Norma API Tr 6af

A P I BULL*bAF 95 0732290 0546303 299

Technical Report on Capabilities of API Flanges Under Combinations of Load

API 6AF SECOND EDITION, SEPTEMBER 1,1995 (FORMERLY BULLETIN 6AF)

American Petroleum institute 1220 L Street. Northwest

11 Washington, D.C. 20005

Copyright American Petroleum Institute Provided by IHS under license with API Licensee=PETREVEN/5969924001, User=Figuera, Guillermo

Not for Resale, 07/31/2008 10:49:42 MDTNo reproduction or networking permitted without license from IHS

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A P I BLILL*bAF 95 W 0732290 0546302 i125


Exploration and Production Department

API 6AF SECOND EDITION, SEPTEMBER 1, 1995 (FORMERLY BULLETIN 6AF)

American Petroleum Institute



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A P I BULL*bAF 95 0732290 0546303 Ob1 =

SPECIAL NOTES

API publications necessarily address problems of a general nature. With respect to particular circumstances, local, state, and federal laws and regulations should be reviewed.

API is not undertaking to meet the duties of employers, manufacturers, or suppliers to warn and properly train and equip their employees, and others exposed, concerning health and safety risks and precautions, nor undertaking their obligations under local, state, or federal laws.

Information concerning safety and health risks and proper precautions with respect to particular materials and conditions should be obtained from the employer, the manufac- turer or supplier of that material, or the material safety data sheet.

Nothing contained in any API publication is to be construed as granting any right, by implication or otherwise, for the manufacture, sale, or use of any method, apparatus, or product covered by letters patent. Neither should anything contained in the publication be construed as insuring anyone against liability for infringement of letters patent.

Generally, API publications are reviewed and revised, reaffirmed, or withdrawn at least every 5 years. Sometimes a one-time extension of up to two years will be added to this re- view cycle. This publication will no longer be in effect 5 years after its publication date as an operative API publication or, where an extension has been granted, upon republication. Status of the publication can be ascertained from the API Authoring Department [telephone (214) 953-1 1011. A catalog of API publications and materials is published annually and updated quarterly by API, 1220 L Street, N.W., Washington, D.C. 20005.

This document was produced solely for the purpose of disseminating technical information, and is not an API standard. Questions concerning the interpretation of the content of this document or comments and questions concerning the procedures under which this document was developed should be directed in writing to the director of the Exploration and Production Department, American Petroleum Institute, 1220 L Street, N.W., Washing- ton, D.C. 20005. Requests for permission to reproduce or translate all or any part of the material published herein should also be addressed to the director.

API technical reports may be used by anyone desiring to do so. Every effort has been made by the Institute to assure the accuracy and reliability of the data contained in them; however, the Institute makes no representation, warranty, or guarantee in connection with this publication and hereby expressly disclaims any liability or responsibility for loss or damage resulting from its use or for the violation of any federal, state, or municipal regulation with which this publication may conflict.

API technical reports are published to facilitate the broad availability of the information contained therein. These documents are not intended to obviate the need for applying sound engineering judgment regarding when and where this information should be utilized. The formulation and publication of API technical reports is not intended in any way to inhibit anyone from using any other data, information, or practices.

Copyright O 1995 American Petroleum Institute



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A P I BULLrbAF 95 0732270 O546304 T T B

CONTENTS Page

INTRODUCTION AND SCOPE . . . . . . . . . . . . . . . . . . . . . , , , . . . . . . . . . . . . i REFERENCES . . . . . . . . , . . . . . , . . . . . . . , . . . . . . . . . . . . . . . . . . . . . . . . . . . 1 INSTRUCTIONS FOR USING RATING CHARTS . . . . . . . . . . . . . . . . . . . . . 1

3.2 Use of Rating Charts . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 1 3.2.4 Example No. 1 2 3.2.5 Example No. 2 . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 2 Discussion of Results with Bolt Mak 2

2

1

2

3 3. i Description of Rating Charts . . . . . . . . . . . . . . . . . . . . . . . . . . 1

. . . . . . . . . . . . , . . . . . . . . . . . . . . . . . . . , . . . . . . .

3.3 Stress = 40,000 psi . . . . . . . . . . . . . . . . . . . , , . . . . . . . . . . . . . . . . . . . , . . . . . . . . . . . . . . 4 RATING CHARTS

Figures 1-Typical Combined Load Capacity Results . . . . . . . . . . . . . , . . . . . . . . , . . . . 4 2-Load Capacity Results to Use with Example Problems . . . . . . . . . 5

Tables 1-API Properties and Material Types . . . . . . . . . . . . . . . . . . . . . . . . . . . 2-Flanges Not Meeting ASME Stress Allowables for Makeup Load Case . . . . 3

Rating Charts 21/16 in. 2,000 psi API 6B Flange 2/16 in. 2,000 psi API 6B Flange 3l/x in. 2,000 psi API 6B Flange . . . . . . . . . . . . . . . . . . , , . . . . . . . . . . . . . . .

7I/16 in. 2,000 psi API 6B Flange Y in. 2,000 psi API 6B Flange . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11 in. 2,000 psi API 6B FI 13Vx in. 2,000 psi API 6B Flange . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

2 i l/4 in. 2,000 psi API 6B 21/10 in. 3,000 psi API 6B Flange 2Y/16 in. 3,000 psi API 6B Flan

4I/16 in. 3,000 psi API 6B Flange l/lh in. 3,000 psi API 6B Flange 9 in. 3,000 psi API 6B Flange . . . . . . . . . . . . . . . . . . . . . . . . . . . .

13% in. 3,000 psi API 6B Flange . . . . . . . . . . . . . . . . . . . . . . . . . 163/4 in. 3,000 psi API 6B Flang 203/4 in. 3,000 psi API 6B 2l/16 in. 5,000 psi API 6B Fiang

31/x in. 5,000 psi API 6B Flange . . . . . . . . . . . . . . . . . . . . . . . . . . 4I/1 in. 5,000 psi API 6B Fiang 71/16 in. 5,000 psi API 6B

i i in . 5,000 psi API 6B Flange

26V4 in. 3,000 psi API 6B 13% in. 5,000 psi API 6B

18V4 in. 5,000 psi API 6BX Flange

. . . . . , . . . . . . . . . . . . . . . . . . . . . .

. . . . . , . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

4I/16 in. 2,000 psi API 6B Flange . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

16V4 in. 2,000 psi API 6B . . . . . . . . . . .

. . . .

31/x in. 3,000 psi API 6B Flange . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

11 in. 3,000 psi API 6B Flange . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .

2y/~6 in. 5,000 psi API 6B Fiang . . . . . . . . . . . . . . . . . . . . < . . . . .

9 in. 5,000 psi API 6B Flange

26V4 in. 2,000 psi API 6B

16V4 in. 5,000 psi API 6BX Flange

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

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

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

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

6 7 8 9

10 I I 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37

111



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A P I BULL*bAF 95 m 0732290 0546305 934 m

21% in . 5. 000 psi API 6BX Flange 113/16 in . 10. 000 psi API 6BX Flange 21/16 in . 10. 000 psi API 6BX Flange 29/16 in . 10. O00 psi API 6BX Flange 31/16 in . 10. O00 psi API 6BX Flange 41/16 in . 10. 000 psi API 6BX Flange 51/x in . 10. 000 psi API 6BX Flange 7I/16 in . IO. 000 psi API 6BX Flange 9 in . 10. 000 psi API 6BX Flange I I in . 10. O00 psi API 6BX Flange 13% in . 10. O00 psi API 6BX Flange 16% in . 10. O00 psi API 6BX Flange 18V4 in . IO. 000 psi API 6BX Flange 2 I 1/4 in . 10. 000 psi API 6BX Flange 1 1 V 1 6 in . 15. 000 psi API 6BX Flange 2l/16 in . 15. 000 psi API 6BX Flange 2V1 in . 15. O00 psi API 6BX Flange 3l/16 in . 15. 000 psi API 6BX Flange 41/16 in . 15. 000 psi API 6BX Flange 7V16 in . 15. O00 psi API 6BX Flange 9 in . 15. 000 psi API 6BX Flange

13% in . 15. O00 psi API 6BX Flange i 8V4 in . 15. 000 psi API 6BX Flange l l V 1 6 in . 20. O00 psi API 6BX Flange 2I/16 in . 20. 000 psi API 6BX Flange 2

A P I BULLrhAF 95 m 0732290 0 5 4 6 3 0 6 870 m

FOREWORD

This technical report is under the jurisdiction of the API Subcommittee on Valves and Wellhead Equipment. The report was first issued as API Bulletin 6AF, First Edition, April 1, 1989, and was reaffirmed and reissued in 1995 as a technical report designated API 6AF.

This document was produced solely for the purpose of disseminating technical information and is not an API standard. API publications may be used by anyone desiring to do so. Every effort has been made by the Institute to assure the accuracy and reliability of the data contained in them; however, the Institute makes no representation, warranty or guarantee in connection with this publication and hereby expressly disclaims any liability or responsibility for loss or damage resulting from its use or for the violation of any federal, state, or municipal regulation with which this publication may conflict.

Suggested revisions are invited and should be submitted in writing to the director of the Exploration and Production Department, American Petroleum Institute, 1220 L Street, N.W., Washington, D.C. 20005.

This documents shall become effective on the date printed on the cover but may be used voluntarily form the date of distribution.



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A P I BULLNcbAF 95 0732290 054b307 707


1 Introduction and Scope This technical report presents the results of analysis work

done in PRAC 86-21 to establish the load capacity of all flanges given in the April 1986 Editions of API 6A and 6AB. A total of 69 different geometries were analyzed. The various loads considered were:

Bolt makeup (preload). Internal pressure. Tension. Bending moment.

All 69 flanges were analyzed with an axisymmetric finite element model for each of the four load cases. A post-pro- cessor program was written to calculate the maximum moment capacity for various levels of pressure and tension, based on linear superposition of results. Three different criteria were used to establish the maximum moment:

1. ASME Section VIII, Division 2 allowable stress cat- egories for the flange with the basic membrane stress allowable established by APL 2. Allowable bolt stresses as established by API. 3. Loss of preload on the ring joint. The results of this post-processing are presented in plots of pressure vs. allowable moment for various tension levels in Section 4.

There are several limitations to this work which should be understood. First, the effects of transverse shear or torsion were not considered in the analysis. Second, the results are for static loading only. No dynamic, fatigue, or fretting phe- nomena were considered in these results. Third, no thermal stresses or elevated temperature effects were considered for this Bulletin. Finally, these charts are not intended to replace a critical evaluation of any particular connection in an application where the charts show the flange to be marginal. The charts are intended to be used only as general guidelines for design.

2 References This technical report references the following documents:

Capabilities of API Flanges Under Combination of Load- ing PRAC 86-21, by K.C. Walker and Joe R. Fowler, Stress Engineering Services, Inc., report prepared for API, October 1987. Specification for Wellhead and Christmas Tree Equipment, Fifteenth Edition, April 1, 1986.

Spec 6A

As a convenience for reference, Table 1 of this technical report presents requirements for body, bonnet, and flange physical properties and material types from API Specifica- tion 6A, Fifteenth Edition.

3 Instructions for Using Rating Charts 3.1 DESCRIPTION OF RATING CHARTS

3.1.1 The plotted results for the combined load capacity of each flange analyzed in this project are given in Section 4. The results are arranged in the same order as found in API 6A. The 6B flanges are first, followed by 6BX flanges. For each flange style the results are given in order of increasing diameter within each working pressure rating. (Thus, the 211/4 in. 2,000 psi 6B flange is before the 21/16 in. 3,000 psi 6B flange; and the 11 in. 5,000 psi 6B flange is before the 26V4 in. 2,000 psi 6BX flange.) Combined load ratings were determined for each flange with two different bolt makeup stresses. The first rating was determined for bolts made up to 52.5 ksi, and the second was done for a makeup stress of 40 ksi. The two plots are given on the same page to help evaluate the effect of a reduced preload on a flanges bending capacity.

3.1.2 The combined load rating for all flanges was plotted even if the stress criteria were exceeded for makeup and/or hydrostatic test pressure load cases. There were only four flanges that did not meet these criteria (Table 2). These flanges all failed to meet the criterion for an extreme fiber (membrane plus bending) stress at a section in the hub im- mediately behind the back of the flange for a bolt makeup of 52.5 ksi. Until these overstressed flanges are modified, it is recommended that the user consider derating the flanges to an appropriate level.

3.2 USE OF RATING CHARTS

3.2.1 An explanation of the proper use of the plotted results in Section 4 is given below. Also, a procedure to use in evaluating a flange for a particular combination of loads is outlined to aid those who will be using these results. Figure 1 is reproduced for the 3 I / i h in. 10,000 psi 6BX flange for reference in the discussion below.

3.2.2 The plotted results given in Section 4 show limiting load combinations of makeup, pressure, tension, and moment. The results are based on the stress criterion or leak criterion that controls at each load combination. As a result, some curves have a knee in them when the controlling criterion changes from a stress limitation to a leak limitation. This can be seen in Figure 1.

1



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2

3.2.3 The steps outlined below are provided to simplifj the use of the curves to evaluate a particular flange.

3.2.3.1

a. Boit makeup stress (52.5 ksi or 40 ksi). b. Pressure (psi). c. Tension (lb). d. Moment (ft-lb). Note: Remember, the pressure load condition includes the tension due to the pressure end load, so if no other tensile loads are present, the tension = O lb curve should be used.

Establish magnitude of each load condition:

3.2.3.2 Determine Flange Load Capacity

a. Pick the appropriate rating chart based on makeup desired. b. Enter the rating chart from left side with pressure. c. Move to right to find required moment. d. Intersection is point that defines maximum tension rating. e. Interpolate between lines to get maximum tension rating.

3.2.3.3 Evaluation

a. If the maximum tension rating is greater than the required tension, the flange is satisfactory for the intended use based on the axisymmeic analyses. b. If the maximum tension rating is less than the required tension, the flange cannot carry the desired load combination based on the axisymmetric analyses. The pressure, tension, or moment will have to be reduced, or in some cases increasing the bolt makeup from 40 ksi to 52.5 ksi will help. If these changes are not acceptable, a more refined stress analysis will be required.

3.2.4 Example No. 1

Using the 31/16 in. 10,000 psi 6BX flange as an example, check the load rating for the following combination of loads:

a. b. Pressure = 10,OOO. c. Tension = O lb. d. Moment = 5,000 kip-ft.

this pressure/moment combination is:

Bolt makeup stress = 52.5 ksi.

Reading from Figure 2, the maximum tension rating for

Maximum tension rating = 6 1 ,000 lb

Since the required tension is O lb, the flange is okay.

3.2.5 Example No. 2

For the same flange, check the following combination:

a. Bolt Makeup Stress = 52.5 ksi. b. Pressure = 8,000 psi. c. Tension = 80,000 lb. d. Moment = 15,000 ft-lb.

this pressure/moment combination is: Reading from Figure 2, the maximum tension rating for

Maximum tension rating = 15,000 lb

Since the required tension is 80,000 lb, the flange is not adequate for this application. Possible lower combinations are:

a. Reduced Tension:

Pressure = 8,000 psi. Tension = 15,000 lb. Moment = 15,000 ft-lb.

b. Reduced Moment:

Pressure = 8,ooO psi. Tension = 80,000 lb. Moment = 7,500 ft-lb.

c. Reduced Pressure:

Pressure = 1,800 psi. Tension = 80,000 lb. Moment = 15,000 ft-lb.

3.3 DISCUSSION OF RESULTS WITH BOLT MAKEUP STRESS = 40,000 PSI

Ten of the 10,000 and 15,000 API 6BX do not have the capacity of rated pressure with a bolt makeup stress of 40,000 psi. This applies when bolts with a yield strength of 80 ski are used.

Table XC1 of API Spec 6A, Fifteenth Edition, indicates that these bolts are only applicable to 5,000 psi flanges less than 13/8 in. diameter, 10,000 psi flanges less than 41/16 in. diameter, and to 15,000 psi flanges less than 2%6 in. diameter. The results of Section 4 show that this caution is warranted yet slightly conservative, since several of the flanges in ques- tion do have adequate pressure capacity with 80 ksi bolting.

4 Rating Charts Refer to Pages 6-76.



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A P I BULLxhAF 95 0732290 O546309 58T

TECHNICAL REPORT ON CAPABILITIES OF API FLANGES UNDER COMBINATIONS OF LOAD 3

Table 1-API Physical Properties and Material Types (See Note)

API Material Property Requirements Bodies, Bonnets, and Flanges (PSL 1-4)

API Material 0.2% Yield Strength, Tensile Strength, Elongation in 2 in., Reduction in Area, Designation Minimum (psi) Minimum (psi) Minimum (46) Minimum (I)

36K 36,000 70,000 22 No requirement 45K 45,000 70,000 19 32 60K 60,000 85,000 18 35 75K 75,000 95,000 18 35

API Material Applications for Bodies, Bonnets, and Flanges (PSL 14)

Pressure Ratings (psi)

1 ,000 2,000 3,000 5.000 10,000 15,000 20,000

part API Material Designation

Body:" bonnet NA 36K, 45K, 36K, 45K. 36K, 45K 36K, 45K 45K, 60K, 60K, 75K

Integral end

60K. 75K 60K, 75K 60K, 75K 60K, 75K 75K

connection Use 7 5 K 4 - these. Flanged NA 60K 60K 60K 60K 75K

Threaded NA 60K 60K 60K NA NA NA

Independent 36K, 4SK. 36K. 45K, screwed wellhead 60K, 75K 60K, 75K NA NA NA NA NA equipment

Loose flanges Weld neck NA 45K 45 K 45K 60K 75K 75K Blind NA 60K 60K 60K 60K 75 K 75K Threaded NA 60K 60K 60K NA NA NA

Note: From API Specification 6A, Fifteenth Edition, April 1, 1986, Tables V DI and V D2. "Provided end connections are of the API material designation indicated, welding is done in accordance with Section Vi and design is performed in accordance with Section III.

Table 2-Flanges Not Meeting ASME Stress Allowables for Makeup Load Case (See Note)

(1) (2) (3) (4)

Stress Intensity (psi)

Size Location FEA Allowable

13% in. 2,000 psi 6B

16% in. 2,000 psi 6B

2 1% in. 2,000 psi 6B

135/~ in. 3,000 psi 6B

ID of hub OD of hub

ID of hub OD of hub

ID of hub OD of hub

ID of hub OD of hub

65,909 61,846

67,057 65,032

62,824 60.994

65,373 60,O6

60,000 60,000

60,000 60,000

60,000 60,000

60,000 60,000

Note: Bolt makeup stress = 52.5 ksi.



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A P I BULL*hAF 95 0732290 054b3LO 2TL W

API 6AF 4

DSI

Figure 1 -Typical Combined Load Capacity Results



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2h6 IN. 2,000 PSI API 6B FLANGE Bore Pressure versus Bending Moment with Tension

Bolt makeuD stress = 52,500 Dsi

4.00 6.00 8.00 10.00 Bending Moment (Thousand ft-lb)



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API B U L L U b A F 95 = 0732290 0.546333 TOO

TECHNICAL REPORT ON CAPABILITIES OF APL FLANGES UNDER COMBINATIONS OF LOAD 7

2 % ~ IN. 2,000 PSI API 6B FLANGE Bore Pressure versus Bending Moment with Tension

= 52,500 psi

Bending Moment (Thousand ft-lb)

Bolt makeup stress = 40,000 psi




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A P I BULL*bAF 95 0732290 0546334 947

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TECHNICAL REPORT ON CAPABILITIES OF API FLANGES UNDER cOMSlNATlONS OF LOAD

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A P I BULL*bAF 95 O732290 0.546323 087


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A P I BULLtbAF 95 O732290 0596322 TL3 m

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A P I B U L L * h A F 75 0732290 0546323 75T

17 TECHNICAL REPORT ON CAPABILITIES OF API FLANGES UNDER COMBINATIONS OF LOAD

29/16 IN. 3,000 PSI API 6B FLANGE Bore Pressure versus Bending Moment with Tension

Bolt makeur, stress = 52,500 psi



Bending Moment (Thousand f-lb)



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A P I B U L L * b A F 95 = 0732290 CI546324 896

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A P I B U L L s b A F 95 W 0732290 054b325 722 W

TECHNICAL REPORT ON CAPABILITIES OF API FLANGES UNDER COMBINATIONS OF LOAD

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20 API 6AF




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A P I BULL*bAF 95 = 0732290 0546327 5T5


Y

O

9 IN. 3,000 PSI API 66 FLANGE Bore Pressure versus Bending Moment with Tension


\

\ \ \ \

\

\

\

\

50.00 100.00 150.00 200.00 250.00 Bending Moment (Thousand it-lb)

50.00 100.00 150.00 200.00 250.00 Bending Moment (Thousand fi-lb)



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API BULL*bAF 95 0732290 0546328 43L =

22 APi 6AF





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~~

A P I BULLxbAF 95 m 0732290 0546329 378 m


135/s IN. 3,000 PSI API 68 FLANGE Bore Pressure versus Bending Moment with Tension




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A P I BULL*bAF 95 W O732290 0546330 09T

24 API 6AF





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A P I BULL*bAF 95 = 0732290 0546333 T2b


20% IN. 3,000 PSI API 66 FLANGE Bore Pressure versus Bending Moment with Tension

Bolt makeuD stress = 52.500 Dsi

" O 0.50 1 .o0 1.50

Bending Moment (Million ft-lb) 2.00

Bending Moment (Million ft-lb)



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A P I BULLshAF 95 M 0732290 0546332 962 = 26 API 6AF

2'k6 IN. 5,000 PSI API 6B FLANGE Bore Pressure versus Bending Moment with Tension

20.00 25.00


"O 5.00 10.00 15.00 20.00 25.00 Bending Moment (Thousand fi-lb)



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A P I BULL*bAF 95 = 0732290 0546333 T 9 = TECHNICAL REPORT ON CAPABILITIES OF API FLANGES UNDER COMBINATIONS OF LOAD 27

29/16 IN. 5,000 PSI API 6B FLANGE Bore Pressure versus Bending Moment with Tension

Bolt rnakeuD stress = 52.500 Dsi

O



40.00




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A P I B U L L * b A F 95 0732290 054b334 735

28 API 6AF

5000

4000

3 v 2 3000 2

?! n

m

3 u> cn

g 2000

1 O00



O 10.00 20.00 30.00 Bending Moment (Thousand ft-lb)

40.00




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A P I BULL*bAF 95 H 0732290 0546335 671 H


u) P v

?!

2 n 2 m

3 u) u)

O

Bolt makeup stress = 52,500 psi u I 41/16 IN. 5,000 PSI API 6B FLANGE

Bore Pressure versus Bending Moment with Tension

20.00 40.00 60.00 80.00 Bending Moment (Thousand fi-lb)


O O

1 80.00




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A P I BULLmbAF 95 W 0732290 0546336 508

30 API 6AF

7 l h IN. 5,000 PSI API 6B FLANGE Bore Pressure versus Bending Moment with Tension

'ooolI!JII n




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~ ~~

API BULLxbAF 95 m 0732290 0546338 380

API 6AF 32



O 200.00 400.00 600.00 800.00 Bending Moment (Thousand it-lb)



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A P I BULL*bAF 95 0732290 O546339 217


26% IN. 2,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension

Boit makeur, stress = 52.500 Dsi

2.00 u 'O

Boit makeup stress = 40,000 psi

I 30

Bending Moment (Million ft-ib)



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A P I BULL*bAF 95 m 0732290 0546340 T39 m

34 API 6AF


Bending Moment (Million fi-lb)



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A P I BULLabAF 95 H 0732290 0546343 975 H



Bolt makeuo stress = 52,500 psi


Bolt makeuo stress = 40,000 psi

800.00 Bending Moment (Thousand fi-lb)



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A P I BULLxbAF 95 0732290 05Vb3Y2 B O L

36 API 6AF

16V4 IN. 5,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension



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A P I BULL*6AF 95 0732290 0546343 748




Bolt makeup stress = 40,000 psi 50001 I l \ l I I I I I I I I I I I

Bending Moment (Million t-ib)



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A P I B U L L * b A F 95 O732290 0546344 684

38 API 6AF





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~~

A P I EULL*bAF 95 0732290 0546345 510 =

TECHNICAL REPORT ON CAPAEILITIES OF APL FLANGES UNDER COMBINATIONS OF LOAD 39

113/is IN. 10,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension

O 1 .o0 2.00 3.00 Bending Moment (Thousand f-lb)

Bolt makeuo stress = 40,000 os

4.00

I I I 1

\

\

5.00



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API BULL*bAF 95 m 0732290 05463Yb Y57 m

40 API 6AF

2I/i6 IN. 10,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension

\ cp O I I I

\ \

\ \

\

\ \ \ \

2.00 4.00 6.00 Bending Moment (Thousand t-lb)

8.00




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A P I BULL*bAF 95 U O 7 3 2 2 9 0 0 5 4 6 3 4 7 393

TECHNICAL REPORT ON CAPAlLlTlES OF API FLANGES UNDER COMBINATIONS OF LOAD 41

29/16 IN. 10,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension

Bolt makeup stress = 52,500 psi 1 O000

8000

?! a

?! n

u) u)

4000 m

2000

O O






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A P I BULL*bAF 95 M 0732290 054b346 22T M

42 API 6AF

3116 IN. 10,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension




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A P I B U L L r L A F 95 0732290 0546349 166 m


4%6 IN. 10,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension


loooo -

O 10.00 Bending Moment (Thousand ft-lb)



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A P I BULL*bAF 95 = 0732290 05Yb350 966 W

44 API 6AF





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A P I BULLUbAF 95 O732290 0546351 814


7?116 IN. 10,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension




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A P I B U L L r b A F 95 0732290 0546352 750

46 API 6AF



L 40 Bending Moment (Thousand ft-lb)



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A P I BULLmSAF 95 = 0732290 0546353 b97 47 TECHNICAL REPORT ON CAPABILITIES OF API FLANGES UNDER COMBINATIONS OF LOAD


Bolt makeua stress = 40,000 psi




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API BULL*bAF 95 0732290 0546354 523

Bolt makeup stress = 52,500 psi I I

- - -

- - -

- ~

-

- - -

- - - - -

O I I I I I I I 1 I I f O 0.50 1 .o0 1.50

48 API 6AF


l o o o 0 a

O 1.50 Bending Moment (Million ft-lb)



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A P I BULLxbAF 95 M 0732270 0546355 4bT M



Bolt makeup stress = 52,500 psi 1 O000

8000

A b 6000 E a t n

m -

Y

a a - -

4000 - - - -

2000 - - -

O 0.50 1 .o0 1.50 2.00 O





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A P I B U L L x h A F 95 0732290 0546356 3Tb

50 API 6AF



O 1 .o0 2.00 3. Bending Moment (Million ft-lb)



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A P I BULLxhAF 95 0732290 0 5 4 6 3 5 7 232



Bending Moment (Million fi-lb)



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A P I B U L L * b A F 95 0732290 0546358 179 m

52 API 6AF

ll%s IN. 15,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension



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API BULLmhAF 95 0732290 0546357 005 =


2l/is IN. 15, PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension


g 6000 m

3000r O 5.00 10.00 1 0-



- IO i O0

I

O0 Bending Moment (Thousand ft-lb)



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A P I BULLxbAF 95 m 0732290 0546360 827

54 API 6AF


Bolt makeup stress = 52,500 psi 15000

12000

e M n 9000 E a m m E n

m

v

6000

3000

O O 5.00 10.00 15.00 20.00 25.00 30.00


O 5.00 10.00 15.00 20.00 25.00 30.00 Bending Moment (Thousand ft-lb)



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A P I BULL*bAF 95 = O732290 054b3b3 763


3% IN. 15,000 PSI APi 6BX FLANGE Bore Pressure versus Bending Moment with Tension

Bending Moment (Thousand f-ib)



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A P I B U L L x b A F 95 W 0732290 0546362 bTT W

56 API 6AF

4'hS IN. 15,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension




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A P I BULLahAF 95 W O732290 0546363 536 W


71/is IN. 15,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension


12000

E 9000 v

6000 m

3000

15000

12000

O



300C

C O0 40 - O0 E 1.00

Bending Moment (Thousand t-lb)



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A P I BULL*bAF 95 M 0732290 0546364 472 M

58 API 6AF

15000

12000

3000

O

15000

12000

6000 m

300C

c


Bolt rnakeur, stress = 52.500 mi


LOO



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A P I BULLahAF 95 m 0732290 0546365 309 m



Bending Moment (Million R-lb)




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A P I BULL*bAF 95 m 0732290 054b3bb 245 m

60 API 6AF




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A P I BULLMbAF 95 = O732290 0 5 4 b 3 b 7 181




- -

O 1 .o0 2.00 3.00 4.00 Bending Moment (Million f-lb)

Bolt makeuo stress = 40.000 DS

Bending Moment (Million f-lb)



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API BULLxbAF 95 m O732290 05q636 018 m

62 API 6AF

1 %e IN. 20,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension

Bolt makeup stress = 52.500 Dsi




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A P I BULL*hAF 95 m 0732290 0546369 T 5 4 m


2he IN. 20,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension

Bolt rnakeui, stress = 52,500 psi

63






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A P I BULL*bAF 75 m O732290 05Lib370 776

64 API 6AF






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~~

A P I BULLmbAF 75 = O732290 0 5 4 6 3 7 3 602


3'116 IN. 20,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension


Bolt makeuD stress = 40.000 DS

" O 50.00 11 Bending Moment (Thousand ft-lb)



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66

~ ~~ ~~

A P I B U L L * b A F 95 0732290 O546372 549

API 6AF

4'116 IN. 20,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension



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A P I B U L L g b A F 95 0732290 O546373 485 W


iih IN. 20,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension


1.20



.o0 1.20




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A P I BULLmbAF 95 0732290 0546374 3 1 1

68 API 6AF


Bending Moment (Million it-lb)



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A P I B U L L a b A F 95 O732290 0546375 258



K 20000

Bending Moment (Million t-lb)


"O 0.50 1 .o0 1.50 2.00 2.50 Bending Moment (Million it-lb)



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A P I BULL*bAF 95 = 0732290 0546376 1 9 4 70 API 6AF


Bolt makeup stress = 52,500 psi I l I I I l I I

- - - -

- -

-

- - - -

o I l I I I l I I O 1 .o0 2.00 3.00 4.00 5.00





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~

A P I BULLabAF 95 = 0732290 0546377 OZ0 W 71 TECHNICAL REPORT ON CAPABILITIES OF API FLANGES UNDER COMBINATIONS OF LOAD

i 1 3 h IN. 30,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension

Bolt makeup stress = 52,500 psi.






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____ ~ ~~

A P I BULL*bAF 95 W 0732290 05qb378 Tb7

72 API 6AF



25000

20000 .- a Q Y

5

g

8 15000 2 n

m 1 O000

5000 -

- -

- -

O I I I I I I I I I I I I -




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API EULL*bAF 95 0732290 05Lib3 T 3

TECHNICAL REPORT ON CAPABILITIES OF APi FLANGES UNDER COMBINATIONS OF LOAD


Boit makeui, stress = 40.000 psi

73

Bending Moment (Thousand f-lb)



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A P I BULLrbAF 95 0732290 05Yb380 bL5 = 74 API 6AF

3 % ~ IN. 30,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension



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A P I BULL*bAF 95 U 0732290 0546381 551 =

TECHNICAL REPORT ON CAPABILITIES OF API FLANGES UNDER COMBINATIONS OF LOAD 75 I



Boit makeup stress = 40,000 psi

Bending Moment (Thousand ft-ib)



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A P I BULL*hAF 95 = 0732290 0546382 498

76 API 6AF

7'/16 IN. 30,000 PSI API 6BX FLANGE Bore Pressure versus Bending Moment with Tension


Boit makeup stress = 40,000 psi 30000

25000

20000

$ 8 15000 E n !! m O

1 O000

5000

O O 0.50 1 .o0 1.50

Bending Moment (Million it-lb) 2.00



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~~ ~~ ~~ ~~

A P I B U L L * b A F 95 = 0732290 0546383 324 =

I-01200-EM (4E)



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ADDITIONAL COPIES AVAILABLE FROM PUBLICATIONS AND DISTRIBUTION (202) 682-8375

American Petroleum Institute 1220 L Street, Northwest

Order No. G06AF2 Copyright American Petroleum Institute Provided by IHS under license with API Licensee=PETREVEN/5969924001, User=Figuera, Guillermo


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Norma API Tr 6af

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