on the vibration signal under operatingconditions. The model uses gear mesh stiffnesschanges to simulate the effects of gear tooth faults.The predicted results were compared withexperimental results obtained from a spiral bevelgear fatigue test. The Wigner--Ville Distribution



(WVD) method applied to the results werecompared to other fault detection techniques toverify theWVD’s ability to detect the pitting damageand determine relative performance.ISBN: 1--55589--644--8 Pages: 8

94FTM10. Computerized Design and Generation ofLow--Noise Gears With Localized Bearing ContactAuthor: F. Litvin, N. Chen, J. Chen and J. Lu

Presents results of research projects directed atreduction of noise caused by misalignment ofvarious gear drives: double--circular arc helicalgears, modified involute helical gears, face--milledspiral bevel gears and face--milled formate cuthypoid gears. A parabolic function of transmissionerrors was developed and successfully tested for aset of spiral bevel gears. The noise was reduced12--18 decibels. The effectiveness of the proposedapproach was investigated by developed TCA(Tooth Contact Analysis) programs. Manufacturingof helical gears with new topology by hobs andgrinding worms was investigated.ISBN: 1--55589--645--6 Pages: 10

94FTM11.Development of TransferGearNoise of 4X4Transmission for Recreational VehiclesAuthor: Yoshiki Kawasaki

Developed new methods to reduce transfer gearnoise, which consisted of gear developmentsmaking use of tooth contact patterns, a newregrinding system for shaving cutters, qualitycontrol, improvement activities for gear productionprocesses, etc. Succeeded in reduction in the rejectrate from 4.5% to 0.5% and improving the transfergear noise rating from 4.0--6.0 to 8.0--10.0.ISBN: 1--55589--646--4 Pages: 6

94FTMS1.Computer--AidedNumerical Determinationof Hofer, Lewis, Niemann and Colbourne PointsAuthor: Chang H. Park

In rating the bending strength of gear teeth, thecritical point located where the fracture occursmustbe determined. Hofer, Lewis, Niemann andColbourne use methods to find the pointapproximately, in which numerical iteration isneeded to solve nonlinear one--variable equationsto find their critical points. This paper presentsequations expressed easily and in a similar way forfinding the critical point as well as the general geartooth profile equations derived by a vector analysismethod. Position comparison of points wasachieved with computer--aided graphical andnumerical output.ISBN: 1--55589--642--1 Pages: 17

1993 PAPERS

93FTM1. Undercutting in Worms and Worm--GearsAuthor: John R. Colbourne

Develops an equation for worms that can be used toensure that there is no undercutting. Explains thatfor wormgears, the possibility of undercuttingdepends onmany variables, and no simple criterionhas been found.Describes procedures for checkingfor undercutting and other potential problems, suchas interference or non--conjugate contact.ISBN: 1--55589--594--8 Pages: 10

93FTM2. Topological Tolerancing of Worm--GearTooth SurfacesAuthor: Vadim Kin

Proposes a method for determining surfacedeviations of the wormgear tooth that result fromcutting edge deviations of the hob used to cut thegear. Demonstrates how to obtain tolerance tablesfor wormgear tooth profiles from the tolerancetables for the corresponding worm threads and hobcutting edges. (Such tables can bean important firststep towards a wormgear inspection standard.)ISBN: 1--55589--595--6 Pages: 6

93FTM3. A Rayleigh--Ritz Approach to DetermineCompliance and Root Stresses in Spiral Bevel GearsUsing Shell TheoryAuthors: Sathya Vaidyanthan, Henry Busby andDonald Houser

Proposes a mathematical model for predictingdeflections and root stresses in spiral bevel gears.Shows a shell model is more representative of thespiral bevel tooth geometry as compared to a beamor plate model. Integrates the compliancecomputations based on the shellmodel into existingcomputer codes for bevel gear design to determinethe load distribution, transmission error, and rootstresses on a personal computer. Concludes thatcomputationally, this procedure is much moreefficient than the finite element method.ISBN: 1--55589--596--4 Pages: 9

93FTM4. Stress Analysis of Spiral Bevel Gears: ANovel Approach to Tooth ModellingAuthors: Ch. Rama Mohana Rao and G.Muthuveerappan

Proposes a geometrical approach for generatingtooth surface coordinates of spiral bevel gears.Demonstrates how this versatile can be adapted,with appropriate modifications, to any type of spiralbevel gear. Analyzes various types of spiral bevelgears (logarithms, circular cut and zerol types).Offers a new procedure, using thethree--dimensional finite element method, fortheoretical determination of exact tooth load



contact line on the surface of the spiral bevel geartooth.ISBN: 1--55589--597--2 Pages: 14

93FTM5. Optimal Gear Design for Equal StrengthTeeth Using Addendum Modification CoefficientsAuthor: C. H. Suh

Defines the addendum modification coefficient(shift factor) and explains it in terms of gear designterminology. Shows the derivation of two types ofhelical gear design equations, one with the truegenerating shift factor, and the other with anaddendum modification factor. Reviews acantilever beam equation used to design equalbending strength teeth. Presents a design method,alongwith numerical examples, to synthesize equalstrength teeth between mating a pinion and gearthat may have different material properties.ISBN: 1--55589--598--0 Pages: 12

93FTM6. Effect of Radial Runout on ElementMeasurementsAuthors: I. Laskin, R. E. Smith and E. Lawson

Proposes that radial runout in a gear can contributesubstantially to measured values of variations inprofile, pitch and index, and in helical gears, to toothalignment (lead) variations. For each variation,gives the equation that relates the measured valueto the radial runout in an otherwise ideal gear.Demonstrates the relationship by comparing theresult of actual measurement with the calculatedvalue. Describes how the equations can: aid theinterpretation of gear inspection data and explaindifferences between measurement methods.ISBN: 1--55589--599--9 Pages: 16

93FTM7. New Developments in Design,Manufacturing and Applications of Cylkro-- (Face)GearsAuthors: Guus Basstein and Anne Sijtstra

Calculates and optimizes the geometry of bothCylkro--gear and pinion, concerning contact ratio,lines of action and contact. Using F.E.M. analysisand a load distribution program, adapts the DIN3990 (ISO/DIS 6336) calculation methods (forbending strength and pitting resistance) to includeCylkro--gear calculations. Tests this method on aback test bench.ISBN: 1--55589--619--7 Pages: 12

93FTM8. Single Flank Testing and Structure--BornNoise AnalysisAuthor: Hermann J. Stadtfeld

Proposes that testing the running behavior of aninstallation--ready gearsetmust take place on beveland hypoid gear testers. Describes single flankgeneration testing and structure--borne noiseanalysis of gear pairs, based on a highly modernreal-time analysis device for which software was

specially developed for the transmission testing ofgearsets. Explains the newpossibilities and offers atrouble shooting example.ISBN: 1--55589--620--0 Pages: 11

93FTM9. Gear Tooth Bending Fatigue CrackDetection by Acoustic Emissions and ToothCompliance MeasurementsAuthors: Jeffrey Wheitner, Donald Houser and CraigBlazakis

Presents the results of gear tooth bending fatiguetests. Explores whether the combination of twotypes of measurement -- acoustic emissions andtooth compliance -- can help detect cracks early on(single tooth bending fatigue tests for severaldifferent gear materials were performed). Uses thetwo crack detection methods to describe fatiguetest characteristics, such as the probable time ofcrack initiation, rate of crack propagation, andpercent of total fatigue life spent in crackpropagation phase. Presents the effects ofmaterials and processing. Shows how crackdetection can reveal the results of surface finish onfatigue.ISBN: 1--55589--621--9 Pages: 7

93FTM10.High Speed, Heavily Loaded and PrecisionAircraft TypeEpicyclic Gear SystemDynamic AnalysisbyUsing AGMAGear DesignGuidelines Enhanced byExact Definition of Dynamic LoadsAuthors: K. Buyukataman and K. Kazerounian

Dynamic analysis of reliable, lightweight, highspeed and high power density epicyclic gearsrequires special effort to predict their maximumpower transmitting capacity. Focuses onsingle--stage epicyclic gears of this category.Presents an overview of key design considerationswith proper application of AGMA standards. Uses astate--of--the--art, elastodynamic simulation thatresponds to input data much as afully--instrumented test cell. Demonstrates that anepicyclic gear system can be a fully reliable aircraftpropulsion component.ISBN: 1--55589--622--7 Pages: 19

93FTM11. The Relative Noise Levels of Parallel AxisGearsSetswithVariousContact ratios andGear ToothFormsAuthors: R. J. Drago, J. W. Lenski , R. H. Spencer, M.Valco and F. Oswald

Describes the design and testing of nine sets ofgears which are as identical as possible except fortheir basic tooth geometry. Measures noise atvarious combinations of load and speed for eachgear set in order to make direct comparisons.Analyzes resultant data, including that geargeometry is an important parameter for designinglow weight, high reliability gear systems for aircraft.ISBN: 1--55589--623--5 Pages15



93FTM12. The Generation of Precision Spur GearsThrough Wire Electrical Discharge MachiningAuthors: Roderick Kleiss, Jack Kleiss, and ScottHoffmann

Maximizes the accuracy and repeatability of wireElectrical Discharge Machines (EDM) throughfixturing and controlled cutting methods. Alsooptimizes mathematical algorithms for the cuttingpath. Presents results slowing the verifiedgeneration of precise spur gears in pitches rangingfrom 5 to 41 DP. Demonstrates the advantage ofthis method, including short lead times (withaccuracy approaching form ground gears) at acompetitive cost. Concludes this method is suitablefor producing small to medium lots of accurate spurgears in any electrically conductive material.ISBN: 1--55589--624--3 Pages: 11

93FTM13. CAGE -- Computer Aided EngineeringSoftwareAuthor: Enrico Esposito

Describes CAGE, a UNIX--based set of computerprograms that uses an industry standard,windows--based graphical user interface forefficient and logical gear design and analysis.Includes manufacturing data and inspection data.Highlights special features, including: file folderscontaining gear--set development information,multi--window display and processing, internationallanguage support, connections to manufacturingand inspectionmachines, and a field, screen andanon--line help facility and user guide.ISBN: 1--55589--625--1 Pages: 14

93FTMS1. Spur Gear Bending Strength GeometryFactors: A Comparison of AGMA and ISO MethodsAuthor: E. R. teRaa

Presents the necessity of comparing ISO andAGMA power rating standards. Gives the results ofusing computer software to compare the behaviorof the bending geometry factor (J--factor) values for135 spur--gear meshes. Shows that differencesexist between the results given by ISO and AGMAstandards, both in the geometry factor values andthe effects of profile shift (which is of particularinterest).ISBN: 1--55589--626--X Pages: 8

1992 PAPERS

92FTM1. Experimental Characterization of SurfaceDurability of Materials for Worm GearsAuthor: M. Octrue and M. Guingand

Presents the methodology used for testingmaterials with a worm gear set--up and with adisc--roller machine. Discusses and analyzesseveral experimental results. Draws a correlationbetween metallurgical analyses of the structure of

bronzes and experimental observations ofsubsurface cracks. Explains specific method of formeasuring wear and describes results.ISBN: 1--55589--581--6 Pages: 7

92FTM2. Face Gear Drives: Design, Analysis, andTesting for Helicopter Transmission ApplicationsAuthors: F. Litvin, J. Wang, R. Bossler, Y. Chen, G.Heath and D. Lewicki

Examines a variety of topics including toothgeneration, limiting inner and outer radii, toothcontact analysis, contact ratio, gear eccentricity,grinding and structural stiffness. Shows that theface gear drive is relatively insensitive to gearmisalignmentwith respect to transmission error, butthat tooth contact is affected by misalignment.Explores a method of localizing the bearing contactto permit operation with misalignment. Investigatestwo new methods for grinding face gear toothsurfaces.ISBN: 1--55589--582--4 Pages: 11

92FTM3. Reduced Fuel Consumption and EmissionsDue to Better Integration of Engine and TransmissionAuthor: B. Höhn

Discusses how better integration of engine andtransmission can help reduce fuel consumption andemissions from combustion. Demonstrates thatgears with a wider ratio range offer threeadvantages: 1) reduced engine speed; 2) improvedacceleration without enlarging the engine; 3)optimal configuration for a new hybrid drive line forpassenger cars.ISBN: 1--55589--583--2 Pages: 7

92FTM4. The Design, Development and Manufactureof Advanced Technology Gearing for Hot Strip RollingMill ApplicationsAuthors: R. Drago and L. Scott

Describes the initiation and process of a programwhich addresses very large gears (approaching200 inches in diameter) and a number of pinionconfigurations. Configurations range from long,integral, solid on--shaft designs to multiple shellpinion designs. Most are carburized and hardfinished; all meet or exceed AGMA Quality Class10. Presents the general design procedures andoverall implementation of the design andmanufacturing program. Describes the results interms of improved mill gear system experience.ISBN: 1--55589--584--0 Pages: 21

92FTM5. Main Advantages of Non--Involute SpurGearsAuthor: J. Hlebanja

Identifies scuffing as the main cause for limitinggear durability in highly loaded and high speedworking gears. Notes that the principal way to avoidscuffing of tooth flanks is to apply an oil film ofsufficient thickness between the mating flanks.Asserts that the shape of the flanks determine thecurvature radius and sliding velocity. In turn, the



curvature radius and sliding velocity decisivelyaffect the forming of the oil film between flanks.Proposes that by shaping the line of action properlyresults in better gear flank shapes and improveddurability.ISBN: 1--555889--585--9 Pages: 6

92FTM6.Comparison of Carburized Gear Materials inPittingAuthors: L. Faure, J. Vasseur, and C. Lefleche

Compares the pitting resistance of five differentsteels commonly used for case carburized gears.Bases the comparison on the test results obtainedon the CETIM gear benches. Describes how thetests were set up the test results interpreted foreach steel. Draws representative curves of pittingperformance. Describes, in detail, the appearanceof these curves and all the deviations encountered.ISBN: 1--55589--586--7 Pages: 7

92FTM7. Differences in the Local Stress of the GearTooth Root Based on Hobbing Cutters and PinionCuttersAuthors: H. Linke and J. Börner

Proposes that use of a pinion--shaped cutter,instead of a hob, causes differences in tooth rootgeometry. Asserts that these differences lead todifferent stress concentrations in the tooth root.Uses the Singularity Method for both types ofproduct to calculate, exactly, tooth root stresses.Discusses differences in both approaches. Provesthat it is possible to calculate stress concentrationusing the stress parameter 2ρFn/sFn (on 30°tangent).ISBN: 1--55589--587--5 Pages: 10

92FTM8. The Role of Reliability for Bearings andGearsAuthor: C. Moyer

Details the experimental basis for the relationshipbetween stress (load), life and reliability forbearings and gears considering the similarity anddifferences of their respective systems. Addressesthe role of stress level and life scatter in terms of theWeibull distribution. Develops the background andequations to calculate reliability factors, as includedin both bearing and gear standards.ISBN: 1--55589--588--3 Pages: 7

92FTM9. Representative Form Accuracy of GearTooth Flanks on the Prediction of Vibration and Noiseof Power TransmissionAuthors: A. Kubo, T. Nonaka, N. Kato, S. Kato, and T.Ohmori

Begins with the premise that gear noise andvibration are troublesome problems in powertransmission systems. Reviews recent researchthat shows accuracy in three dimensional toothflank form, usually represented by tooth form andtooth lead form, are important factors in noise andvibration. Discusses investigation into what form

accuracy of gear tooth flank has a good correlationwith gear vibration andnoise,when the scattering ofaccuracy in tooth flank form cannot be avoided.ISBN: 1--55589--589--1 Pages: 6

92FTM10. The Influence of the Kinematical MotionError on the LoadedTransmissionError of Spiral BevelGearsAuthors: C. Gosselin, L. Cloutier, and Q. Nguyen

Presents the basis of a Loaded Tooth ContactAnalysis program predicting the motion error ofspiral bevel gear sets under load. Shows amplitudeand shape of the unloaded motion error curve canaffect the kinematical behavior under load.Evaluates the effects of tooth composite deflection,tooth contact deformation, and initial profileseparation due to motion error.ISBN: 1--55589--590--5 Pages: 11

92FTM11. New Findings on the Loading of PlasticSpur Gear TeethAuthors: J. Bessette and H. Yelle

Proposes that tooth breakage at the tip of plasticgears is the result of interference on the back of thetooth. Provides verification of this interferencethrough experiments. Explains how CAD softwareand plastic gear calculating software can simulatethe kinematics of a gear pair to predict and localizeinterference on the back of the tooth.ISBN: 1--55589--591--5 Pages: 8

92FTM12. Noise Reduction in a Plastic and PowderMetal Gear Set Through Control of “Mean InvoluteSlope”Authors: R. Smith and I. Laskin

Recognizes mismatched involute profiles as acause of tooth meshing noise. Traces a noisereduction process applied to a consumer productwith a noisy gearset. (Gearset consists of a powdermetal pinion driving a molded plastic gear.) Notesthat measurements of profiles on both gearsshowed a mismatch of pressure angles. Proposesthat such a mismatch could be related to “meaninvolute slope’. Shows that when the mismatch isreduced, noise components drop to acceptablelevels.ISBN: 1--55589--592--1 Pages: 8

92FTMS1. Spur Gears -- A New Approach to ToothDesignAuthor: B. Srinivasulu

Studies a new spur gear tooth design in which eachtooth has a through hole made on its center lineparallel to the gear axis. Studies the effect of holesize and location. Reports that the same loadcontact stresses in a hollow--solid mesh are lowerthan that of a solid--solid mesh. Further reports thatdynamic loads in a hollow--solid mesh are the sameas that of a solid--solid mesh with the samedamping.ISBN: 1--55589--593--X Pages: 25



1991 PAPERS

91FTM1.CNCBevelGearGenerators andFlaredCupFormate Gear GrindingAuthor: T. Krenzer

Full CNC bevel generators are positioned relativelybetween the tool and work with simplemechanismsand electronic controls. As a result, the gearengineer has new freedoms for the control of geartooth shapes and contact characteristics. Thispaper defines the flared cup Formate gear grindingprocess and the motions that can be applied to theprocess. Surface comparison charts and toothcontact analysis are used to demonstrate theeffects of the freedoms. Comparisons of jobsdesignedwith andwithout themotions are included.ISBN: 1--55589--574--3 Pages: 14

91FTM2. CNC Technology and New CalculationMethods Permit Efficient System IndependentManufacturing of Spiral Bevel GearsAuthor: D. Weiner

A strictly applied CNC technology on machines forcutting or grinding spiral bevel gears allows themachining of different gearing systems on onemachine. Based on this, the selection of the mostfavorable gearing system is possible, consideringeconomic issues, load bearing capacity and noisecharacteristics.ISBN: 1--55589--602--2 Pages: 10

91FTM3. High Efficiency Gear HobbingAuthors: G. Ashcroft and B. Cluff

Discusses the design advances of disposable gearcutting tools, specifically those which haveproduced the non--resharpenable Wafer hob, theapplication of the tools, and the benefits derivedfrom applying these tools in gear manufacturing.The concurrent development of hobbing machinescapable of efficiently applying these tool designs isalso detailed.ISBN: 1--55589--600--6 Pages: 17

91FTM4. Low Noise Marine GearsAuthor: W. Haller

Reduction gears for frigates, corvettes, destroyersand submarines have to be reliable, durable, easyto maintain, small in size and as light as possible. Inprinciple, there are two ways of reducing structureborne noise emission of gearboxes: primary andsecondary. This paper deals with primarymeasures, those which tend to eliminate thegeneration of noise at its source.ISBN: 1--55589--601--4 Pages: 13

91FTM5. Machine Tool Condition MonitoringAuthor: L.E. Stockline

Actual production applications of computerassisted Tool Condition Monitoring Systems are

reviewed from case studies over the last severalyears. New applications are being encouraged bythe aircraft and automotive industries which, due tothe development of new sensors andmicroprocessor strategy, allow untendedmanufacturing. There is a major impact on qualitycontrol, maintenance and machine uptime whentool wear, tool breakage and missing tool or forcescan be accurately measured.ISBN: 1--55589--573--5 Pages: 8

91FTM6. Comparing Surface Failure Modes inBearings And Gears: Appearances versusMechanismsAuthor: C. Moyer

Contact fatiguemodes are identified over a range ofmodified lambda values. Describes failure modesand interprets the wear, fracture and/or fatiguemechanisms that lead to the failure initiation.Considering the similarity in appearance of gearand bearing failure modes in light of the differentrelative surface motions and tractions of the twocontacts, this comparison helps provide insight intothe basic causes of the failures and suggestsmethods to avoid them.ISBN: 1--55589--603--0 Pages: 13

91FTM7. Low Cycle and Static Bending Strength ofCarburized and High Hardness Through HardenedGear TeethAuthor:W. Pizzichil

Presents a summary of the testing methodsemployed and the results generated forunidirectional and reverse bending tests of verycoarse and medium pitch gear teeth. Actualmeasured stresses were compared with FEMtheoretical stresses and AGMA stress numbers.The purpose of this testing was to evaluate whichtype of hardening method would yield a gear tooththat could carry the highest load withoutcatastrophic breakage failure in a single, or very lowcyclic load application. This testing simulated theoutput pinion and a planet gear for a jack--up geardrive used on oil drilling platforms. Three separatetests were conducted over a period of time.ISBN: 1--55589--604--9 Pages: 15

91FTM8. Methods of Statistical Dynamics for theCalculation of Gear Stress Distribution and its Effecton Gear Failure ProbabilityAuthor: M. Haykin

The process ofmostmachine loading has a randomcharacter which is determined by external variationand dynamic qualities of the system. Such anapproach was used to obtain the load spectrum forgears and the probability of its failure. Analysis andexperiments showed that gain factor for gear isdistinguished by the similar parameter of the entiredrive system. This is explained by the uniformdistribution of gear stress even for cases of static



loading. Method of gear strength calculation withthe statistical parameter is discussed.ISBN: 1--55589--613--8 Pages: 10

91FTM9. Rerating Damaged Naval Ship PropulsionGearsAuthors: R. Coblenz and C. Reeves

When naval ship propulsion gear teeth break, theaffected teeth are ”field dressed”, so that the unitscan be put back into service. Then the gears arererated to a lower rating and used reliably, at leastuntil replacement elements become available.Using sketches or computers, an estimate is madeof the instantaneous total length of contact as thedamaged sections go throughmeshwith the resultsbeing used as a basis of rerating the unit.Consideration is given to end reliefs, the location ofthe damage on the helix and the nature of the fielddressing, and actual material properties. Theresults of this analysis, together with analysis of thecauses of the original failure, provide limits withinwhich the unit can be operated with the samereliability as new.ISBN: 1--55589--606--5 Pages: 9

91FTM10. Dynamic Measurements of Gear ToothFriction and LoadAuthors: B. Rebbechi, F. Oswald, and D. Townsend

Aprogram to experimentally and theoretically studyfundamental mechanisms of gear dynamicbehavior is being conducted at the NASA LewisResearch Center in support of a joint researchprogram between NASA and the U.S. Army. Thispaper presents the results of dynamic tooth--filletstrain gage measurements from the NASAgear--noise rig, and it introduces a technique forusing these measurements to separate the normaland tangential (friction) components of the load atthe tooth contact.ISBN: 1--55589--607--3 Pages: 13

91FTM11. Initial Design of Gears Using ArtificialNeural NetAuthors: T. Jeong, T. Kicher, and R. Zab

Most mechanical engineering design problemsrequire both computational and decision makingaspects. Those decision making tasks can beperformed by an artificial neural net. Theadaptability of the artificial neural net for initial geardesign was demonstrated and the detailedapplication is explained throughout the paper.ISBN: 1--55589--608--1 Pages: 11

91FTM12. The Combined Mesh StiffnessCharacteristics of Straight and Spiral Bevel GearsAuthors: K. Yoon, J.W. David, and M. Choi

The combined mesh stiffness of spiral bevel gearsis one important factor for dynamic analysis. Thetotal deflection on the contact line of a tooth pair is

composed of bending, shear and tooth contactdeflections. The bending and shear deflections onthe contact line of the gear tooth are evaluated bythe finite element method with isoparametric shellelements, and the tooth contact deflections areevaluated using Hertzian contact theory. Based onthese deflections, stiffness is obtained using the socalled flexibility method, and then the combinedmesh stiffness is obtained by applying contact andload sharing ratios.ISBN: 1--55589--609--X Pages: 9

91FTM13. Separation of Lubrication and Cooling inOil--Jet Lubricated GearsAuthors: J. Greiner and K. Langenbeck

Results from tests on a high--speed back--to--backstand (vt = 70 m/sec = 13725 ft/min) show theinfluence of the separation of lubrication andcooling oil supply on gear temperatures (scuffingload capacity) and efficiency. The gear mesh is onlygiven the minimum oil flow rate necessary forlubricating the working tooth flanks. Cooling isprovided by spraying oil onto the inner surfaces ofthe rims. This leads to a reduction of up to 60% ofthe total oil flow rate compared to currentlyrecommended flow rates. In spite of the reducedtotal oil flow rate the temperature level of the gearscan be kept low while the efficiency slightlyincreases due to reduced hydraulic losses in thegear mesh.ISBN: 1--55589--610--3 Pages: 19

91FTM14. The Effect of Thermal Shrink andExpansion on Plastic Gear GeometryAuthor: R. Kleiss

When plastic gears are meshed with steel gearsthere can be the differences in thermal expansionbetween the twomaterials. If a particular gearmeshis expected to operate satisfactorily over a widethermal range, the variations inmesh geometry dueto temperature must be taken into account. Thesevariable parameters can pose vexing problems tothe plastics gear designer. This paper presents astraightforward way to consider the shrinkage ofplastic gears both in molding and in operation.ISBN: 1--55589--611--1 Pages: 6

91FTM15. Gear Hardness TechnologyAuthors: M. Broglie and D. Smith

As demands on the gear designer to make gearingthat is smaller, lighter and more reliable increasesso does the demand for better materials and heattreat processes. Proper hardness of a gear, both inthe tooth and in the body is becoming increasinglycritical since load carrying capacity is dependent onhardness. The scope of this paper is limited to themost common methods of heat treating steelgearing; however, there are many methods of heattreatment in wide use throughout the industry.ISBN: 1--55589--612--X Pages: 14



91FTM16. Contact Analysis of Gears Using aCombined Finite Element and Surface IntegralMethodAuthors: S.M. Vijayakar and D.R. Houser

Describes a new method for solving the contactproblem in gears. The method uses a combinationof the finite element method and a surface integralform of the Bousinesq and Cerruti solutions.Numerical examples are presented for contactinghypoid, helical, and crossed axis helical gears.ISBN: 1--55589--614--6 Pages: 12

91FTM17.The Influence of Lubrication on theOnset ofSurface Pitting in Machinable Hardness Gear TeethAuthors: C. Massey, C. Reeves, and E. Shipley

Tests have been run on machinable hardnesshelical gears to study the influence of changes incalculated oil film thickness in the operating gearteeth in regard to the onset of surface pitting.Control tests were run at constant load to developtypical pitting patterns on the gear teeth within areasonable test period. Subsequent tests werecarried out to evaluate the changes in resistance topitting that occurred when the oil film thickness wasvaried. All the tests were operated with an amplecontrolled supply of a petroleum--based lubricant,symbol 2190 TEP, that meets the specifications ofMIL--L--1 7331.ISBN: 1--55589--605--7 Pages: 24

91FTMS1. The Element Stress Analysis of a GenericSpur Gear ToothAuthor: E. A. Tennyson

The prediction of bending stresses in a gear tooth,resulting froman externally applied torque, requiresspecial consideration when designing spur gearsystems. The tooth geometry is such that excessrisers exist which must be accounted for. Inaddition, variables affecting the exact load point onthe tooth and the direction of the applied load arecritical. An interactive preprocessor is developedwhich generates all the information, including adetailed tooth profile, necessary to perform a finiteelement bending stress analysis of the gearsystem. To validate the procedure, a test group ofspur gears is identified and analyzed. The resultsare compared to those obtained via the AmericanGear Manufacturers Association (AGMA)standards. The comparison revealed the finiteelement stresses to be slightly more conservativethan corresponding AGMA standard stresses. Ageneralized stress equation and geometry factor,based on the finite element approach, are alsointroduced. This paper is intended only as a proof ofconcept.ISBN: 1--55589--615--4 Pages: 12

1990 PAPERS

90FTM1. Contact Stresses in Gear TeethAuthor: J.R. Colbourne

It is shown that neither Hertz’s fine contact theorynor his point contact theory are entirely adequatefor the accurate calculation of contact stresses ingear teeth. A numerical procedure is described,which can be used to find the contact stress incases where the relative curvatures in the contactregion are not constant.ISBN: 1--55589--553--0 Pages: 15

90FTM2. An Industrial Approach for Load CapacityCalculation of Worm Gears (Verifying and Design)Author: M. Octrue

The method proposed in this paper is based on ananalytical ratingmethod which has been developedsome years ago by the author (see AGMA paper88FTM6). The calculation is based on thedetermination of themaximumof pressure betweenthe mating teeth which is made by using a specificcriteria for worm gears. The method can be used toverify the load capability of a worm gear but also todesign a new gear covering several types of toothprofile. Calculations are provided as examples andcomparisons have beenmadewith results obtainedby the initial analyticalmethod, and by standardizedmethods (AGMA, BS).ISBN: 1--55589--554--9 Pages: 10

90FTM3. Simulation of Meshing, Transmission Errorsand Bearing Contact for Single--EnvelopingWorm--Gear DrivesAuthors: F.L. Litvin, and V. Kin

The authors have developed a computerizedmethod for simulation of meshing and bearingcontact (TCA) for single--enveloping worm--geardrives. The developed computer programs enableone to determine the transmission errors and theshift of bearing contact that are caused by wormand gear misalignment. An important theorem isproven for determination of the transfer point on thetheoretical line of contact where the path of pointcontact starts for a misaligned worm--gear drive. Amethod of assembly for compensation ofmisalignment is proposed.ISBN: 1--55589--555--7 Pages: 14

90FTM4. Different Types of Wear -- How to Classify?Author: L. Faure

In the first part, this document describes all thetypes and aspects of wear which can occur on thegear teeth in operation, with causes andexplanations concerning their appearance. Foreach type of wear, the possible evolution and thelimits which should not be passed to avoid a failureor severe damage to the tooth, thus reducing the lifeof the gear, are clearly specified. Aspects of wear



types which can be considered as normal, mediumor progressive are also described and solutions arepresented as a guide for wear stabilizing.ISBN: 1--55589--556--5 Pages: 17

90FTM5. Polishing WearAuthors: A. Milburn, R. Errichello and D. Godfrey

Polishing wear has been known to occur on pistonrings, cylinder bores, valve lifters, hydrauliccomponents, rolling--element bearings and gearteeth. The bright, polished surfaces may look good,but polishingwear is detrimental because it is a highwear phenomenon which reduces the geometricaccuracy of the components. A case history ispresented of a gearbox which suffered extensivepolishingwear of the gear teeth and rolling--elementbearings. The results of research into the basicmechanism of polishing wear, and laboratoryanalyses of materials and lubricants are presented.Polishing wear is shown to be due to fine--scaleabrasion. It is promoted by a combination of a fineabrasive and a gear oil with chemically--activeadditives.ISBN: 1--55589--557--3 Pages: 17

90FTM6. Dynamic Responses of Aircraft GearsAuthor: K. Buyukataman

Rapid and destructive failures of high quality, highspeed, light weight and highly loaded aircraft gearsare indications of the vibrational energy (associatedwith neutral frequency modes) exceeding thefatigue endurance limit of advanced gear materials.The paper reviews: A) Experimental and analyticalmethods to identify and define resonant mode, B)Effects of gear design and manufacturing variableson the generation and damping of vibrationalenergy.ISBN: 1--55589--558--1 Pages: 21

90FTM7. Advanced Rotorcraft Transmission Program-- A Status ReviewAuthors: R.J. Drago and J.W. Lanski

The paper reports on Boeing Helicopters contractwith the U. S. Army to conduct the AdvancedRotorcraft Transmission (ART) TechnologyIntegration Demonstration program, The objectivesof the program are to reduce transmission weight,reduce transmission noise and improvetransmission life. The paper presents an overviewof the planned program and a broad description ofthe major tasks to be accomplished.ISBN: 1--55589--559--X Pages: 19

90FTM8. Investigations on the Scuffing Resistance ofHigh--Speed GearsAuthors: H. Winter and H. F. Collenberg

Test results with a high speed four square gear testrig (nmax = 26 000 rpm) show the influence ofspeed, viscosity, base oil, type, and amount ofadditive on the scuffing load. In some cases at highspeed the scuffing load can be more than twice the

value calculated according to ISO/DIS 6336/4. Thereason for the speed--dependency of the scuffingload is explained by the kinetics of the chemicalreaction between the metal and the additive. It isdescribed, how a calculation method could takeaccount of the high scuffing load at high speed.ISBN: 1--55589--560--3 Pages: 18

90FTM9. A Procedure That Accounts forManufacturing Errors in the Design Minimization ofTransmission Error in Helical GearsAuthors: S. Sundareson, K. Ishii and D.R. Houser

This paper deals with the design of helical gearsthat have minimum transmission error and, at thesame time, are less sensitive to manufacturingerrors. The paper addresses two stages in design:1) Design generation stage where feasible designsare generated for a specification and 2) Design ofprofile and lead modifications that minimizetransmission error and its sensitivity tomanufacturing errors. The paper presents a briefdiscussion on how one can effectively minimizetransmission error in helical gears by combiningboth lead and profile modificationsISBN: 1--55589--561--1 Pages: 19

90FTM10. The Mechanism of Failure With andWithout Titanium Nitride Coating in Roller TestsAuthors: J. Vižintin

To clarify the effect of Titanium Nitride (TiN) coatingon failure resistance and frictional characteristicsand compare this effect with that produced by healtreated coatings, two roller tests have been madeand the stress resulting from the combination of theHertzian stress field and frictional force field on andbelow the contacting surface as well as the flashtemperature rise were calculated. The failureresistance of the TiN--coated roller pair was greaterthan that of the heat treated roller pair. Themechanism of failure resistance can be explainedby the shearing stress (Hertzian stress + frictionalforce) acting on the contact surface. This stressmodifies the structure in the vicinity below the TiNlayer which is then sheared in the weak trackdirection.ISBN: 1--55589--562--X Pages: 33

90FTM11. Multiple Iteration -- RespectableTrial--and--ErrorAuthor: M.L. Baxter

“Trial--and--error” was once a dirty word. Now, withcomputers, it has become the most valuable tool inengineering calculation. The procedure describedin this paper permits any number of input variables(say A,B,C) to be systematically varied until anequal number of results (say X,Y,Z) are zero,regardless of the complexity of the equationsrelating A,B, C to X,Y,Z. It has been usedsuccessfully by the writer for up to seven variables.This paper is not concernedwith the structure of thecomputer program representing this procedure, but



rather with the kinds of engineering problems thatcan use it, and how it can be used as a subroutine inengineering programs. Two actual gearapplications will be described.ISBN: 1--55589--563--8 Pages: 15

90FTM12. Design of New Systems of ControlledSpeed DrivesAuthors: M. Hirt, T. Weiss and P. Bolger

Processes in chemical industries and power plantstations require, to a certain extent, variable speeddrives of high power capacity. In contrast tocontrolled hydrodynamic or friction clutches, a newsystem of hydrostatic controlled superimposedplanetary gears was developed. Design andcalculations as well as efficiency comparisons toother systems will be described. Practicalexperiences in the drive of large boiler feed pumpswill be explained which prove the reliability of thesedrives.ISBN: 1--55589--564--6 Pages: 14

90FTM13. Face Milling or Face HobbingAuthor: Theodore J. Krenzer

Face milling and face hobbing are the two principalprocesses used in the production of bevel andhypoid gears. A manufacturer must decide on oneor the other. This paper defines the methods andthe inherent characteristics they impose on thetooth design and manufacture. Geometric toothdesign differences and the reasons for thedifferences are examined. TCA, finite elementanalysis and test results for the two processes areincluded. Cutting tools and processes arecompared; advantages and disadvantages of eachprocess are enumerated and criteria for theselection of one process over the other is proposed.ISBN: 1--55589--565--4 Pages: 13

90FTM14. AClosed and Fast Solution Formulation forPractice Oriented Optimization of Real Spiral Beveland Hypoid Gear Flank GeometryAuthor: H.J. Stadtfeld

If a very specific and systematic method is appliedto spiral bevel and hypoid gear correction, a newpossibility exists to accurately and quickly designand manufacture high quality gearsets. Allgenerated data can be archived on a diskette,saved in machine control memory or stored in acentral host computer. The described algorithm isbased on a differential geometry calculation which

is to activate about simple and intuitive inputgraphics.ISBN: 1--55589--566--2 Pages: 11

90FTM15. Optimal Design of Straight Bevel GearsAuthors: Rajiv Agrawal, Gary L. Kinzer and Donald R.Houser

Describes the design of a straight bevel gearsetwith the objective of minimizing the enclosedvolume. The specifications for the design are thepower requirements, the gear ratio, pinion speedand the material properties. The design variablesare the number of pinion teeth, the diametral pitch,and the face width. Constraints are set onfacewidth,minimumnumber of pinion teeth, and thesafety factors for bending and pitting strength. Thecomplete analysis for the gearset is based on therating procedure described in the ANSI/AGMA2003--A86 standard. The optimization procedure isillustrated through a numerical example and thedesign is also compared with a spur gearoptimization method using Tregold’sapproximation.ISBN: 1--55589--567--0 Pages: 11

90FTMS1. Kinematic Analysis of Transmissions --Based on the Finite Element MethodAuthor: A.L. Sytstra

In order to evaluate the kinematic properties of adesign of a transmission in its early stages, acomputer program has been developed. By meansof geometric reasoning, a finite element model isdeduced from the conceptual design which hasbeen built using an experimental 3D object editor.Since the interrelations between the objects are notspecified by the designer they are found by thecomputer by supplying a set of rules. The followingkinematic analysis uses a mixed Euler/Lagrangedescription and detects mechanisms (possibleinfinitesimal displacements of the nodal pointswithout causing strain in the elements) in thetransmission. The mechanisms found arevisualized by the object editor by means ofalternating images of the design on the screenwhich gives a real idea of motion. A well--foundeddecision can be made whether the conceptualmodel has to be changed, rejected, or can beaccepted. The method of analysis used gives agood start for a static and dynamic analysis.ISBN: 1--55589--568--9 Pages: 18



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Catalog of Technical Publications


AGMA STANDARDS

Full Set of Current Standards (CD) $3870.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .(Priced separately: $5952.00)

Full Set of Current Standards (Printed copy) $4960.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

NUMBER TITLE LIST PRICE217.01 (R1999) Information Sheet -- Gear Scoring Design Guide for Aerospace Spur and

Helical Power Gears $43.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .299.01 (R1999) Gear Sound Manual: Section I, Fundamentals of Sound as Related to Gears;

Section II, Sources, Specifications, and Levels of Gear Sound; Section III,Gear--Noise Control $69.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

900--G00 Style Manual for the Preparation of Standards $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .901--A92 (R1997) A Rational Procedure for the Preliminary Design of Minimum Volume Gears $32.00. . . .904--C96 Metric Usage $40.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .908--B89 (R1999) Information Sheet -- Geometry Factors for Determining the Pitting Resistance

and Bending Strength of Spur, Helical and Herringbone Gear Teeth $80.00. . . . . . . . . . .910--C90 (R2003) Formats for Fine--Pitch Gear Specification Data $48.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .911--A94 (R2000) Guidelines for Aerospace Gearing $91.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .912--A04 Mechanisms of Gear Tooth Failure $66.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .913--A98 Method for Specifying the Geometry of Spur and Helical Gears $55.00. . . . . . . . . . . . . . .914--B04 Gear Sound Manual -- Part I: Fundamentals of Sound as Related to Gears; Part II:

Sources, Specifications and Levels of Gear Sound; Part III: Gear Noise Control $72.00915--1--A02 Inspection Practices -- Part 1: Cylindrical Gears -- Tangential Measurements $55.00. . .915--2--A05 Inspection Practices -- Part 2: Cylindrical Gears -- Radial Measurements $44.00. . . . . . .915--3--A99 Inspection Practices -- Gear Blanks, Shaft Center Distance and Parallelism $30.00. . . . .917--B97 (R2003) Design Manual for Parallel Shaft Fine--Pitch Gearing $80.00. . . . . . . . . . . . . . . . . . . . . . . .918--A93 (R1998) A Summary of Numerical Examples Demonstrating the Procedures for

Calculating Geometry Factors for Spur and Helical Gears $64.00. . . . . . . . . . . . . . . . . . . .920--A01 Materials for Plastic Gears $55.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .922--A96 Load Classification and Service Factors for Flexible Couplings $38.00. . . . . . . . . . . . . . . .923--B05 Metallurgical Specifications for Steel Gearing $75.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .925--A03 Effect of Lubrication on Gear Surface Distress $65.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .926--C99 Recommended Practice for Carburized Aerospace Gearing $45.00. . . . . . . . . . . . . . . . . .927--A01 Load Distribution Factors -- Analytical Methods for Cylindrical Gears $65.00. . . . . . . . . . .930--A05 Calculated Bending Load Capacity of Powder Metallurgy (P/M) External

Spur Gears $83.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .931--A02 Calibration of Gear Measuring Instruments and Their Application to the

Inspection of Product Gears $60.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .932--A05 NEW Rating the Pitting Resistance and Bending Strength of Hypoid Gears $60.00. . . . . . . . . .933--B03 Basic Gear Geometry $35.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .935--A05 Recommendations Relative to the Evaluation of Radial Composite Gear Double

Flank Testers $40.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .938--A05 NEW Shot Peening of Gears $45.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1003--G93 (R1999) Tooth Proportions for Fine--Pitch Spur and Helical Gears $64.00. . . . . . . . . . . . . . . . . . . . .1006--A97 (R2003) Tooth Proportions for Plastic Gears $64.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1010--E95 (R2000) Appearance of Gear Teeth --Terminology of Wear and Failure $91.00. . . . . . . . . . . . . . . . .1012--G05 Gear Nomenclature, Definitions of Terms with Symbols $78.00. . . . . . . . . . . . . . . . . . . . . .1102--A03 Tolerance Specification for Gear Hobs $78.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1106--A97 (R2003) Tooth Proportions for Plastic Gears $59.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .


AGMA Standards (continued)

1328--1 Cylindrical Gears -- ISO System of Accuracy -- Part 1: Definitions andAllowable Values of Deviations Relevant to Corresponding Flanks of GearTeeth $60.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

1328--2 Cylindrical Gears -- ISO System of Accuracy -- Part 2: Definitions andAllowable Values of Deviations Relevant to Radial Composite Deviations andRunout Information $40.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

2000--A88 Gear Classification and Inspection Handbook -- Tolerances and MeasuringMethods for Unassembled Spur and Helical Gears (Including MetricEquivalents) $133.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

2001--D04 Fundamental Rating Factors and Calculation Methods for Involute Spur andHelical Gear Teeth $159.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

2002--B88 (R1996) Tooth Thickness Specification and Measurement $85.00. . . . . . . . . . . . . . . . . . . . . . . . . . . .2003--B97 (R2003) Rating the Pitting Resistance and Bending Strength of Generated Straight

Bevel, Zerol Bevel, and Spiral Bevel Gear Teeth $138.00. . . . . . . . . . . . . . . . . . . . . . . . . . .2004--B89 (R2000) Gear Materials and Heat Treatment Manual $96.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2005--D03 Design Manual for Bevel Gears $159.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2007--C00 Surface Temper Etch Inspection After Grinding $38.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2008--C01 Assembling Bevel Gears $64.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2009--B01 Bevel Gear Classification, Tolerances, and Measuring Methods $96.00. . . . . . . . . . . . . . .2010--A94 (R2000) Measuring Instrument Calibration ---- Part I, Involute Measurement $55.00. . . . . . . . . . . .2011--A98 Cylindrical Wormgearing Tolerance and Inspection Methods $80.00. . . . . . . . . . . . . . . . . .2015--1--A01 Accuracy Classification System -- Tangential Measurements for Cylindrical

Gears $60.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2015--2--A06 NEW Accuracy Classification System -- Radial Measurements for Cylindrical Gears $40.00. . .Supp to Accuracy Classification System -- Tangential Measurement Tolerance Tables2015/915 for Cylindrical Gears $35.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2101--D04 Fundamental Rating Factors and Calculation Methods for Involute Spur and

Helical Gear Teeth $133.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2110--A94 (R2000) Measuring Instrument Calibration ---- Part I, Involute Measurement (Metric) $55.00. . . . .2111--A98 Cylindrical Wormgearing Tolerance and Inspection Methods $70.00. . . . . . . . . . . . . . . . . .2113--A97 Measuring Instrument Calibration, Gear Tooth Alignment Measurement $55.00. . . . . . . .2114--A98 Measuring Instrument Calibration, Gear Pitch and Runout Measurements $64.00. . . . . .2116--A05 Evaluation of Double Flank Testers for Radial Composite Measurement of Gears $38.006000--B96 (R2002) Specification for Measurement of Linear Vibration on Gear Units $69.00. . . . . . . . . . . . . .6001--D97 (R2003) Design and Selection of Components for Enclosed Gear Drives $80.00. . . . . . . . . . . . . . .6002--B93 (R2001) Design Guide for Vehicle Spur and Helical Gears $64.00. . . . . . . . . . . . . . . . . . . . . . . . . . . .6004--F88 (R1996) Gear Power Rating for Cylindrical Grinding Mills, Kilns, Coolers and Dryers $80.00. . . . .6005--B89 (R1996) Power Rating for Helical and Herringbone Gearing for Rolling Mill Service $75.00. . . . . .6006--A03 Standard for Design and Specification of Gearboxes for Wind Turbines $198.00. . . . . . .6008--A98 Specifications for Powder Metallurgy Gears $53.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6011--I03 Specification for High Speed Helical Gear Units $95.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .6013--A06 NEW Standard for Industrial Enclosed Gear Drives $159.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6022--C93 (R2000) Design Manual for Cylindrical Wormgearing $69.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6023--A88 (R2000) Design Manual for Enclosed Epicyclic Gear Drives $80.00. . . . . . . . . . . . . . . . . . . . . . . . . .6025--D98 Sound for Enclosed Helical, Herringbone and Spiral Bevel Gear Drives $75.00. . . . . . . .6032--A94 (R2000) Standard for Marine Gear Units: Rating $95.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6033--B98 Materials for Marine Propulsion Gearing $80.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6034--B92 (R1999) Practice for Enclosed Cylindrical Wormgear Speed Reducers and Gearmotors $53.00. .6035--A02 Design, Rating and Application of Industrial Globoidal Wormgearing $75.00. . . . . . . . . . .6113--A06 NEW Standard for Industrial Enclosed Gear Drives (Metric) $135.00. . . . . . . . . . . . . . . . . . . . . . .



AGMA Standards (concluded)

6123--A88 (R2000) Design Manual for Enclosed Epicyclic Metric Module Gear Drives $80.00. . . . . . . . . . . . .6133--B98 Materials for Marine Propulsion Gearing $70.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6135--A02 Design, Rating and Application of Industrial Globoidal Wormgearing (Metric) $70.00. . . .9000--C90 (R2001) Flexible Couplings -- Potential Unbalance Classification $59.00. . . . . . . . . . . . . . . . . . . . . .9001--B97 (R2003) Flexible Couplings -- Lubrication $38.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .9002--B04 Bores and Keyways for Flexible Couplings (Inch Series) $52.00. . . . . . . . . . . . . . . . . . . . .9003--A91 (R1999) Flexible Couplings -- Keyless Fits $48.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .9004--A99 Flexible Couplings -- Mass Elastic Properties and Other Characteristics $65.00. . . . . . . .9005--E02 Industrial Gear Lubrication $80.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .9008--B00 Flexible Couplings – Gear Type – Flange Dimensions, Inch Series $38.00. . . . . . . . . . . .9009--D02 Flexible Couplings -- Nomenclature for Flexible Couplings $46.00. . . . . . . . . . . . . . . . . . .9112--A04 Bores and Keyways for Flexible Couplings (Metric Series) $50.00. . . . . . . . . . . . . . . . . . . .10064--1 Cylindrical Gears -- Code of Inspection Practice -- Part 1: Inspection of

Corresponding Flanks of Gear Teeth $75.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .10064--2 Cylindrical Gears -- Code of Inspection Practice -- Part 2: Inspection Related

to Radial Composite Deviations, Runout, Tooth Thickness and Backlash $55.00. . . . . . .14179--1 Gear Reducers -- Thermal Capacity Based on ISO/TR 14179--1 $65.00. . . . . . . . . . . . . . .

ISO STANDARDS BY TECHNICAL COMMITTEE 60

53:1998 Cylindrical gears for general and heavy engineering – Standard basic racktooth profile $41.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

54:1996 Cylindrical gears for general engineering and for heavy engineering -- Modules $30.00.677:1976 Straight bevel gears for general engineering and heavy engineering -- Basic

rack $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .678:1976 Straight bevel gears for general engineering and heavy engineering -- Modules

and diametral pitches $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .701:1998 International gear notation -- Symbols for geometric data $35.00. . . . . . . . . . . . . . . . . . . . .1122--1:1998 Glossary of gear terms -- Part 1: Definitions related to geometry $139.00. . . . . . . . . . . . .1122--2:1999 Vocabulary of gear terms -- Part 2: Definitions related to worm gear geometry $82.00. .1328--1:1995 Cylindrical gears -- ISO system of accuracy -- Part 1: Definitions and allowable

values of deviations relevant to corresponding flanks of gear teeth (SeeANSI/AGMA ISO 1328--1) -- --. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

1328--2:1997 Cylindrical gears -- ISO system of accuracy -- Part 2: Definitions and allowablevalues of deviations relevant to radial composite deviations and runoutinformation (See ANSI/AGMA ISO 1328--2) -- --. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

1340:1976 Cylindrical gears -- Information to be given to the manufacturer by thepurchaser in order to obtain the gears required $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .

1341:1976 Straight bevel gears -- Information to be given to the manufacturer by thepurchaser in order to obtain the gears required $30.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .

2490:1996 Single--start solid (monoblock) gear hobs with tenon drive or axial keyway,1 to 40 module -- Nominal dimensions $35.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

4468:1982 Gear hobs -- Single start -- Accuracy requirements $71.00. . . . . . . . . . . . . . . . . . . . . . . . . . .6336--1:1996 Calculation of load capacity of spur and helical gears -- Part 1: Basic

principles, introduction and general influence factors $160.00. . . . . . . . . . . . . . . . . . . . . . . .6336--2:1996 Calculation of load capacity of spur and helical gears -- Part 2: Calculation of

surface durability (pitting) $102.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6336--3:1996 Calculation of load capacity of spur and helical gears -- Part 3: Calculation of

tooth bending strength $150.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .6336--5:2003 Calculation of load capacity of spur and helical gears -- Part 5: Strength and

quality of materials $117.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .


Full set of 4 ISO 6336 Standards (cannot be used individually) $475.00. . . . . . . . . . .8579--1:2002 Acceptance code for gears -- Part 1: Determination of airborne sound power

levels emitted by gear units $131.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .8579--2:1993 Acceptance code for gears -- Part 2: Determination of mechanical vibration of

gear units during acceptance testing $66.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .9083:2001 Calculation of load capacity of spur and helical gears -- Application to marine

gears $131.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .9085:2002 Calculation of load capacity of spur and helical gears -- Application for

industrial gears $131.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .TR10064--1:1992 Cylindrical gears -- Code of inspection practice -- Part 1: Inspection of

corresponding flanks of gear teeth (See AGMA ISO 10064--1) -- --. . . . . . . . . . . . . . . . . . . .TR10064--2:1996 Cylindrical gears -- Code of inspection practice -- Part 2: Inspection related to

radial composite deviations, runout, tooth thickness and backlash (See AGMAISO 10064--2) -- --. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

TR10064--3:1996 Cylindrical gears -- Code of inspection practice -- Part 3: Recommendationsrelative to gear blanks, shaft centre distance and parallelism of axes $41.00. . . . . . . . . . .

TR10064--4:1998 Cylindrical gears -- Code of inspection practice -- Part 4: Recommendationsrelative to surface texture and tooth contact pattern checking $92.00. . . . . . . . . . . . . . . . .

10300--1:2001 Calculation of load capacity of bevel gears -- Part 1: Introduction and generalinfluence factors $124.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

10300--2:2001 Calculation of load capacity of bevel gears -- Part 2: Calculation of surfacedurability (pitting) $77.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

10300--3:2001 Calculation of load capacity of bevel gears -- Part 3: Calculation of tooth rootstrength $112.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

TR10495:1997 Cylindrical gears-- Calculation of service life under variable loads -- Conditionsfor cylindrical gears according to ISO 6336 $66.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

10825:1995 Gears -- Wear and damage to gear teeth -- Terminology $139.00. . . . . . . . . . . . . . . . . . . . .TR10828:1997 Wormgears -- Geometry of worm profiles $82.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .TR13593:1999 Enclosed gear drives for industrial applications $150.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . .13691:2001 Petroleum and natural gas industries -- High speed special--purpose gear units $139.00TR13989--1:2000 Calculation of scuffing load capacity of cylindrical, bevel and hypoid gears –

Part 1: Flash temperature method $112.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .TR13989--2:2000 Calculation of scuffing load capacity of cylindrical, bevel and hypoid gears –

Part 2: Integral temperature method $124.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .14104:1995 Gears -- Surface temper etch inspection after grinding $41.00. . . . . . . . . . . . . . . . . . . . . . .14179--1:2001 Gears -- Thermal capacity -- Part 1: Rating gear drives with thermal equilibrium

at 95°C sump temperature -- --. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .TR14179--2:2001 Gears -- Thermal capacity -- Part 2: Thermal load--carrying capacity $102.00. . . . . . . . . .14635--1:2000 Gears – FZG test procedures – Part 1: FZG method A/8, 3/90 for relative

scuffing load carrying capacity of oils $77.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .14635--3:2005 Gears -- FZG test procedures -- Part 3: FZG test method A/2,8/50 for relative scuffing

load--carrying capacity and wear characteristics of semifluid gear greases $82.00. . . . . .17485:2006 Bevel gears ---- ISO system of accuracy $98.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .



TECHNICAL PAPERS

2005 Full Set of Fall Technical Meeting Papers (20 papers on CD) $490.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2004 Full Set of Fall Technical Meeting Papers (14 papers on CD) $300.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2002 Full Set of Fall Technical Meeting Papers (12 papers on CD) $200.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .2001 Full Set of Fall Technical Meeting Papers (12 papers on CD) $150.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .1990--2000 AGMA Fall Technical Meeting Papers -- Millennium CD $200.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

All Individual Technical Papers $35.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .For titles and authors of papers from FTM Meetings prior to 1990, please send for our “TECHNICAL PAPERS CATALOG”.

GEAR SOFTWARE

Gear Rating Suite (AGMA Members) $1195.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .(Non Members) $1495.00. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

AGMA index

Documents

Transcript of AGMA index