pig calc.pdf

286
AKTEK DESIGN DEPARTMENT DOCUMENT CODE/NO AKTEK F0406GD-TEK113R0-035-F1/IA EC 13-P113/2 HC 10.2006 IA IA 10.2006 PM Name Date Name Name Date Status Prepared, revised Checked Approved Remark, kind of revision BAYINDIR MESCİOĞLU NAZİLLİ İZMİR DOĞALGAZ İLETİM HATTI – FAZ 4 Q.L. DL-No. DCC Doc. Class AKTEK Project Name 40”-48” 600# PIG L/R TRAP Project No. 13-P113 Document No. 5465656577 Sheet / of 1-286 Revision 0 Version:00 created 03/98 File:00135r02.xls Dervied of Datasheet FA0210 Copying of this document, and giving it to others and the use or communica- tion of the contents thereof, are forbidden without express authority by LNG. Offenders are liable to the payment of damages. All rights are reserved in the event of the grant of a patent or the registration of a utility model or design. AKTEK TECHNOLOGY ENGINEERING CO.LTD PRESSURE VESSELS DIVISION. www.aktektechnology.com PRESSURE VESSEL DESIGN CALCULATIONS Item: 40"-48" 600# PIG TRAP Vessel No: TR100 Customer: TURKISH PIPELINE NATURAL GAS PETROLEUM TRANSPORTATION GOVERMENT COMPANY Contract: C-45490-R56 Designer: MECH.ENG.IHSAN AKGUN Date: Çarşamba , Eylül 20, 2006 Vessel Name: 4048_600# PIG TRAP NQA 1,2006 Edition #1, Revision 0 Dated 20-10-2006 CONTROLLED # UNCONTROLLED#

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Page 1: PIG CALC.pdf

AKTEK DESIGN DEPARTMENT DOCUMENT

CODE/NO

AKTEK F0406GD-TEK113R0-035-F1/IA EC

13-P113/2

HC 10.2006 IA IA 10.2006 PM

Name Date Name Name Date Status

Prepared, revised Checked Approved Remark, kind of revision

BAYINDIR – MESCİOĞLU NAZİLLİ İZMİR DOĞALGAZ İLETİM HATTI – FAZ 4

Q.L. DL-No. DCC Doc. Class

AKTEK Project Name

40”-48” 600# PIG L/R TRAP

Project No.

13-P113 Document No.

5465656577

Sheet / of

1-286 Revision

0

Version:00 created 03/98 File:00135r02.xls Dervied of Datasheet FA0210

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AKTEK TECHNOLOGY ENGINEERING CO.LTD PRESSURE VESSELS DIVISION.

www.aktektechnology.com

PRESSURE VESSEL DESIGN CALCULATIONS

Item: 40"-48" 600# PIG TRAP

Vessel No: TR100

Customer: TURKISH PIPELINE NATURAL GAS PETROLEUM TRANSPORTATION GOVERMENT COMPANY

Contract: C-45490-R56

Designer: MECH.ENG.IHSAN AKGUN

Date: Çarşamba , Eylül 20, 2006

Vessel Name: 4048_600# PIG TRAP

NQA – 1,2006

Edition #1, Revision 0 Dated 20-10-2006

CONTROLLED # UNCONTROLLED#

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AKTEK TECHNOLOGY ENGINEERING CO.LTD.

TURKEY

www.aktektechnology.com

PRESSURE VESSEL DESIGN CALCULATIONS

J O I N T V E N T U R E

Item: 40"-48" 600# PIG L/R TRAP

Vessel No: TR100

Customer: BAYINDIR-MESCIOGLU

Contract: C-45490-R56

Designer: MECH.ENG.IHSAN AKGUN

Date: Çarşamba , Eylü�l 20, 2006

Vessel Name: 4048_600# PIG TRAP

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INDEX 1- BASIC COVER PAGE 2- DESIGN COVER PAGE 3- INDEX 4- VIEW SOLID 5- VIEW SOLID 6- VIEW SOLID 7- VIEW SOLID 8- VIEW SOLID 9- VIEW SOLID 10- VIEW SOLID 11- VIEW SOLID 12- VIEW SOLID 13- VIEW SOLID 14- VIEW SOLID 15- REVISION HISTORY 16- Design Basic Settings Summary 17- Deficiensies Summary 18- Nozzle Schedule 19- Nozzle Summary 20- Pressure Summary 22- Thickness Summary 23- Weight Summary 24- Hydrostatic Test Summary 26 Vacuum Summary 27 MAJOR BARREL 30 TRANSITION 40 MINOR BARREL 43 ASME B16.5/16.47 Blind on Flange #35 44 Straight Flange on Ellipsoidal Head #1 47 Ellipsoidal Head #1 50 DREYN NOZZLE - Nozzle #7 (N7) 62 Flange #35 63 KICKER NOZZLE - Nozzle #1 (N1) 75 KICKER NOZZLE - Nozzle #2 (N2) 87 PIG SIGNALLER - Nozzle #8 (N8) 100 PRESSURE INDICATOR - Nozzle #4 (N4) 112 SAFETY VALVE NOZZLE - Nozzle #5 (N5) 124 VENT NOZZLE - Nozzle #2 (N2) 136 SADDLE #1 150 Seismic Code 151 Wind Code 152 Lifting Lug #1 159 Lifting Lug #2 166 NOZZLE FINITE ELEMENT ANALYSIS 167 KICKER NOZZLE-1 FINITE ELEMENT ANALYSIS 184 SAFETY VALVE NOZZLE FINITE ELEMENT ANALYSIS 201 PRESSURE INDICATOR NOZZLE FINITE ELEMENT ANALYSIS 218 VENT NOZZLE FINITE ELEMENT ELEMENT ANALYSIS 235 DREYN NOZZLE FINITE ELEMENT ANALYSIS 252 KICKER NOZZLE-2 FINITE ELEMENT ANALYSIS 268 PIG SIGNAL FINITE ELEMENT ANALYSIS

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1.1.1.1 Revision History

No. Date Operator Notes

0 9/20/2006 IHSAN AKGUN FOR APPROVED

1

2

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1.1.1.2 Design Basic Settings Summary

1.1.1.3 Units: English 1.1.1.4 Datum Line Location: 0,00" from right seam 1.1.1.5 Design

ASME Section VIII Division 1, 2004 Edition

Design or Rating: Get Thickness from Pressure

Minimum thickness: 1/16" per UG-16(b)

Design for cold shut down only: No

Design for lethal service (full radiography required): No

Design nozzles for: Design P, find nozzle MAWP and MAP

Corrosion weight loss: 100% of theoretical loss

UG-23 Stress Increase: 1,20

Skirt/legs stress increase: 1,0

Minimum nozzle projection: 6,0000"

Yes

Preheat P-No 1 Materials > 1,25" and <= 1,50" thick: No

Pipe under-tolerance is not applied to cylindrical shell thicknesses. Pipe under-tolerance is not applied to nozzle wall thicknesses. Butt welds are tapered per Figure UCS-66.3(a).

1.1.1.6 Hydro/Pneumatic Test

Shop Hydrotest Pressure: 1,3 times vessel MAWP

Test liquid specific gravity: 1,00

Field Hydrotest Pressure: 1,3 times design P

Wind load present @ field: 33% of design

Maximum stress during test: 90% of yield

1.1.1.7 Code Interpretations

Apply interpretation VIII-1-83-66: Yes

Apply interpretation VIII-1-86-175: Yes

Apply interpretation VIII-1-83-115: Yes

Apply interpretation VIII-1-01-37: Yes

Disallow UG-20(f) exemptions: No

1.1.1.8 UG-22 Loadings

UG-22 (a) Internal or External Design Pressure : Yes

UG-22 (b) Weight of the vessel and normal contents under operating or test conditions: Yes

UG-22 (c) Superimposed static reactions from weight of attached equipment (external loads): No

UG-22 (d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: Yes

UG-22 (f) Wind reactions: Yes

UG-22 (f) Seismic reactions: Yes

Note: UG-22 (b),(c) and (f) loads only considered when supports are present.

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1.1.1.9 Deficiencies Summary

No deficiencies found.

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1.1.1.10 Nozzle Schedule

Nozzle mark

Service Size

Materials

Nozzle Impact Norm Fine Grain

Pad Impact Norm Fine Grain

Flange

N1 KICKER NOZZLE - Nozzle #1

14" Sch 160

SA-106 B Smls pipe

No No No API 5L X65 (user defined)

No No No WN A105 600#

N2 VENT NOZZLE - Nozzle #2

2" XX Heavy

SA-106 B Smls pipe

No No No API 5L X65 (user defined)

No No No WN A105 600#

N2 KICKER NOZZLE - Nozzle #2

14" Sch 160

SA-106 B Smls pipe

No No No API 5L X65 (user defined)

No No No WN A105 600#

N4 PRESSURE INDICATOR - Nozzle #4

2" XX Heavy

SA-106 B Smls pipe

No No No API 5L X65 (user defined)

No No No WN A105 600#

N5

SAFETY VALVE NOZZLE - Nozzle #5

1" XX Heavy

SA-106 B Smls pipe

No No No API 5L X65 (user defined)

No No No WN A105 600#

N7 DREYN NOZZLE - Nozzle #7

4" XX Heavy

SA-106 B Smls pipe

No No No API 5L X65 (user defined)

No No No WN A105 600#

N8 PIG SIGNALLER - Nozzle #8

2" XX Heavy

SA-106 B Smls pipe

No No No API 5L X65 (user defined)

No No No WN A105 600#

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1.1.1.11 Nozzle Summary

Nozzle mark

OD (in)

tn (in)

Req tn (in)

A1? A2?

Shell Reinforcement

Pad Corr (in)

Aa/Ar (%)

Nom t (in)

Design t (in)

User t (in)

Width (in)

tpad (in)

N1 14,00 1,4060 0,5107 Yes Yes 0,6880 0,6880 6,0000 1,0000 0,0000 103,4

N2 2,38 0,4360 0,1347 No No 0,6880 0,6880 4,0000 1,1000 0,0000 102,5

N2 14,00 1,4060 0,5107 Yes Yes 0,6880 0,6880 6,0000 1,0000 0,0000 103,4

N4 2,38 0,4360 0,1347 No No 0,6880 0,6880 4,0000 1,1000 0,0000 102,5

N5 1,32 0,3580 0,2344 No No 0,6880 0,6880 4,0000 0,6880 0,1180 115,8

N7 4,50 0,6740 0,2074 Yes Yes 0,6880 0,6880 4,0000 1,2000 0,0000 100,0

N8 2,38 0,4360 0,1347 Yes Yes 0,6880 0,6880 4,0000 1,0000 0,0000 130,4

tn: Nozzle thickness

Req tn: Nozzle thickness required per UG-45/UG-16

Nom t: Vessel wall thickness

Design t: Required vessel wall thickness due to pressure + corrosion allowance per UG-37

User t: Local vessel wall thickness (near opening)

Aa: Area available per UG-37, governing condition

Ar: Area required per UG-37, governing condition

Corr: Corrosion allowance on nozzle wall

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1.1.1.12 Pressure Summary Pressure Summary for Chamber bounded by Ellipsoidal Head #1 and ASME B16.5/16.47 Blind on Flange

#35

Identifier P

Design ( psi)

T Design

(°F)

MAWP ( psi)

MAP ( psi)

MAEP ( psi)

Te external

(°F)

MDMT Rating Total Corrosion Allowance

(in)

Impact Test MDMT

(°F) Exemption

ASME B16.5/16.47 Blind on Flange #35

1088,0 150,0 1412,86 1480,00 N/A 150,0 -40,0 Note 1, 2 0,000 No

MAJOR BARREL

1088,0 150,0 1882,81 1884,95 125,30 150,0 N/A N/A 0,000 Yes

Transition #1 1088,0 150,0 1088,00 1748,68 15,00 150,0 N/A N/A 0,000 Yes

MINOR BARREL

1088,0 150,0 2265,20 2267,20 267,63 150,0 N/A N/A 0,000 Yes

Straight Flange on Ellipsoidal Head #1

1088,0 150,0 1122,77 1124,74 549,16 150,0 -20,0 Note 4 0,000 No

Ellipsoidal Head #1

1088,0 150,0 1155,31 1157,29 541,99 150,0 -20,0 Note 3 0,000 No

Flange #35 1088,0 150,0 1412,86 1480,00 N/A 150,0 -40,0 Note 1, 2 0,000 No

Saddle #1 1088,0 150,0 1088,00 N/A N/A N/A N/A N/A N/A N/A

KICKER NOZZLE - Nozzle #1 (N1)

1088,0 150,0 1413,85 1480,00 125,30 150,0 -20,0 Nozzle Note 5

0,000 No

VENT NOZZLE - Nozzle #2 (N2)

1088,0 150,0 1415,00 1480,00 125,30 150,0 -55,0 Nozzle Note 6

0,000 No

KICKER NOZZLE - Nozzle #2 (N2)

1088,0 150,0 1413,85 1480,00 125,30 150,0 -20,0 Nozzle Note 5

0,000 No

PRESSURE INDICATOR - Nozzle #4 (N4)

1088,0 150,0 1415,00 1480,00 125,30 150,0 -55,0 Nozzle Note 6

0,000 No

SAFETY VALVE NOZZLE - Nozzle #5 (N5)

1088,0 150,0 1415,00 1480,00 125,30 150,0 -55,0 Nozzle Note 6

0,118 No

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DREYN NOZZLE - Nozzle #7 (N7)

1088,0 150,0 1398,46 1400,50 125,30 150,0 -55,0 Nozzle Note 6

0,000 No

PIG SIGNALLER - Nozzle #8 (N8)

1088,0 150,0 1414,69 1480,00 267,63 150,0 -46,5 Nozzle Note 7

0,000 No

Chamber design MDMT is -20,00°F Chamber rated MDMT is -20,00°F @ 1088,00 psi

Chamber MAWP hot & corroded is 1088,00 psi @ 150,0°F This is governed by a juncture of the transition Transition #1.

Chamber MAP cold & new is 1124,74 psi @ 70,0°F

Chamber MAEP is 15,00 psi @ 150,0°F Vacuum rings did not govern the external pressure rating.

1.1.1.13 Notes for MDMT Rating:

Note # Exemption Details

1. UCS-66(b)(1)(b)

2. Bolts rated MDMT per Fig UCS-66 note (e) = -40 °F

3. Straight Flange governs MDMT

4. Material is impact test exempt per UG-20(f) UCS-66 governing thickness = 0,688 in

5. Nozzle is impact test exempt per UG-20(f) UCS-66 governing thickness = 1 in.

6. Flange rating governs: UCS-68(c) applies. Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F

UCS-66(b)(1)(b)

7. Flange rating governs: UCS-66(b)(1)(b)

Design notes are available on the Settings Summary page.

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1.1.1.14 Thickness Summary

Component Identifier

Material Diameter

(in) Length

(in)

Nominal t

(in)

Design t

(in)

Joint E

Load

MAJOR BARREL API 5L X65 (user defined)

48,00 OD 177,00 0,6880 0,3999 1,0000 Internal

Transition #1 API 5L X65 (user defined)

40,00/48,00 OD

20,00 0,6880 0,4306 1,0000 Internal

MINOR BARREL API 5L X65 (user defined)

40,00 OD 110,00 0,6880 0,3332 1,0000 Internal

Straight Flange on Ellipsoidal Head #1

SA-516 70 40,00 OD 3,00 1,1000 1,0668 1,0000 Internal

Ellipsoidal Head #1 SA-516 70 40,00 OD 10,55 1,1000* 1,0357 1,0000 Internal

Nominal t: Vessel wall nominal thickness

Design t: Required vessel thickness due to governing loading + corrosion

Joint E: Longitudinal seam joint efficiency

* Head minimum thickness after forming

Load

internal: Circumferential stress due to internal pressure governs

external: External pressure governs

Wind: Combined longitudinal stress of pressure + weight + wind governs

Seismic: Combined longitudinal stress of pressure + weight + seismic governs

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1.1.1.15 Weight Summary

Component

Weight ( lb) Contributed by Vessel Elements

Metal New*

Metal Corroded*

Insulation &

Supports Lining

Piping +

Liquid

Operating Liquid

Test Liquid

ASME B16.5/16.47 Blind on Flange #35

7.329,00 7.329,00 0,00 0,00 0,00 0,00 0,00

MAJOR BARREL 5.057,32 5.057,32 0,00 0,00 0,00 10.994,71 10.994,66

Transition #1 569,98 569,98 0,00 0,00 0,00 1.028,06 1.028,06

MINOR BARREL 2.644,24 2.644,24 0,00 0,00 0,00 4.652,58 4.652,58

Ellipsoidal Head #1 664,64 664,64 0,00 0,00 0,00 376,73 376,73

Saddle #1 2.118,00 2.118,00 0,00 0,00 0,00 0,00 0,00

TOTAL: 18.383,18 18.383,18 0,00 0,00 0,00 17.052,08 17.052,03

* Shells with attached nozzles have weight reduced by material cut out for opening.

Component

Weight ( lb) Contributed by Attachments

Body Flanges Nozzles & Flanges Packed

Beds Trays &

Supports

Rings &

Clips

Vertical Loads

New Corroded New Corroded

ASME B16.5/16.47 Blind on Flange #35

0,00 0,00 0,00 0,00 0,00 0,00 0,00 0,00

MAJOR BARREL 2.855,00 2.855,00 1.393,15 1.392,70 0,00 0,00 47,92 0,00

Transition #1 0,00 0,00 0,00 0,00 0,00 0,00 0,00 0,00

MINOR BARREL 0,00 0,00 38,26 38,26 0,00 0,00 0,00 0,00

Ellipsoidal Head #1 0,00 0,00 0,00 0,00 0,00 0,00 0,00 0,00

TOTAL: 2.855,00 2.855,00 1.431,41 1.430,97 0,00 0,00 47,92 0,00

Vessel operating weight, Corroded: 39.769 lb

Vessel operating weight, New: 39.770 lb

Vessel empty weight, Corroded: 22.717 lb

Vessel empty weight, New: 22.718 lb

Vessel test weight, New: 39.770 lb

1.1.1.16 Vessel center of gravity location (from datum)

Vessel Lift Weight, New: 22.718 lb

Center of Gravity: 229,87"

1.1.1.17 Vessel Capacity

**The vessel capacity does not include volume of nozzle, piping or other attachments.

Vessel Capacity** (New): 2.035 US gal

Vessel Capacity** (Corroded): 2.035 US gal

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1.1.1.18 Hydrostatic Test

Shop test pressure determination for Chamber bounded by Ellipsoidal Head #1 and ASME B16.5/16.47 Blind on Flange #35 based on MAWP per UG-99(b) Shop hydrostatic test gauge pressure is 1.414,400 psi at 70,00 °F (the chamber MAWP = 1.088,000 psi) The shop test is performed with the vessel in the horizontal position.

Identifier

Local test

pressure psi

Test liquid static head psi

UG-99 stress ratio

UG-99 pressure

factor

Stress during

test psi

Allowable test

stress psi

Stress excessive?

MAJOR BARREL (1) 1.416,392 1,992 1,0000 1,30 48.697 58.500 No

Flange #35 1.416,392 1,992 N/A 1,30 NI NI NI

Transition #1 1.416,390 1,990 1,0000 1,30 51.572 58.500 No

MINOR BARREL 1.416,392 1,992 1,0000 1,30 40.462 58.500 No

Straight Flange on Ellipsoidal Head #1

1.416,377 1,977 1,0000 1,30 25.037 34.200 No

Ellipsoidal Head #1 1.416,377 1,977 1,0000 1,30 21.902 34.200 No

DREYN NOZZLE - Nozzle #7 (N7)

1.416,702 2,302 1,0000 1,30 17.493 45.933 No

KICKER NOZZLE - Nozzle #1 (N1)

1.415,753 1,353 1,0000 1,30 19.552 41.381 No

KICKER NOZZLE - Nozzle #2 (N2)

1.415,753 1,353 1,0000 1,30 19.552 41.381 No

PIG SIGNALLER - Nozzle #8 (N8)

1.414,973 0,573 1,0000 1,30 16.188 47.250 No

PRESSURE INDICATOR - Nozzle #4 (N4)

1.414,684 0,284 1,0000 1,30 18.445 46.724 No

SAFETY VALVE NOZZLE - Nozzle #5 (N5)

1.414,684 0,284 1,0000 1,30 23.967 37.124 No

VENT NOZZLE - Nozzle #2 (N2) 1.414,684 0,284 1,0000 1,30 18.445 46.724 No

Notes: (1) MAJOR BARREL limits the UG-99 stress ratio. (2) NI indicates that test stress was not investigated. (3) PL stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399, pages 77-82. (4) VIII-2, AD-151.1(b) used as the basis for nozzle allowable test stress. (5) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-most flange. The test temperature of 70,00 °F is warmer than the minimum recommended temperature of 10,00 °F so the brittle fracture provision of UG-99(h) has been met.

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Field test pressure determination for Chamber bounded by Ellipsoidal Head #1 and ASME B16.5/16.47 Blind on Flange #35 based on design P per UG-99(b) Field hydrostatic test gauge pressure is 1.414,400 psi at 70,00 °F (the chamber design P = 1.088,000 psi)

Identifier

Local test

pressure psi

Test liquid static head psi

UG-99 stress ratio

UG-99 pressure

factor

Stress during

test psi

Allowable test

stress psi

Stress excessive?

MAJOR BARREL (1) 1.416,392 1,992 1,0000 1,30 48.697 58.500 No

Flange #35 1.416,392 1,992 N/A 1,30 NI NI NI

Transition #1 1.416,390 1,990 1,0000 1,30 51.572 58.500 No

MINOR BARREL 1.416,392 1,992 1,0000 1,30 40.462 58.500 No

Straight Flange on Ellipsoidal Head #1

1.416,377 1,977 1,0000 1,30 25.037 34.200 No

Ellipsoidal Head #1 1.416,377 1,977 1,0000 1,30 21.902 34.200 No

DREYN NOZZLE - Nozzle #7 (N7)

1.416,702 2,302 1,0000 1,30 17.493 45.933 No

KICKER NOZZLE - Nozzle #1 (N1)

1.415,753 1,353 1,0000 1,30 19.552 41.381 No

KICKER NOZZLE - Nozzle #2 (N2)

1.415,753 1,353 1,0000 1,30 19.552 41.381 No

PIG SIGNALLER - Nozzle #8 (N8)

1.414,973 0,573 1,0000 1,30 16.188 47.250 No

PRESSURE INDICATOR - Nozzle #4 (N4)

1.414,684 0,284 1,0000 1,30 18.445 46.724 No

SAFETY VALVE NOZZLE - Nozzle #5 (N5)

1.414,684 0,284 1,0000 1,30 23.967 37.124 No

VENT NOZZLE - Nozzle #2 (N2) 1.414,684 0,284 1,0000 1,30 18.445 46.724 No

Notes: (1) MAJOR BARREL limits the UG-99 stress ratio. (2) NI indicates that test stress was not investigated. (3) PL stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399, pages 77-82. (4) VIII-2, AD-151.1(b) used as the basis for nozzle allowable test stress. (5) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-most flange. The test temperature of 70,00 °F is warmer than the minimum recommended temperature of 10,00 °F so the brittle fracture provision of UG-99(h) has been met.

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1.1.1.19 Vacuum Summary

Component Line of Support

Elevation above Datum

(in)

Length Le (in)

ASME B16.5/16.47 Blind on Flange #35 - 327,13 N/A

- 1/3 depth of ASME B16.5/16.47 Blind on Flange #35

319,69 N/A

MAJOR BARREL Top - 307,00 189,69

MAJOR BARREL Bottom - 130,00 189,69

Transition #1 Top - 130,00 18,33

- Transition #1 Top 130,00 18,33

- Transition #1 Bottom 110,00 18,33

Transition #1 Bottom - 110,00 18,33

MINOR BARREL Top - 110,00 116,15

MINOR BARREL Bottom - 0,00 116,15

Straight Flange on Ellipsoidal Head #1 Top

- 0,00 116,15

Straight Flange on Ellipsoidal Head #1 Bottom

- -3,00 116,15

- 1/3 depth of Ellipsoidal Head #1 -6,15 N/A

Ellipsoidal Head #1 - -13,55 N/A

Note

For main components, the listed value of 'Le' is the largest unsupported length for the component.

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1.1.1.20 MAJOR BARREL

1.1.1.21 ASME Section VIII Division 1, 2004 Edition Component: Cylinder Material specification: API 5L X65 (user defined) Pipe NPS and Schedule: 48" Sch 0,688

Not a UCS-66 material. Internal design pressure: P = 1088 psi @ 150°F External design pressure: Pe = 15 psi @ 150°F

1.1.1.22 Static liquid head: Ps = 2,1367 psi (SG=1,0000, Hs=59,1920" Operating head) Pth = 1,9923 psi (SG=1,0000, Hs=55,1920", Horizontal test head) Corrosion allowance: Inner C = 0,0000" Outer C = 0,0000" PWHT is performed Radiography: Longitudinal joint - Full UW-11(a) Type 1 Left circumferential joint - Full UW-11(a) Type 1 Right circumferential joint - Full UW-11(a) Type 1 Estimated weight: New = 5122,3491 lb corr = 5122,3491 lb Capacity: New = 1308,1883 gal corr = 1308,1883 gal

OD = 48,0000" Length Lc = 177,0000" t = 0,6880"

1.1.1.23 Design thickness, (at 150,00°F) Appendix 1-1 t = P*Ro/(S*E + 0,40*P) + Corrosion = 1090,1367*24,0000/(65000,0000*1,00 + 0,40*1090,1367) + 0,0000 = 0,3999" 1.1.1.24 Maximum allowable working pressure, (at 150,00°F) Appendix 1-1 P = S*E*t/(Ro - 0,40*t) - Ps = 65000,0000*1,00*0,6880 / (24,0000 - 0,40*0,6880) - 2,1367 = 1882,8108 psi 1.1.1.25 Maximum allowable pressure, (at 70,00°F) Appendix 1-1 P = S*E*t/(Ro - 0,40*t) = 65000,0000*1,00*0,6880 / (24,0000 - 0,40*0,6880) = 1884,9475 psi 1.1.1.26 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 189,6900/48,0000 = 3,9519 Do/t = 48,0000/0,291693 = 164,5565

From table G: A = 0,000153

From table CD-1: B = 1851,2589

Pa = 4*B/(3*(Do/t))

= 4*1851,2589/(3*(48,0000/0,291693))

=

15,0000 psi

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1.1.1.27 Design thickness for external pressure Pa = 15,0000 psi

= t + Corrosion = 0,291693 + 0,0000 = 0,2917" 1.1.1.28 Maximum Allowable External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 189,6900/48,0000 = 3,9519 Do/t = 48,0000/0,6880 = 69,7674

From table G: A = 0,000544

From table CD-1: B = 6556,4819

Pa = 4*B/(3*(Do/t))

= 4*6556,4819/(3*(48,0000/0,6880))

= 125,3017 psi

1.1.1.29 Allowable Compressive Stress, Hot and Corroded- ScHC, (table CD-1)

A = 0,125 / (Ro / t)

= 0,125 / (24,0000 / 0,6880)

= 0,003583

B = 16895,1758 psi

S = 65000,0000 / 1,0000

= 65000,0000 psi

ScHC = 16895,1758 psi

1.1.1.30 Allowable Compressive Stress, Hot and New- ScHN

ScHN = ScHC

= 16895,1758 psi

1.1.1.31 Allowable Compressive Stress, Cold and New- ScCN, (table CD-1)

A = 0,125 / (Ro / t)

= 0,125 / (24,0000 / 0,6880)

= 0,003583

B = 17052,7793 psi

S = 65000,0000 / 1,0000

= 65000,0000 psi

ScCN = 17052,7793 psi

1.1.1.32 Allowable Compressive Stress, Cold and Corroded- ScCC

ScCC = ScCN

= 17052,7793 psi

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1.1.1.33 Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CD-1)

A = 0,125 / (Ro / t)

= 0,125 / (24,0000 / 0,6880)

= 0,003583

B = 16895,1758 psi

S = 65000,0000 / 1,0000

= 65000,0000 psi

ScVC = 16895,1758 psi

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1.1.1.34 Transition #1

1.1.1.35 ASME Section VIII Division 1, 2004 Edition

Component: Transition Material specification: API 5L X65 (user defined)

Not a UCS-66 material. Internal design pressure: P = 1088,0000 psi @ 150,00°F External design pressure: Pe = 15,0000 psi @ 150,00°F

1.1.1.36 Static liquid head:

Ps = 1,9904 psi (SG=1,0000, Hs=55,1390" Operating head at small end) Ps = 1,9904 psi (SG=1,0000, Hs=55,1390" Operating head at large end) Pth = 1,9904 psi (SG=1,0000, Hs=55,1390", Horizontal test head at small end) Pth = 1,9904 psi (SG=1,0000, Hs=55,1390", Horizontal test head at large end) Corrosion allowance: Inner C = 0,0000" Outer C = 0,0000" PWHT is not performed Radiography: Category A joints - Full UW-11(a) Type 1 Circ. joint top/left - Full UW-11(a) Type 1 Circ. joint right/bottom - Full UW-11(a) Type 1 Estimated weight: New = 570,0 lb corr = 570,0 lb Capacity: New = 123,3 US gal corr = 123,3 US gal

Axial length = 20,0000" Large End OD = 48,0000" Small End OD = 40,0000" Cone tc = 0,6880"

1.1.1.37 Design thickness, (at 150,00°F) App 1-4(e) (Large End)

t = P*Do = 1089,9904*48,0000 / (2*Cos(21,801411)*(65000,0000*1,00 + 0.4*1089,9904)) + 0,0000 = 0,4306"

Small End design thickness (t = 0,3588") does not govern.

1.1.1.38 MAWP, (Corroded at 150,00°F) App 1-4(e) (Large End)

P = o - - Ps

= 2*65000,0000*1,00*0,6880*Cos(21,801411) / (48,0000 - 0,80*0,6880*Cos(21,801411)) - 1,9904

= 1746,6886 psi

Small End MAWP (2100,9504 psi) does not govern.

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1.1.1.39 MAP, (New at 70,00°F) App 1-4(e) (Large End)

P = o - - Ps

= 2*65000,0000*1,00*0,6880*Cos(21,801411) / (48,0000 - 0,80*0,6880*Cos(21,801411)) - 0,0000

= 1748,6790 psi

Small End MAP (2102,9407 psi) does not govern.

1.1.1.40 External Pressure, (Corroded & at 150,00°F) UG-33(f)

DL = 48,0000"

Le = (L/2)*(1+Ds/DL)

= (20,0000/2)*(1+40,0000/48,0000)

= 18,3333"

te = t * Cos(

= 0,110385

Le/DL = 18,3333/48,0000 = 0,3819 DL/te = 48,0000/0,110385 = 434,8400

From table G: A = 0,000406

From table CD-1: B = 4891,9722

Pa = 4*B/(3*(DL/te))

= 4*4891,9722/(3*(48,0000/0,110385))

= 15,0001 psi

1.1.1.41 Design thickness for external pressure Pa = 15,0001 psi

= te 1.1.1.42 Maximum Allowable External Pressure, (Corroded & at 150,00°F) UG-33(f) te Le/DL = 18,3333/48,0000 = 0,3819 DL/te = 48,0000/0,6388 = 75,1418

From table G: A = 0,006218

From table CD-1: B = 17974,9922

Pa = 4*B/(3*(DL/te))

= 4*17974,9922/(3*(48,0000/0,6388))

= 318,9522 psi

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1.1.1.43 % Extreme fiber elongation - User defined non-carbon steel material = (50 * t / Rf) * (1 - Rf / Ro) = (50 * 0,7410 / 19,6295) * (1 - 19 = 1,8875 %

Cone juncture large end calculations, P =1.089,990 psi (MAWP = 1.088,000 psi) Appendix 1-5(d)

Loading Area check

required

U-2(g) analysis required

f1 (lbf /in)

QL (lbf /in)

ArL (in

2)

AeL (in

2)

Ring area (in

2)

Status

Pressure No No 0,00 12.704,93 0,00 2,27 none OK

Cone large end calculations per Appendix 1-5(d), pressure, corroded f1 = -Wl m) + 12*Ml m

2)

= -2)

= 0 lb/in P*RL/2 = 12.704,93 lb/in |f1| <= P*RL/2 so a U-2(g) analysis is not required. P/(Ss*E1) = 1.089,99/(65.000,00*1) = 0,016769 From table 1-

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Cone juncture small end calculations P = 1.090,135 psi (MAWP = 1.088,000 psi) Appendix 1-5(e)

Loading Area check

required

U-2(g) analysis required

f2 (lbf /in)

Qs (lbf /in)

Ars (in

2)

Aes (in

2)

Ring area (in

2)

Status

Pressure Yes No 0,00 10.526,34 0,60 2,05 none OK

Cone small end calculations per Appendix 1-5(e), pressure, corroded f2 = -Ws m) + 12*Ms m

2)

= -2)

= 0 lb/in P*Rs/2 = 10.526,34 lb/in |f2| <= P*Rs/2 so a U-2(g) analysis is not required. P/(Ss*E1) = 1.090,135/(65.000,00*1) = 0,016771 From table 1-

Qs = P*Rs/2 + f2 = 10.526,34 + 0 = 10.526,34 lb/in Ars = (k*Qs*Rs/(Ss*E1))*(1 - = (1*10.526,34*19,312/(65.000,00*1))*(1 - 11,37/21,8014)*tan(21,8014) = 0,5985627 in

2

Aes = 0,78*(Rs*ts)

0,5*[(ts - t) + (tc - tr

= 0,78*(19,312*0,688)0,5

*[(0,688 - 0,3271798) + (0,688 - 0,3523834)/cos(21,8014)] = 2,053593 in

2

Aes >= Ars therefore the small end juncture is adequately reinforced.

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Cone large end calculations for external pressure of 15,000 psi Appendix 1-8(b)

Loading

Area check req'd

U-2(g) analysis

req'd

f1 (lbf /in)

QL (lbf /in)

ArL (in

2)

AeL (in

2)

Ring area (in

2)

Area status

I's (in

4)

I' (in

4)

I status

Vacuum Yes No 0,00 180,00 0,03 4,52 none OK 0,9041 0,9279 OK

Cone large end calculations per Appendix 1-8(b), wind + external pressure f1 = Wl m) + 12*Ml m

2)

2)

= 0 lb/in P*RL/2 = 180 lb/in f1 + P*RL/2 is in compression so a U-2(g) analysis is not required. P/(Ss*E1) = 15/(65.000,00*1) = 0,000231 From table 1-

QL = P*RL/2 + f1 = 180 + 0 = 180 lb/in ArL = (k*QL*RL s*E1))*[1 - 0,25*((P*RL-QL)/QL = (1*180*24*tan(21,8014)/(65.000,00*1))*[1 - 0,25*((15*24-180)/180)*(0,58/21,8014)] = 0,0264 in

2

AeL = 0,55*(DL*ts)

0,5*(ts + tc

= 0,55*(48*0,688)0,5

*(0,688 + 0,688/cos(21,8014)) = 4,5166 in

2

AeL >= ArL therefore the large end juncture is adequately reinforced. M = -RL L/2 + (RL

2 - Rs

2)/(3*RL

= -24*tan(21,8014)/2 + 189,69/2 + (242 - 20

2)/(3*24*tan(21,8014))

= 96,15611 Lc = (L

2 + (RL - Rs)

2)0,5

= (20

2 + (24 - 20)

2)0,5

= 20,39608 ATL = LL*ts/2 + Lc * tc/2 + As = 189,69*0,688/2 + 20,39608 * 0,688/2 + 0 = 72,26962 FL = P*M + f1 = 15*96,15611 + 0*tan(21,8014) = 1.442,342

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B = 0,75*FL*DL/ATL = 0,75*1.442,342*48/72,26962 = 718,4803 From Table CD-1: A = 0,000059 (shell, 150,00°F) I's = A*DL

2*ATL/10,9

= 5,918276E-05*482*72,26962/10,9

= 0,90408 in4

The calculated I' for the combined shell-cone cross section is 0,9279 in

4

As I' >= I's the large end is adequately stiffened per Appendix 1-8(b).

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Cone small end calculations for external pressure of 15,000 psi Appendix 1-8(c)

Loading U-2(g)

analysis req'd

f2 (lbf /in)

Qs (lbf /in)

Ars (in

2)

Aes (in

2)

Ring area (in

2)

Area status

I's (in

4)

I' (in

4)

I status

Vacuum No 0,00 150,00 0,02 3,37 none OK 0,3576 0,7311 OK

Cone small end calculations per Appendix 1-8(c), wind + external pressure f2 = Ws m) + 12*Ms m

2)

2)

= 0 lb/in P*Rs/2 = 150 lb/in f2 + P*Rs/2 is in compression so a U-2(g) analysis is not required. Qs = P*Rs/2 + f2 = 150 + 0 = 150 lb/in Ars = (k*Qs*Rs s*E1)) = (1*150*20*tan(21,8014)/(65.000,00*1)) = 1,846154E-02 in

2

Aes = 0,55*(Ds*ts)

0,5*((ts - t) + (tc - tr

= 0,55*(40*0,688)0,5

*((0,688 - 0,2133743) + (0,688 - 4,308531E-02)/cos(21,8014)) = 3,373519 in

2

Aes >= Ars therefore the small end juncture is adequately reinforced. N = Rs s/2 + (RL

2 - Rs

2)/(6*Rs*tan(

= 20*tan(21,8014)/2 + 116,15/2 + (242 - 20

2)/(6*20*tan(21,8014))

= 65,74167 Lc = (L

2 + (RL - Rs)

2)0,5

= (20

2 + (24 - 20)

2)0,5

= 20,39608 Ats = Ls*ts/2 + Lc * tc/2 + As = 116,15*0,688/2 + 20,39608 * 0,688/2 + 0 = 46,97185 Fs = P*N + f2 = 15*65,74167 + 0*tan(21,8014) = 986,125 B = 0,75*Fs*Ds/Ats = 0,75*986,125*40/46,97185 = 629,8187

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From Table CD-1: A = 0,000052 (shell, 150,00°F) I's = A*Ds

2*Ats/10,9

= 5,186052E-05*402*46,97185/10,9

= 0,35758 in4

The calculated I' for the combined shell-cone cross section is 0,7311 in

4

As I' >= I's the small end is adequately stiffened per Appendix 1-8(c).

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MAP Cone juncture large end calculations, P =1.748,679 psi Appendix 1-5(d)

Loading Area check

required

U-2(g) analysis required

f1 (lbf /in)

QL (lbf /in)

ArL (in

2)

AeL (in

2)

Ring area (in

2)

Status

Pressure No No 0,00 20.405,80 0,00 0,20 none OK

Cone large end calculations per Appendix 1-5(d), pressure, new f1 = -Wl m) + 12*Ml m

2)

= -2)

= 0 lb/in P*RL/2 = 20.405,80 lb/in |f1| <= P*RL/2 so a U-2(g) analysis is not required. P/(Ss*E1) = 1.748,679/(65.000,00*1) = 0,026903 From table 1-

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MAP Cone juncture small end calculations P = 1.748,679 psi Appendix 1-5(e)

Loading Area check

required

U-2(g) analysis required

f2 (lbf /in)

Qs (lbf /in)

Ars (in

2)

Aes (in

2)

Ring area (in

2)

Status

Pressure Yes No 0,00 16.905,86 0,70 0,82 none OK

Cone small end calculations per Appendix 1-5(e), pressure, new f2 = -Ws m) + 12*Ms m

2)

= -2)

= 0 lb/in P*Rs/2 = 16.905,86 lb/in |f2| <= P*Rs/2 so a U-2(g) analysis is not required. P/(Ss*E1) = 1.748,679/(65.000,00*1) = 0,026903 From table 1-

Qs = P*Rs/2 + f2 = 16.905,86 + 0 = 16.905,86 lb/in Ars = (k*Qs*Rs/(Ss*E1))*(1 - = (1*16.905,86*19,312/(65.000,00*1))*(1 - 14,23/21,8014)*tan(21,8014) = 0,697755 in

2

Aes = 0,78*(Rs*ts)

0,5*[(ts - t) + (tc - tr

= 0,78*(19,312*0,688)0,5

*[(0,688 - 0,5287251) + (0,688 - 0,5694544)/cos(21,8014)] = 0,8158537 in

2

Aes >= Ars therefore the small end juncture is adequately reinforced.

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1.1.1.44 MINOR BARREL

1.1.1.45 ASME Section VIII Division 1, 2004 Edition

Component: Cylinder Material specification: API 5L X65 (user defined) Pipe NPS and Schedule: 40" Sch 0,688

Not a UCS-66 material. Internal design pressure: P = 1088 psi @ 150°F External design pressure: Pe = 15 psi @ 150°F

1.1.1.46 Static liquid head:

Ps = 1,9923 psi (SG=1,0000, Hs=55,1920" Operating head) Pth = 1,9923 psi (SG=1,0000, Hs=55,1920", Horizontal test head) Corrosion allowance: Inner C = 0,0000" Outer C = 0,0000" PWHT is not performed Radiography: Longitudinal joint - Full UW-11(a) Type 1 Left circumferential joint - Full UW-11(a) Type 1 Right circumferential joint - Full UW-11(a) Type 1 Estimated weight: New = 2645,1021 lb corr = 2645,1021 lb Capacity: New = 557,9369 gal corr = 557,9369 gal

OD = 40,0000" Length Lc = 110,0000" t = 0,6880"

1.1.1.47 Design thickness, (at 150,00°F) Appendix 1-1

t = P*Ro/(S*E + 0,40*P) + Corrosion = 1089,9923*20,0000/(65000,0000*1,00 + 0,40*1089,9923) + 0,0000

= 0,3332"

1.1.1.48 Maximum allowable working pressure, (at 150,00°F) Appendix 1-1

P = S*E*t/(Ro - 0,40*t) - Ps = 65000,0000*1,00*0,6880 / (20,0000 - 0,40*0,6880) - 1,9923

= 2265,2043 psi

1.1.1.49 Maximum allowable pressure, (at 70,00°F) Appendix 1-1 P = S*E*t/(Ro - 0,40*t) = 65000,0000*1,00*0,6880 / (20,0000 - 0,40*0,6880)

2267,1968 psi

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1.1.1.50 External Pressure, (Corroded & at 150,00°F) UG-28(c)

L/Do = 116,1500/40,0000 = 2,9037 Do/t = 40,0000/0,213458 = 187,3907

From table G: A = 0,000174

From table CD-1: B = 2108,1433

Pa = 4*B/(3*(Do/t))

= 4*2108,1433/(3*(40,0000/0,213458))

= 15,0000 psi

1.1.1.51 Design thickness for external pressure Pa = 15,0000 psi

= t + Corrosion = 0,213458 + 0,0000 = 0,2135" 1.1.1.52 Maximum Allowable External Pressure, (Corroded & at 150,00°F) UG-28(c)

L/Do = 116,1500/40,0000 = 2,9037 Do/t = 40,0000/0,6880 = 58,1395

From table G: A = 0,000970

From table CD-1: B = 11669,8730

Pa = 4*B/(3*(Do/t))

= 4*11669,8730/(3*(40,0000/0,6880))

= 267,6291 psi

1.1.1.53 Allowable Compressive Stress, Hot and Corroded- ScHC, (table CD-1)

A = 0,125 / (Ro / t)

= 0,125 / (20,0000 / 0,6880)

= 0,004300

B = 17279,7852 psi

S = 65000,0000 / 1,0000

= 65000,0000 psi

ScHC = 17279,7852 psi

1.1.1.54 Allowable Compressive Stress, Hot and New- ScHN

ScHN = ScHC

= 17279,7852 psi

1.1.1.55 Allowable Compressive Stress, Cold and New- ScCN, (table CD-1)

A = 0,125 / (Ro / t)

= 0,125 / (20,0000 / 0,6880)

= 0,004300

B = 17435,6836 psi

S = 65000,0000 / 1,0000

= 65000,0000 psi

ScCN = 17435,6836 psi

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1.1.1.56 Allowable Compressive Stress, Cold and Corroded- ScCC

ScCC = ScCN

= 17435,6836 psi

1.1.1.57 Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CD-1)

A = 0,125 / (Ro / t)

= 0,125 / (20,0000 / 0,6880)

= 0,004300

B = 17279,7852 psi

S = 65000,0000 / 1,0000

= 65000,0000 psi

ScVC = 17279,7852 psi

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1.1.1.58 ASME B16.5/16.47 Blind on Flange #35

This is an ASME B16.5/16.47 rated blind flange.

Flange description: 48 inch 600# WN A105

Bolt Material: SA-193 B7 Bolt (2 1/2 < t <= 4)

Flange rated MDMT: -40 °F

(UCS-66(b)(1)(b))

(Bolts rated MDMT per Fig UCS-66 note (e) = -40 °F)

Liquid static head on flange: 2,1367 psi

ASME B16.47 flange rating MAWP: 1415 psi@ 150°F

ASME B16.47 flange rating MAP: 1480 psi@ 70°F

ASME B16.47 flange hydro test: 2225 psi@ 70°F

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1.1.1.59 Straight Flange on Ellipsoidal Head #1

1.1.1.60 ASME Section VIII Division 1, 2004 Edition

Component: Straight Flange Material specification: SA-516 70 (ASME II-D p. 14, ln. 20)

Material is impact test exempt per UG-20(f) UCS-66 governing thickness = 0,688 in Internal design pressure: P = 1088 psi @ 150°F External design pressure: Pe = 15 psi @ 150°F

1.1.1.61 Static liquid head:

Ps = 1,9774 psi (SG=1,0000, Hs=54,7800" Operating head) Pth = 1,9774 psi (SG=1,0000, Hs=54,7800", Horizontal test head) Corrosion allowance: Inner C = 0,0000" Outer C = 0,0000" Design MDMT = -20,00°F No impact test performed Rated MDMT = -20,00°F Material is not normalized Material is not produced to Fine Grain Practice PWHT is not performed Radiography: Longitudinal joint - Seamless No RT Circumferential joint - Full UW-11(a) Type 1 Estimated weight: New = 114,1301 lb corr = 114,1301 lb Capacity: New = 14,5741 gal corr = 14,5741 gal

OD = 40,0000" Length Lc = 3,0000" t = 1,1000"

1.1.1.62 Design thickness, (at 150,00°F) Appendix 1-1

t = P*Ro/(S*E + 0,40*P) + Corrosion = 1089,9774*20,0000/(20000,0000*1,00 + 0,40*1089,9774) + 0,0000 = 1,0668" 1.1.1.63 Maximum allowable working pressure, (at 150,00°F) Appendix 1-1 P = S*E*t/(Ro - 0,40*t) - Ps = 20000,0000*1,00*1,1000 / (20,0000 - 0,40*1,1000) - 1,9774 = 1122,7670 psi 1.1.1.64 Maximum allowable pressure, (at 70,00°F) Appendix 1-1

P = S*E*t/(Ro - 0,40*t) = 20000,0000*1,00*1,1000 / (20,0000 - 0,40*1,1000) = 1124,7444 psi

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1.1.1.65 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 116,1500/40,0000 = 2,9037 Do/t = 40,0000/0,201341 = 198,6675

From table G: A = 0,000156

From table CS-2: B = 2235,0144

Pa = 4*B/(3*(Do/t))

= 4*2235,0144/(3*(40,0000/0,201341))

= 15,0000 psi

1.1.1.66 Design thickness for external pressure Pa = 15,0000 psi = t + Corrosion = 0,201341 + 0,0000 = 0,2013" 1.1.1.67 Maximum Allowable External Pressure, (Corroded & at 150,00°F) UG-28(c)

L/Do = 116,1500/40,0000 = 2,9037 Do/t = 40,0000/1,1000 = 36,3636

From table G: A = 0,001989

From table CS-2: B = 14976,9785

Pa = 4*B/(3*(Do/t))

= 4*14976,9785/(3*(40,0000/1,1000))

= 549,1559 psi

1.1.1.68 % Extreme fiber elongation - UCS-79(d) = (50 * t / Rf) * (1 - Rf / Ro) = (50 * 1,1000 / 19,4500) * (1 - = 2,8278 %

1.1.1.69 Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2)

A = 0,125 / (Ro / t)

= 0,125 / (20,0000 / 1,1000)

= 0,006875

B = 17278,4180 psi

S = 20000,0000 / 1,0000

= 20000,0000 psi

ScHC = 17278,4180 psi

1.1.1.70 Allowable Compressive Stress, Hot and New- ScHN

ScHN = ScHC

= 17278,4180 psi

1.1.1.71 Allowable Compressive Stress, Cold and New- ScCN, (table CS-2)

A = 0,125 / (Ro / t)

= 0,125 / (20,0000 / 1,1000)

= 0,006875

B = 17278,4180 psi

S = 20000,0000 / 1,0000

= 20000,0000 psi

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ScCN = 17278,4180 psi

1.1.1.72 Allowable Compressive Stress, Cold and Corroded- ScCC

ScCC = ScCN

= 17278,4180 psi

1.1.1.73 Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2)

A = 0,125 / (Ro / t)

= 0,125 / (20,0000 / 1,1000)

= 0,006875

B = 17278,4180 psi

S = 20000,0000 / 1,0000

= 20000,0000 psi

ScVC = 17278,4180 psi

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.74 Ellipsoidal Head #1

1.1.1.75 ASME Section VIII, Division 1, 2004 Edition

Component: Ellipsoidal Head

Material Specification: SA-516 70 (ASME II-D p.14, ln. 20)

Straight Flange governs MDMT Internal design pressure: P = 1.088,00 psi @ 150 °F External design pressure: Pe = 15 psi @ 150 °F 1.1.1.76 Static liquid head: Ps= 1,9774 psi (SG=1, Hs=54,78" Operating head) Pth= 1,9774 psi (SG=1, Hs=54,78" Horizontal test head)

Corrosion allowance: Inner C = 0" Outer C = 0"

Design MDMT = -20°F No impact test performed

Rated MDMT = -20°F Material is not normalized

Material is not produced to fine grain practice

PWHT is not performed

Do not Optimize MDMT / Find MAWP

Radiography: Category A joints - Seamless No RT

Head to shell seam - Full UW-11(a) Type 1

Estimated weight*: new = 664,6 lb corr = 664,6 lb

Capacity*: new = 45,2 US gal corr = 45,2 US gal

* includes straight flange

Outer diameter = 40" Minimum head thickness = 1,1" Head ratio D/2h = 2 (new) Head ratio D/2h = 2 (corroded) Straight flange length Lsf = 3" Nominal straight flange thickness tsf = 1,1"

Insulation thk*: 0" density: 0 lb/ft3 weight: 0 lb

Insulation support ring spacing:

0" individual weight: 0 lb total weight: 0 lb

Lining/ref thk*: 0" density: 0 lb/ft3 weight: 0 lb

includes straight flange if applicable

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1.1.1.77 Results Summary The governing condition is internal pressure. Minimum thickness per UG-16 = 0,0625" + 0" = 0,0625" Design thickness due to internal pressure (t) = 1,0357" Design thickness due to external pressure (te) = 0,0986" Maximum allowable working pressure (MAWP) = 1155,308 psi Maximum allowable pressure (MAP) = 1157,286 psi Maximum allowable external pressure (MAEP) = 541,9866 psi 1.1.1.78 Design thickness for internal pressure, (Corroded at 150 °F) UG-32(d)(1) t = P*D/(2*S*E - 0,20*P) + Corrosion = 1089,977*37,8/(2*20000*1 - 0,20*1089,977) + 0 = 1,0357" The head internal pressure design thickness is 1,0357". 1.1.1.79 Maximum allowable working pressure, (Corroded at 150 °F) UG-32(d)(1) P = 2*S*E*t/(D + 0,20*t) - Ps = 2*20000*1*1,1/(37,8 +0,20*1,1) - 1,9774 = 1155,308 psi The maximum allowable working pressure (MAWP) is 1155,308 psi. 1.1.1.80 Maximum allowable pressure, (New at 70 °F) UG-32(d)(1) P = 2*S*E*t/(D + 0,20*t) - Ps = 2*20000*1*1,1/(37,8 +0,20*1,1) - 0 = 1157,286 psi The maximum allowable pressure (MAP) is 1157,286 psi. 1.1.1.81 Design thickness for external pressure, (Corroded at 150 °F) UG-33(d) Equivalent outside spherical radius (Ro) Ro = Ko*Do = 0,8531 * 40 = 34,1232 in A = 0,125 / (Ro/t) = 0,125 / (34,1232/0,098556) = 0,000361 From Table CS-2: B=5.193,4536 psi

Pa = B/(Ro/t) = 5.193,454/(34,1232/0,098556) = 15 psi t = 0,0986" + Corrosion = 0,0986" + 0" = 0,0986"

Check the external pressure per UG-33(a)(1) UG-32(d)(1)

t = 1,67*Pe*D/(2*S*E - 0,20*1,67*Pe) + Corrosion = 1,67*15*37,8/(2*20000*1 - 0,20*1,67*15) + 0 = 0,0237"

The head external pressure design thickness (te) is 0,098556".

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1.1.1.82 Maximum Allowable External Pressure, (Corroded at 150 °F) UG-33(d)

Equivalent outside spherical radius (Ro) Ro = Ko*Do = 0,8531 * 40 = 34,1232 in A = 0,125 / (Ro/t) = 0,125 / (34,1232/1,1) = 0,00403 From Table CS-2: B=16.813,0293 psi

Pa = B/(Ro/t) = 16.813,03/(34,1232/1,1) = 541,9866 psi

Check the Maximum External Pressure, UG-33(a)(1) UG-32(d)(1)

P = 2*S*E*t/((D + 0,20*t)*1,67) - Ps2 = 2*20000*1*1,1/((37,8 +0,20*1,1)*1,67) - 0 = 692,9855 psi

The maximum allowable external pressure (MAEP) is 541,9866 psi.

1.1.1.83 % Extreme fiber elongation - UCS-79(d)

= (75*t / Rf)*(1 - Rf / Ro)

= (75*1,1 / 6,976)*(1 -

= 11,8263%

The extreme fiber elongation exceeds 5 percent and the thickness exceeds 5/8 inch;. Heat treatment per UCS-56 is required if fabricated by cold forming.

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1.1.1.84 DREYN NOZZLE - Nozzle #7 (N7)

ASME Section VIII Division 1, 2004 Edition

tw(lower) = 0,6880 in

Leg41 = 1,0000 in

tw(upper) = 1,2000 in

Leg42 = 1,0000 in

Dp = 12,5000 in

te = 1,2000 in

Note: round inside edges per UG-76(c)

Located on: MAJOR BARREL

Liquid static head included: 2,0171 psi

Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5)

Nozzle longitudinal joint efficiency: 1,00

Nozzle description: 4" XX Heavy

Pad material specification: API 5L X65 (user defined)

Pad diameter: 12,5 in

Flange description: 4 inch 600# WN A105

Bolt Material: SA-193 B7 Bolt <= 2 1/2

Flange rated MDMT: -55 °F

(UCS-66(b)(1)(b))

(UCS-68(c) applies. Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F)

Liquid static head on flange: 2,3016 psi

ASME B16.5 flange rating MAWP: 1415 psi@ 150°F

ASME B16.5 flange rating MAP: 1480 psi@ 70°F

ASME B16.5 flange hydro test: 2225 psi@ 70°F

Nozzle orientation: 180 °

Local vessel minimum thickness: 0,688 in

Nozzle center line offset to datum line: 292,59 in

End of nozzle to shell center: 31,88 in

Nozzle inside diameter, new: 3,152 in

Nozzle nominal wall thickness: 0,674 in

Nozzle corrosion allowance: 0 in

Projection available outside vessel, Lpr: 7,88 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for Internal Pressure Available reinforcement per UG-37 governs the MAWP of this nozzle.

UG-37 Area Calculation Summary (in2)

For P = 1400,47 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

2,8520 2,8520 -- 0,4872 -- 2,1648 0,2000 0,2074 0,6740

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

185.379,66 185.380,00 673.859,63 60.528,34 701.145,56 201.240,34 859.292,56

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,4718 1,2000 weld size is adequate

Calculations for internal pressure 1400,47 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,15498).

Nozzle UCS-66 governing thk: 0,674 in

Nozzle rated MDMT: -155 °F

Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 3,152 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

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Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1400,474*1,576/(17100*1 - 0,6*1400,474) = 0,1357 in

tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 3,152*0,688*1 + 2*0,674*0,688*1*(1 - 0,2631) = 2,852 in

2

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 3,152*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 0,674)*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,4872 in

2

= 5*(tn - trn)*fr2*t = 5*(0,674 - 0,1357)*0,2631*0,688 = 0,4872 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(0,674 - 0,1357)*(2,5*0,674 + 1,2)*0,2631 = 0,8172 in

2

A41 = Leg2*fr3

= 0,87182*0,2631

= 0,2 in2

(Part of the weld is outside of the limits)

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A42 = Leg2*fr4

= 02*1

= 0 in2

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (6,304 - 3,152 - 2*0,674)*1,2*1 = 2,1648 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,4872 + 0,2 + 0 + 2,1648 = 2,852 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,674 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,1358 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5127 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,2074 in

The greater of tr2 or tr3: tr5 = 0,5127 in

The lesser of tr4 or tr5: tr6 = 0,2074 in

Required per UG-45 is the larger of tr1 or tr6 = 0,2074 in Available nozzle wall thickness new, tn = 0,674 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

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Strength of welded joints: (1) Inner fillet weld in shear ( i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (2,852 - 0 + 2*0,674*0,2631*(1*0,688 - 1*0,688))*65000 = 185379,7 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,4872 + 2,1648 + 0,2 + 0)*65000 = 185380 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,4872 + 0 + 0,2 + 0 + 2*0,674*0,688*0,2631)*65000 = 60528,34 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,4872 + 0 + 2,1648 + 0,2 + 0 + 0 + 2*0,674*0,688*0,2631)*65000 = 201240,3 lbf

Load for path 1-1 lesser of W or W1-1 = 185379,7 lbf Path 1-1 through (2) & (3) = 625373,3 + 48486,29 = 673859,6 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 60528,34 lbf Path 2-2 through (1), (4), (6) = 59227,66 + 233919,2 + 407998,7 = 701145,6 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 185379,7 lbf Path 3-3 through (2), (4) = 625373,3 + 233919,2 = 859292,6 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for MAP Available reinforcement per UG-37 governs the MAP of this nozzle.

UG-37 Area Calculation Summary (in2)

For P = 1400,5 psi @ 70 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

2,8520 2,8520 -- 0,4872 -- 2,1648 0,2000 0,2074 0,6740

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

185.379,66 185.380,00 673.859,63 60.528,34 701.145,56 201.240,34 859.292,56

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,4718 1,2000 weld size is adequate

Calculations for internal pressure 1400,5 psi @ 70 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 3,152 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1400,497*1,576/(17100*1 - 0,6*1400,497) = 0,1357 in

tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 3,152*0,688*1 + 2*0,674*0,688*1*(1 - 0,2631) = 2,852 in

2

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 3,152*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 0,674)*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,4872 in

2

= 5*(tn - trn)*fr2*t = 5*(0,674 - 0,1357)*0,2631*0,688 = 0,4872 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(0,674 - 0,1357)*(2,5*0,674 + 1,2)*0,2631 = 0,8172 in

2

A41 = Leg2*fr3

= 0,87182*0,2631

= 0,2 in2

(Part of the weld is outside of the limits)

A42 = Leg2*fr4

= 02*1

= 0 in2

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (6,304 - 3,152 - 2*0,674)*1,2*1 = 2,1648 in

2

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Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,4872 + 0,2 + 0 + 2,1648 = 2,852 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,674 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,1357 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5127 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,2074 in

The greater of tr2 or tr3: tr5 = 0,5127 in

The lesser of tr4 or tr5: tr6 = 0,2074 in

Required per UG-45 is the larger of tr1 or tr6 = 0,2074 in Available nozzle wall thickness new, tn = 0,674 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Strength of welded joints: (1) Inner fillet weld in shear ( i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

(6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (2,852 - 0 + 2*0,674*0,2631*(1*0,688 - 1*0,688))*65000 = 185379,7 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,4872 + 2,1648 + 0,2 + 0)*65000 = 185380 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,4872 + 0 + 0,2 + 0 + 2*0,674*0,688*0,2631)*65000 = 60528,34 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,4872 + 0 + 2,1648 + 0,2 + 0 + 0 + 2*0,674*0,688*0,2631)*65000 = 201240,3 lbf

Load for path 1-1 lesser of W or W1-1 = 185379,7 lbf Path 1-1 through (2) & (3) = 625373,3 + 48486,29 = 673859,6 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 60528,34 lbf Path 2-2 through (1), (4), (6) = 59227,66 + 233919,2 + 407998,7 = 701145,6 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 185379,7 lbf Path 3-3 through (2), (4) = 625373,3 + 233919,2 = 859292,6 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for External Pressure

UG-37 Area Calculation Summary (in2)

For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

1,4260 2,9361 -- 0,5713 -- 2,1648 0,2000 0,0625 0,6740

Weld Failure Path Analysis Summary

Weld strength calculations are not required for external pressure

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,4718 1,2000 weld size is adequate

Calculations for external pressure 125,3 psi @ 150 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 3,152 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-28 trn = 0,0428 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = 0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) = 0,5*(3,152*0,688*1 + 2*0,674*0,688*1*(1 - 0,2631)) = 1,426 in

2

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Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 3,152*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 0,674)*(1*0,688 - 1*0,688) - 2*0,674*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,5713 in

2

= 5*(tn - trn)*fr2*t = 5*(0,674 - 0,0428)*0,2631*0,688 = 0,5713 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(0,674 - 0,0428)*(2,5*0,674 + 1,2)*0,2631 = 0,9582 in

2

A41 = Leg2*fr3

= 0,87182*0,2631

= 0,2 in2

(Part of the weld is outside of the limits)

A42 = Leg2*fr4

= 02*1

= 0 in2

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (6,304 - 3,152 - 2*0,674)*1,2*1 = 2,1648 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,5713 + 0,2 + 0 + 2,1648 = 2,9361 in

2

As Area >= A the reinforcement is adequate.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,674 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0428 in

Wall thickness per UG-45(b)(2): tr2 = 0,0462 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,2074 in

The greater of tr2 or tr3: tr5 = 0,0625 in

The lesser of tr4 or tr5: tr6 = 0,0625 in

Required per UG-45 is the larger of tr1 or tr6 = 0,0625 in Available nozzle wall thickness new, tn = 0,674 in The nozzle neck thickness is adequate.

1.1.1.85 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 7,9857/4,5000 = 1,7746 Do/t = 4,5000/0,042791 = 105,1633

From table G: A = 0,000685

From table CS-2: B = 9882,7188

Pa = 4*B/(3*(Do/t))

= 4*9882,7188/(3*(4,5000/0,042791))

= 125,2999 psi

1.1.1.86 Design thickness for external pressure Pa = 125,2999 psi

= t + Corrosion = 0,042791 + 0,0000 = 0,0428"

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.87 Flange #35

Flange description: 48 inch 600# WN A105

Bolt Material: SA-193 B7 Bolt (2 1/2 < t <= 4)

Flange rated MDMT: -40 °F

(UCS-66(b)(1)(b))

(Bolts rated MDMT per Fig UCS-66 note (e) = -40 °F)

Liquid static head on flange: 2,1367 psi

ASME B16.47 flange rating MAWP: 1415 psi@ 150°F

ASME B16.47 flange rating MAP: 1480 psi@ 70°F

ASME B16.47 flange hydro test: 2225 psi@ 70°F

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EC-100

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63-286

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.88 KICKER NOZZLE - Nozzle #1 (N1)

ASME Section VIII Division 1, 2004 Edition

Note: round inside edges per UG-76(c)

Located on: MAJOR BARREL

Liquid static head included: 1,1508 psi

Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5)

Nozzle longitudinal joint efficiency: 1,00

Nozzle description: 14" Sch 160

Pad material specification: API 5L X65 (user defined)

Pad diameter: 26 in

Flange description: 14 inch 600# WN A105

Bolt Material: SA-193 B7 Bolt <= 2 1/2

Flange rated MDMT: -46,4 °F

(UCS-66(b)(1)(b))

Liquid static head on flange: 1,1508 psi

ASME B16.5 flange rating MAWP: 1415 psi@ 150°F

ASME B16.5 flange rating MAP: 1480 psi@ 70°F

ASME B16.5 flange hydro test: 2225 psi@ 70°F

Nozzle orientation: 270 °

Local vessel minimum thickness: 0,688 in

Nozzle center line offset to datum line: 228,03 in

End of nozzle to shell center: 42,69 in

Nozzle inside diameter, new: 11,188 in

Nozzle nominal wall thickness: 1,406 in

Nozzle corrosion allowance: 0 in

Projection available outside vessel, Lpr: 18,69 in

tw(lower) = 0,6880 in

Leg41 = 1,0000 in

tw(upper) = 1,0000 in

Leg42 = 1,0000 in

Dp = 26,0000 in

te = 1,0000 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP.

UG-37 Area Calculation Summary (in2)

For P = 1415 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

9,1230 9,4502 -- 0,8317 -- 8,3760 0,2425 0,4871 1,4060

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

592.994,50 614.262,94 1.633.714,25 102.908,52 1.969.786,88 647.348,50 2.028.525,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,5250 1,0000 weld size is adequate

Calculations for internal pressure 1415 psi @ 150 °F Nozzle is impact test exempt per UG-20(f).

Nozzle UCS-66 governing thk: 1 in

Nozzle rated MDMT: -20 °F

Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 11,188 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1415*5,594/(17100*1 - 0,6*1415) = 0,4871 in

tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631) = 9,123 in

2

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,8317 in

2

= 5*(tn - trn)*fr2*t = 5*(1,406 - 0,4871)*0,2631*0,688 = 0,8317 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(1,406 - 0,4871)*(2,5*1,406 + 1)*0,2631 = 2,1831 in

2

A41 = Leg2*fr3

= 0,962*0,2631

= 0,2425 in2

(Part of the weld is outside of the limits)

Page 66: PIG CALC.pdf

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

A42 = Leg2*fr4

= 02*1

= 0 in2

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (22,376 - 11,188 - 2*1,406)*1*1 = 8,376 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,8317 + 0,2425 + 0 + 8,376 = 9,4502 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,4871 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,518 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in

The greater of tr2 or tr3: tr5 = 0,518 in

The lesser of tr4 or tr5: tr6 = 0,3281 in

Required per UG-45 is the larger of tr1 or tr6 = 0,4871 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Strength of welded joints: (1) Inner fillet weld in shear

i f (2) Outer fillet weld in shear

o = f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

Nozzle OD*tw*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (9,123 - 0 + 2*1,406*0,2631*(1*0,688 - 1*0,688))*65000 = 592994,5 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,8317 + 8,376 + 0,2425 + 0)*65000 = 614262,9 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,8317 + 0 + 0,2425 + 0 + 2*1,406*0,688*0,2631)*65000 = 102908,5 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,8317 + 0 + 8,376 + 0,2425 + 0 + 0 + 2*1,406*0,688*0,2631)*65000 = 647348,5 lbf

Load for path 1-1 lesser of W or W1-1 = 592994,5 lbf Path 1-1 through (2) & (3) = 1300777 + 332937,8 = 1633714 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 102908,5 lbf Path 2-2 through (1), (4), (6) = 184263,8 + 727748,8 + 1057774 = 1969787 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 592994,5 lbf Path 3-3 through (2), (4) = 1300777 + 727748,8 = 2028525 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

Page 68: PIG CALC.pdf

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AKTEK_ENG_13_P113_EC

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EC-100

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68-286

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Date

02.11.2010

FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP.

UG-37 Area Calculation Summary (in2)

For P = 1480 psi @ 70 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

9,1230 9,4288 -- 0,8103 -- 8,3760 0,2425 0,5107 1,4060

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

592.994,50 612.871,94 1.633.714,25 101.517,52 1.969.786,88 645.957,50 2.028.525,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,5250 1,0000 weld size is adequate

Calculations for internal pressure 1480 psi @ 70 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 11,188 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1480*5,594/(17100*1 - 0,6*1480) = 0,5107 in

tr (full area replacement) =0,688 in

Page 69: PIG CALC.pdf

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631) = 9,123 in

2

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,8103 in

2

= 5*(tn - trn)*fr2*t = 5*(1,406 - 0,5107)*0,2631*0,688 = 0,8103 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(1,406 - 0,5107)*(2,5*1,406 + 1)*0,2631 = 2,127 in

2

A41 = Leg2*fr3

= 0,962*0,2631

= 0,2425 in2

(Part of the weld is outside of the limits)

A42 = Leg2*fr4

= 02*1

= 0 in2

Page 70: PIG CALC.pdf

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70-286

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Date

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (22,376 - 11,188 - 2*1,406)*1*1 = 8,376 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,8103 + 0,2425 + 0 + 8,376 = 9,4288 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,5107 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5415 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in

The greater of tr2 or tr3: tr5 = 0,5415 in

The lesser of tr4 or tr5: tr6 = 0,3281 in

Required per UG-45 is the larger of tr1 or tr6 = 0,5107 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Page 71: PIG CALC.pdf

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EC-100

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Strength of welded joints: (1) Inner fillet weld in shear

i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg ,8 lbf (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (9,123 - 0 + 2*1,406*0,2631*(1*0,688 - 1*0,688))*65000 = 592994,5 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,8103 + 8,376 + 0,2425 + 0)*65000 = 612871,9 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,8103 + 0 + 0,2425 + 0 + 2*1,406*0,688*0,2631)*65000 = 101517,5 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,8103 + 0 + 8,376 + 0,2425 + 0 + 0 + 2*1,406*0,688*0,2631)*65000 = 645957,5 lbf

Load for path 1-1 lesser of W or W1-1 = 592994,5 lbf Path 1-1 through (2) & (3) = 1300777 + 332937,8 = 1633714 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 101517,5 lbf Path 2-2 through (1), (4), (6) = 184263,8 + 727748,8 + 1057774 = 1969787 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 592994,5 lbf Path 3-3 through (2), (4) = 1300777 + 727748,8 = 2028525 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

Page 72: PIG CALC.pdf

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EC-100

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for External Pressure

UG-37 Area Calculation Summary (in2)

For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

4,5615 9,7820 -- 1,1635 -- 8,3760 0,2425 0,1204 1,4060

Weld Failure Path Analysis Summary

Weld strength calculations are not required for external pressure

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,5250 1,0000 weld size is adequate

Calculations for external pressure 125,3 psi @ 150 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 11,188 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-28 trn = 0,1204 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = 0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) = 0,5*(11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631)) = 4,5615 in

2

Page 73: PIG CALC.pdf

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EC-100

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73-286

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Date

02.11.2010

FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 1,1635 in

2

= 5*(tn - trn)*fr2*t = 5*(1,406 - 0,1204)*0,2631*0,688 = 1,1635 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(1,406 - 0,1204)*(2,5*1,406 + 1)*0,2631 = 3,0543 in

2

A41 = Leg2*fr3

= 0,962*0,2631

= 0,2425 in2

(Part of the weld is outside of the limits)

A42 = Leg2*fr4

= 02*1

= 0 in2

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (22,376 - 11,188 - 2*1,406)*1*1 = 8,376 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 1,1635 + 0,2425 + 0 + 8,376 = 9,782 in

2

As Area >= A the reinforcement is adequate.

Page 74: PIG CALC.pdf

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EC-100

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74-286

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Date

02.11.2010

FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,1204 in

Wall thickness per UG-45(b)(2): tr2 = 0,0462 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in

The greater of tr2 or tr3: tr5 = 0,0625 in

The lesser of tr4 or tr5: tr6 = 0,0625 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1204 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate.

1.1.1.89 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 19,7335/14,0000 = 1,4095 Do/t = 14,0000/0,120413 = 116,2664

From table G: A = 0,000757

From table CS-2: B = 10926,2178

Pa = 4*B/(3*(Do/t))

= 4*10926,2178/(3*(14,0000/0,120413))

= 125,3009 psi

1.1.1.90 Design thickness for external pressure Pa = 125,3009 psi

= t + Corrosion = 0,120413 + 0,0000 = 0,1204"

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.91 KICKER NOZZLE - Nozzle #2 (N2) ASME Section VIII Division 1, 2004 Edition

Note: round inside edges per UG-76(c)

Located on: MAJOR BARREL

Liquid static head included: 1,1508 psi

Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5)

Nozzle longitudinal joint efficiency: 1,00

Nozzle description: 14" Sch 160

Pad material specification: API 5L X65 (user defined)

Pad diameter: 26 in

Flange description: 14 inch 600# WN A105

Bolt Material: SA-193 B7 Bolt <= 2 1/2

Flange rated MDMT: -46,4 °F

(UCS-66(b)(1)(b))

Liquid static head on flange: 1,1508 psi

ASME B16.5 flange rating MAWP: 1415 psi@ 150°F

ASME B16.5 flange rating MAP: 1480 psi@ 70°F

ASME B16.5 flange hydro test: 2225 psi@ 70°F

Nozzle orientation: 270 °

Local vessel minimum thickness: 0,688 in

Nozzle center line offset to datum line: 168,976 in

End of nozzle to shell center: 42,69 in

Nozzle inside diameter, new: 11,188 in

Nozzle nominal wall thickness: 1,406 in

Nozzle corrosion allowance: 0 in

Projection available outside vessel, Lpr: 18,69 in

tw(lower) = 0,6880 in

Leg41 = 1,0000 in

tw(upper) = 1,0000 in

Leg42 = 1,0000 in

Dp = 26,0000 in

te = 1,0000 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP.

UG-37 Area Calculation Summary (in2)

For P = 1415 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

9,1230 9,4502 -- 0,8317 -- 8,3760 0,2425 0,4871 1,4060

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

592.994,50 614.262,94 1.633.714,25 102.908,52 1.969.786,88 647.348,50 2.028.525,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,5250 1,0000 weld size is adequate

Calculations for internal pressure 1415 psi @ 150 °F Nozzle is impact test exempt per UG-20(f).

Nozzle UCS-66 governing thk: 1 in

Nozzle rated MDMT: -20 °F

Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 11,188 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1415*5,594/(17100*1 - 0,6*1415) = 0,4871 in

tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631) = 9,123 in

2

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,8317 in

2

= 5*(tn - trn)*fr2*t = 5*(1,406 - 0,4871)*0,2631*0,688 = 0,8317 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(1,406 - 0,4871)*(2,5*1,406 + 1)*0,2631 = 2,1831 in

2

A41 = Leg2*fr3

= 0,962*0,2631

= 0,2425 in2

(Part of the weld is outside of the limits)

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

A42 = Leg2*fr4

= 02*1

= 0 in2

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (22,376 - 11,188 - 2*1,406)*1*1 = 8,376 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,8317 + 0,2425 + 0 + 8,376 = 9,4502 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,4871 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,518 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in

The greater of tr2 or tr3: tr5 = 0,518 in

The lesser of tr4 or tr5: tr6 = 0,3281 in

Required per UG-45 is the larger of tr1 or tr6 = 0,4871 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Strength of welded joints: (1) Inner fillet weld in shear

i f (2) Outer fillet weld in shear

o = f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

ozzle OD*tw*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (9,123 - 0 + 2*1,406*0,2631*(1*0,688 - 1*0,688))*65000 = 592994,5 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,8317 + 8,376 + 0,2425 + 0)*65000 = 614262,9 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,8317 + 0 + 0,2425 + 0 + 2*1,406*0,688*0,2631)*65000 = 102908,5 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,8317 + 0 + 8,376 + 0,2425 + 0 + 0 + 2*1,406*0,688*0,2631)*65000 = 647348,5 lbf

Load for path 1-1 lesser of W or W1-1 = 592994,5 lbf Path 1-1 through (2) & (3) = 1300777 + 332937,8 = 1633714 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 102908,5 lbf Path 2-2 through (1), (4), (6) = 184263,8 + 727748,8 + 1057774 = 1969787 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 592994,5 lbf Path 3-3 through (2), (4) = 1300777 + 727748,8 = 2028525 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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02.11.2010

FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP.

UG-37 Area Calculation Summary (in2)

For P = 1480 psi @ 70 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

9,1230 9,4288 -- 0,8103 -- 8,3760 0,2425 0,5107 1,4060

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

592.994,50 612.871,94 1.633.714,25 101.517,52 1.969.786,88 645.957,50 2.028.525,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,5250 1,0000 weld size is adequate

Calculations for internal pressure 1480 psi @ 70 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 11,188 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1480*5,594/(17100*1 - 0,6*1480) = 0,5107 in

tr (full area replacement) =0,688 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631) = 9,123 in

2

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,8103 in

2

= 5*(tn - trn)*fr2*t = 5*(1,406 - 0,5107)*0,2631*0,688 = 0,8103 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(1,406 - 0,5107)*(2,5*1,406 + 1)*0,2631 = 2,127 in

2

A41 = Leg2*fr3

= 0,962*0,2631

= 0,2425 in2

(Part of the weld is outside of the limits)

A42 = Leg2*fr4

= 02*1

= 0 in2

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (22,376 - 11,188 - 2*1,406)*1*1 = 8,376 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,8103 + 0,2425 + 0 + 8,376 = 9,4288 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,5107 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5415 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in

The greater of tr2 or tr3: tr5 = 0,5415 in

The lesser of tr4 or tr5: tr6 = 0,3281 in

Required per UG-45 is the larger of tr1 or tr6 = 0,5107 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Page 83: PIG CALC.pdf

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Strength of welded joints: (1) Inner fillet weld in shear

i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg 8 lbf (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (9,123 - 0 + 2*1,406*0,2631*(1*0,688 - 1*0,688))*65000 = 592994,5 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,8103 + 8,376 + 0,2425 + 0)*65000 = 612871,9 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,8103 + 0 + 0,2425 + 0 + 2*1,406*0,688*0,2631)*65000 = 101517,5 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,8103 + 0 + 8,376 + 0,2425 + 0 + 0 + 2*1,406*0,688*0,2631)*65000 = 645957,5 lbf

Load for path 1-1 lesser of W or W1-1 = 592994,5 lbf Path 1-1 through (2) & (3) = 1300777 + 332937,8 = 1633714 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 101517,5 lbf Path 2-2 through (1), (4), (6) = 184263,8 + 727748,8 + 1057774 = 1969787 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 592994,5 lbf Path 3-3 through (2), (4) = 1300777 + 727748,8 = 2028525 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

Page 84: PIG CALC.pdf

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for External Pressure

UG-37 Area Calculation Summary (in2)

For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

4,5615 9,7820 -- 1,1635 -- 8,3760 0,2425 0,1204 1,4060

Weld Failure Path Analysis Summary

Weld strength calculations are not required for external pressure

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,5250 1,0000 weld size is adequate

Calculations for external pressure 125,3 psi @ 150 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 11,188 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-28 trn = 0,1204 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = 0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) = 0,5*(11,188*0,688*1 + 2*1,406*0,688*1*(1 - 0,2631)) = 4,5615 in

2

Page 85: PIG CALC.pdf

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EC-100

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Date

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 11,188*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 1,406)*(1*0,688 - 1*0,688) - 2*1,406*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 1,1635 in

2

= 5*(tn - trn)*fr2*t = 5*(1,406 - 0,1204)*0,2631*0,688 = 1,1635 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(1,406 - 0,1204)*(2,5*1,406 + 1)*0,2631 = 3,0543 in

2

A41 = Leg2*fr3

= 0,962*0,2631

= 0,2425 in2

(Part of the weld is outside of the limits)

A42 = Leg2*fr4

= 02*1

= 0 in2

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (22,376 - 11,188 - 2*1,406)*1*1 = 8,376 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 1,1635 + 0,2425 + 0 + 8,376 = 9,782 in

2

As Area >= A the reinforcement is adequate.

Page 86: PIG CALC.pdf

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86-286

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Date

02.11.2010

FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,75 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,1204 in

Wall thickness per UG-45(b)(2): tr2 = 0,0462 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,3281 in

The greater of tr2 or tr3: tr5 = 0,0625 in

The lesser of tr4 or tr5: tr6 = 0,0625 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1204 in Available nozzle wall thickness new, tn = 1,406 in The nozzle neck thickness is adequate.

1.1.1.92 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 19,7335/14,0000 = 1,4095 Do/t = 14,0000/0,120413 = 116,2664

From table G: A = 0,000757

From table CS-2: B = 10926,2178

Pa = 4*B/(3*(Do/t))

= 4*10926,2178/(3*(14,0000/0,120413))

= 125,3009 psi

1.1.1.93 Design thickness for external pressure Pa = 125,3009 psi

= t + Corrosion = 0,120413 + 0,0000 = 0,1204"

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.94 PIG SIGNALLER - Nozzle #8 (N8)

ASME Section VIII Division 1, 2004 Edition

tw(lower) = 0,6880 in

Leg41 = 1,0000 in

tw(upper) = 1,0000 in

Leg42 = 1,0000 in

Dp = 10,3750 in

te = 1,0000 in

Note: round inside edges per UG-76(c)

Located on: MINOR BARREL

Liquid static head included: 0,5732 psi

Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5)

Nozzle longitudinal joint efficiency: 1,00

Nozzle description: 2" XX Heavy

Pad material specification: API 5L X65 (user defined)

Pad diameter: 10,375 in

Flange description: 2 inch 600# WN A105

Bolt Material: SA-193 B7 Bolt <= 2 1/2

Flange rated MDMT: -46,5 °F

(UCS-66(b)(1)(b))

Liquid static head on flange: 0,3139 psi

ASME B16.5 flange rating MAWP: 1415 psi@ 150°F

ASME B16.5 flange rating MAP: 1480 psi@ 70°F

ASME B16.5 flange hydro test: 2225 psi@ 70°F

Nozzle orientation: 0 °

Local vessel minimum thickness: 0,688 in

Nozzle center line offset to datum line: 55 in

End of nozzle to shell center: 27,185 in

Nozzle inside diameter, new: 1,503 in

Nozzle nominal wall thickness: 0,436 in

Nozzle corrosion allowance: 0 in

Projection available outside vessel, Lpr: 7,185 in

This nozzle passes through a Category A joint.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP.

UG-37 Area Calculation Summary (in2)

For P = 1415,26 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

1,4762 1,9283 -- 0,3354 -- 1,3760 0,2169 0,1348 0,4360

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

95.950,20 125.339,49 534.955,50 46.159,30 334.160,25 135.599,30 642.517,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,3052 1,0000 weld size is adequate

Calculations for internal pressure 1415,26 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,11408).

Nozzle UCS-66 governing thk: 0,436 in

Nozzle rated MDMT: -155 °F

Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1415,259*0,7515/(17100*1 - 0,6*1415,259) = 0,0654 in

tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) = 1,4762 in

2

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 1,503*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 0,436)*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,3354 in

2

= 5*(tn - trn)*fr2*t = 5*(0,436 - 0,0654)*0,2631*0,688 = 0,3354 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(0,436 - 0,0654)*(2,5*0,436 + 1)*0,2631 = 0,4076 in

2

A41 = Leg2*fr3

= 0,90792*0,2631

= 0,2169 in2

(Part of the weld is outside of the limits)

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

A42 = Leg2*fr4

= 02*1

= 0 in2

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (3,751 - 1,503 - 2*0,436)*1*1 = 1,376 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,3354 + 0,2169 + 0 + 1,376 = 1,9283 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0654 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,4317 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in

The greater of tr2 or tr3: tr5 = 0,4317 in

The lesser of tr4 or tr5: tr6 = 0,1348 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Strength of welded joints: (1) Inner fillet weld in shear ( i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 = 95950,2 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,3354 + 1,376 + 0,2169 + 0)*65000 = 125339,5 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,3354 + 0 + 0,2169 + 0 + 2*0,436*0,688*0,2631)*65000 = 46159,3 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,3354 + 0 + 1,376 + 0,2169 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 135599,3 lbf

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 46159,3 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 179443,8 = 334160,3 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP.

UG-37 Area Calculation Summary (in2)

For P = 1480 psi @ 70 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

1,4762 1,9254 -- 0,3325 -- 1,3760 0,2169 0,1348 0,4360

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

95.950,20 125.151,00 534.955,50 45.970,80 334.160,25 135.410,80 642.517,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,3052 1,0000 weld size is adequate

Calculations for internal pressure 1480 psi @ 70 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1480*0,7515/(17100*1 - 0,6*1480) = 0,0686 in

tr (full area replacement) =0,688 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) = 1,4762 in

2

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 1,503*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 0,436)*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,3325 in

2

= 5*(tn - trn)*fr2*t = 5*(0,436 - 0,0686)*0,2631*0,688 = 0,3325 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(0,436 - 0,0686)*(2,5*0,436 + 1)*0,2631 = 0,4041 in

2

A41 = Leg2*fr3

= 0,90792*0,2631

= 0,2169 in2

(Part of the weld is outside of the limits)

A42 = Leg2*fr4

= 02*1

= 0 in2

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (3,751 - 1,503 - 2*0,436)*1*1 = 1,376 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,3325 + 0,2169 + 0 + 1,376 = 1,9254 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0686 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,4513 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in

The greater of tr2 or tr3: tr5 = 0,4513 in

The lesser of tr4 or tr5: tr6 = 0,1348 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Strength of welded joints: (1) Inner fillet weld in shear ( i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 = 95950,2 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,3325 + 1,376 + 0,2169 + 0)*65000 = 125151 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,3325 + 0 + 0,2169 + 0 + 2*0,436*0,688*0,2631)*65000 = 45970,8 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,3325 + 0 + 1,376 + 0,2169 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 135410,8 lbf

Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 45970,8 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 179443,8 = 334160,3 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for External Pressure

UG-37 Area Calculation Summary (in2)

For Pe = 267,63 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

0,7381 1,9510 -- 0,3581 -- 1,3760 0,2169 0,0822 0,4360

Weld Failure Path Analysis Summary

Weld strength calculations are not required for external pressure

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,3052 1,0000 weld size is adequate

Calculations for external pressure 267,63 psi @ 150 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-28 trn = 0,0403 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = 0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) = 0,5*(1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631)) = 0,7381 in

2

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area available from FIG. UG-37.1 A1 = larger of the following= 0 in

2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 1,503*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0,688 + 0,436)*(1*0,688 - 1*0,688) - 2*0,436*(1*0,688 - 1*0,688)*(1 - 0,2631) = 0 in

2

A2 = smaller of the following= 0,3581 in

2

= 5*(tn - trn)*fr2*t = 5*(0,436 - 0,0403)*0,2631*0,688 = 0,3581 in

2

= 2*(tn - trn)*(2,5*tn + te)*fr2 = 2*(0,436 - 0,0403)*(2,5*0,436 + 1)*0,2631 = 0,4351 in

2

A41 = Leg2*fr3

= 0,90792*0,2631

= 0,2169 in2

(Part of the weld is outside of the limits)

A42 = Leg2*fr4

= 02*1

= 0 in2

(Part of the weld is outside of the limits)

A5 = (Dp - d - 2*tn)*te*fr4 = (3,751 - 1,503 - 2*0,436)*1*1 = 1,376 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0,3581 + 0,2169 + 0 + 1,376 = 1,951 in

2

As Area >= A the reinforcement is adequate.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0403 in

Wall thickness per UG-45(b)(2): tr2 = 0,0822 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in

The greater of tr2 or tr3: tr5 = 0,0822 in

The lesser of tr4 or tr5: tr6 = 0,0822 in

Required per UG-45 is the larger of tr1 or tr6 = 0,0822 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate.

1.1.1.95 External Pressure, (Corroded & at 150,00°F) UG-28(c) L/Do = 7,2203/2,3750 = 3,0401 Do/t = 2,3750/0,040342 = 58,8711

From table G: A = 0,000903

From table CS-2: B = 11816,6680

Pa = 4*B/(3*(Do/t))

= 4*11816,6680/(3*(2,3750/0,040342))

= 267,6282 psi

1.1.1.96 Design thickness for external pressure Pa = 267,6282 psi

= t + Corrosion = 0,040342 + 0,0000 = 0,0403"

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.97 PRESSURE INDICATOR - Nozzle #4 (N4)

ASME Section VIII Division 1, 2004 Edition

tw(lower) = 0,6880 in

Leg41 = 1,0000 in

tw(upper) = 1,1000 in

Leg42 = 1,0000 in

Dp = 10,3750 in

te = 1,1000 in

Note: round inside edges per UG-76(c)

Located on: MAJOR BARREL

Liquid static head included: 0,2844 psi

Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5)

Nozzle longitudinal joint efficiency: 1,00

Nozzle description: 2" XX Heavy

Pad material specification: API 5L X65 (user defined)

Pad diameter: 10,375 in

Flange description: 2 inch 600# WN A105

Bolt Material: SA-193 B7 Bolt <= 2 1/2

Flange rated MDMT: -55 °F

(UCS-66(b)(1)(b))

(UCS-68(c) applies. Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F)

Liquid static head on flange: 0 psi

ASME B16.5 flange rating MAWP: 1415 psi@ 150°F

ASME B16.5 flange rating MAP: 1480 psi@ 70°F

ASME B16.5 flange hydro test: 2225 psi@ 70°F

Nozzle orientation: 0 °

Local vessel minimum thickness: 0,688 in

Nozzle center line offset to datum line: 257,55 in

End of nozzle to shell center: 31,88 in

Nozzle inside diameter, new: 1,503 in

Nozzle nominal wall thickness: 0,436 in

Nozzle corrosion allowance: 0 in

Projection available outside vessel, Lpr: 7,88 in

This nozzle passes through a Category A joint.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP.

UG-37 Area Calculation Summary (in2)

For P = 1415,28 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

1,4762 1,5136 -- -- -- 1,5136 -- 0,1348 0,4360

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

95.950,20 120.185,00 534.955,50 32.060,80 352.104,66 130.444,80 642.517,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,3052 1,1000 weld size is adequate

Calculations for internal pressure 1415,28 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,11405).

Nozzle UCS-66 governing thk: 0,436 in

Nozzle rated MDMT: -155 °F

Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1415,284*0,7515/(17100*1 - 0,6*1415,284) = 0,0654 in

tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) = 1,4762 in

2

Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations.

A5 = (Dp - d - 2*tn)*te*fr4 = (3,751 - 1,503 - 2*0,436)*1,1*1 = 1,5136 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0 + 0 + 0 + 1,5136 = 1,5136 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0654 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5181 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in

The greater of tr2 or tr3: tr5 = 0,5181 in

The lesser of tr4 or tr5: tr6 = 0,1348 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Strength of welded joints: (1) Inner fillet weld in shear

i f (2) Outer fillet weld in shear

OD*Leg*So f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 = 95950,2 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,3354 + 1,5136 + 0 + 0)*65000 = 120185 lbf

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W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,3354 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 32060,8 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,3354 + 0 + 1,5136 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 130444,8 lbf

Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 32060,8 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 197388,2 = 352104,7 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP.

UG-37 Area Calculation Summary (in2)

For P = 1480 psi @ 70 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

1,4762 1,5136 -- -- -- 1,5136 -- 0,1348 0,4360

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

95.950,20 119.996,50 534.955,50 31.872,31 352.104,66 130.256,30 642.517,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,3052 1,1000 weld size is adequate

Calculations for internal pressure 1480 psi @ 70 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1480*0,7515/(17100*1 - 0,6*1480) = 0,0686 in

tr (full area replacement) =0,688 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) = 1,4762 in

2

Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations.

A5 = (Dp - d - 2*tn)*te*fr4 = (3,751 - 1,503 - 2*0,436)*1,1*1 = 1,5136 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0 + 0 + 0 + 1,5136 = 1,5136 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0686 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5415 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in

The greater of tr2 or tr3: tr5 = 0,5415 in

The lesser of tr4 or tr5: tr6 = 0,1348 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Strength of welded joints: (1) Inner fillet weld in shear ( i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 = 95950,2 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,3325 + 1,5136 + 0 + 0)*65000 = 119996,5 lbf

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,3325 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 31872,31 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,3325 + 0 + 1,5136 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 130256,3 lbf

Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 31872,31 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 197388,2 = 352104,7 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for External Pressure

UG-37 Area Calculation Summary (in2)

For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

0,7381 1,5136 -- -- -- 1,5136 -- 0,0625 0,4360

Weld Failure Path Analysis Summary

Weld strength calculations are not required for external pressure

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,3052 1,1000 weld size is adequate

Calculations for external pressure 125,3 psi @ 150 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-28 trn = 0,0298 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = 0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) = 0,5*(1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631)) = 0,7381 in

2

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations.

A5 = (Dp - d - 2*tn)*te*fr4 = (3,751 - 1,503 - 2*0,436)*1,1*1 = 1,5136 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0 + 0 + 0 + 1,5136 = 1,5136 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0298 in

Wall thickness per UG-45(b)(2): tr2 = 0,0462 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in

The greater of tr2 or tr3: tr5 = 0,0625 in

The lesser of tr4 or tr5: tr6 = 0,0625 in

Required per UG-45 is the larger of tr1 or tr6 = 0,0625 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.98 External Pressure, (Corroded & at 150,00°F) UG-28(c)

L/Do = 7,9094/2,3750 = 3,3303 Do/t = 2,3750/0,029784 = 79,7400

From table G: A = 0,000520

From table CS-2: B = 7493,5347

Pa = 4*B/(3*(Do/t))

= 4*7493,5347/(3*(2,3750/0,029784))

= 125,2995 psi

1.1.1.99 Design thickness for external pressure Pa = 125,2995 psi

= t + Corrosion = 0,029784 + 0,0000 = 0,0298"

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.100 SAFETY VALVE NOZZLE - Nozzle #5 (N5)

ASME Section VIII Division 1, 2004 Edition

tw(lower) = 0,6880 in

Leg41 = 0,5000 in

tw(upper) = 0,6880 in

Leg42 = 0,5000 in

Dp = 9,3150 in

te = 0,6880 in

Note: round inside edges per UG-76(c)

Located on: MAJOR BARREL

Liquid static head included: 0,2844 psi

Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5)

Nozzle longitudinal joint efficiency: 1,00

Nozzle description: 1" XX Heavy

Pad material specification: API 5L X65 (user defined)

Pad diameter: 9,315 in

Flange description: 1 inch 600# WN A105

Bolt Material: SA-193 B7 Bolt <= 2 1/2

Flange rated MDMT: -55 °F

(UCS-66(b)(1)(b))

(UCS-68(c) applies. Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F)

Liquid static head on flange: 0 psi

ASME B16.5 flange rating MAWP: 1415 psi@ 150°F

ASME B16.5 flange rating MAP: 1480 psi@ 70°F

ASME B16.5 flange hydro test: 2225 psi@ 70°F

Nozzle orientation: 0 °

Local vessel minimum thickness: 0,688 in

Nozzle center line offset to datum line: 239,84 in

End of nozzle to shell center: 31,88 in

Nozzle inside diameter, new: 0,599 in

Nozzle nominal wall thickness: 0,358 in

Nozzle corrosion allowance: 0,118 in

Projection available outside vessel, Lpr: 7,88 in

This nozzle passes through a Category A joint.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP.

UG-37 Area Calculation Summary (in2)

For P = 1415,28 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

0,8178 0,9467 -- -- -- 0,9467 -- 0,2344 0,3580

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

53.159,20 70.504,72 237.865,14 14.617,60 145.366,63 76.152,32 301.370,50

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,1680 0,3500 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,3500 weld size is adequate

Nozzle to pad groove (Upper) 0,1680 0,6880 weld size is adequate

Calculations for internal pressure 1415,28 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,11511).

Nozzle UCS-66 governing thk: 0,358 in

Nozzle rated MDMT: -155 °F

Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,3455 in

Normal to the vessel wall outside: 2,5*(tn - Cn) + te = 1,288 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1415,284*0,4175/(17100*1 - 0,6*1415,284) = 0,0364 in

tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 0,835*0,688*1 + 2*0,24*0,688*1*(1 - 0,2631) = 0,8178 in

2

Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations.

A5 = (Dp - d - 2*tn)*te*fr4 = (2,691 - 0,835 - 2*0,24)*0,688*1 = 0,9467 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0 + 0 + 0 + 0,9467 = 0,9467 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,24 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,168 in

tc(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,1544 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5181 in

Wall thickness per UG-16(b): tr3 = 0,1805 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,2344 in

The greater of tr2 or tr3: tr5 = 0,5181 in

The lesser of tr4 or tr5: tr6 = 0,2344 in

Required per UG-45 is the larger of tr1 or tr6 = 0,2344 in Available nozzle wall thickness new, tn = 0,358 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Strength of welded joints: (1) Inner fillet weld in shear ( i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (0,8178 - 0 + 2*0,24*0,2631*(1*0,688 - 1*0,688))*65000 = 53159,2 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,138 + 0,9467 + 0 + 0)*65000 = 70504,72 lbf

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,138 + 0 + 0 + 0 + 2*0,24*0,688*0,2631)*65000 = 14617,6 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,138 + 0 + 0,9467 + 0 + 0 + 0 + 2*0,24*0,688*0,2631)*65000 = 76152,32 lbf

Load for path 1-1 lesser of W or W1-1 = 53159,2 lbf Path 1-1 through (2) & (3) = 233014,1 + 4851,03 = 237865,1 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 14617,6 lbf Path 2-2 through (1), (4), (6) = 8653,82 + 68356,4 + 68356,4 = 145366,6 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 53159,2 lbf Path 3-3 through (2), (4) = 233014,1 + 68356,4 = 301370,5 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP.

UG-37 Area Calculation Summary (in2)

For P = 1480 psi @ 70 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

0,7751 0,9467 -- -- -- 0,9467 -- 0,1164 0,3580

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

50.382,47 79.442,22 239.455,94 26.331,84 145.366,63 87.866,55 301.370,50

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,3500 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,3500 weld size is adequate

Nozzle to pad groove (Upper) 0,2506 0,6880 weld size is adequate

Calculations for internal pressure 1480 psi @ 70 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,3455 in

Normal to the vessel wall outside: 2,5*(tn - Cn) + te = 1,583 in

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1480*0,2995/(17100*1 - 0,6*1480) = 0,0273 in

tr (full area replacement) =0,688 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 0,599*0,688*1 + 2*0,358*0,688*1*(1 - 0,2631) = 0,7751 in

2

Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations.

A5 = (Dp - d - 2*tn)*te*fr4 = (2,691 - 0,599 - 2*0,358)*0,688*1 = 0,9467 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0 + 0 + 0 + 0,9467 = 0,9467 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,358 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0273 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5415 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1164 in

The greater of tr2 or tr3: tr5 = 0,5415 in

The lesser of tr4 or tr5: tr6 = 0,1164 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1164 in Available nozzle wall thickness new, tn = 0,358 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Strength of welded joints: (1) Inner fillet weld in shear

i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

zle dia*tn*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (0,7751 - 0 + 2*0,358*0,2631*(1*0,688 - 1*0,688))*65000 = 50382,47 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,2755 + 0,9467 + 0 + 0)*65000 = 79442,22 lbf

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,2755 + 0 + 0 + 0 + 2*0,358*0,688*0,2631)*65000 = 26331,84 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,2755 + 0 + 0,9467 + 0 + 0 + 0 + 2*0,358*0,688*0,2631)*65000 = 87866,55 lbf

Load for path 1-1 lesser of W or W1-1 = 50382,47 lbf Path 1-1 through (2) & (3) = 233014,1 + 6441,83 = 239455,9 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 26331,84 lbf Path 2-2 through (1), (4), (6) = 8653,82 + 68356,4 + 68356,4 = 145366,6 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 50382,47 lbf Path 3-3 through (2), (4) = 233014,1 + 68356,4 = 301370,5 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for External Pressure

UG-37 Area Calculation Summary (in2)

For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

0,4089 0,9467 -- -- -- 0,9467 -- 0,1805 0,3580

Weld Failure Path Analysis Summary

Weld strength calculations are not required for external pressure

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,1680 0,3500 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,3500 weld size is adequate

Nozzle to pad groove (Upper) 0,1680 0,6880 weld size is adequate

Calculations for external pressure 125,3 psi @ 150 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,3455 in

Normal to the vessel wall outside: 2,5*(tn - Cn) + te = 1,288 in

Nozzle required thickness per UG-28 trn = 0,0215 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = 0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) = 0,5*(0,835*0,688*1 + 2*0,24*0,688*1*(1 - 0,2631)) = 0,4089 in

2

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations.

A5 = (Dp - d - 2*tn)*te*fr4 = (2,691 - 0,835 - 2*0,24)*0,688*1 = 0,9467 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0 + 0 + 0 + 0,9467 = 0,9467 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,24 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,168 in

tc(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*0,5 = 0,35 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,1395 in

Wall thickness per UG-45(b)(2): tr2 = 0,0462 in

Wall thickness per UG-16(b): tr3 = 0,1805 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,2344 in

The greater of tr2 or tr3: tr5 = 0,1805 in

The lesser of tr4 or tr5: tr6 = 0,1805 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1805 in Available nozzle wall thickness new, tn = 0,358 in The nozzle neck thickness is adequate.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.101 External Pressure, (Corroded & at 150,00°F) UG-28(c)

L/Do = 7,8890/1,3150 = 5,9992 Do/t = 1,3150/0,021462 = 61,2712

From table G: A = 0,000400

From table CS-2: B = 5758,1777

Pa = 4*B/(3*(Do/t))

= 4*5758,1777/(3*(1,3150/0,021462))

= 125,3046 psi

1.1.1.102 Design thickness for external pressure Pa = 125,3046 psi

= t + Corrosion = 0,021462 + 0,1180 = 0,1395"

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.103 VENT NOZZLE - Nozzle #2 (N2)

ASME Section VIII Division 1, 2004 Edition

tw(lower) = 0,6880 in

Leg41 = 1,0000 in

tw(upper) = 1,1000 in

Leg42 = 1,0000 in

Dp = 10,3750 in

te = 1,1000 in

Note: round inside edges per UG-76(c)

Located on: MAJOR BARREL

Liquid static head included: 0,2844 psi

Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 5)

Nozzle longitudinal joint efficiency: 1,00

Nozzle description: 2" XX Heavy

Pad material specification: API 5L X65 (user defined)

Pad diameter: 10,375 in

Flange description: 2 inch 600# WN A105

Bolt Material: SA-193 B7 Bolt <= 2 1/2

Flange rated MDMT: -55 °F

(UCS-66(b)(1)(b))

(UCS-68(c) applies. Bolts rated MDMT per Fig UCS-66 note (e) = -55 °F)

Liquid static head on flange: 0 psi

ASME B16.5 flange rating MAWP: 1415 psi@ 150°F

ASME B16.5 flange rating MAP: 1480 psi@ 70°F

ASME B16.5 flange hydro test: 2225 psi@ 70°F

Nozzle orientation: 0 °

Local vessel minimum thickness: 0,688 in

Nozzle center line offset to datum line: 275,26 in

End of nozzle to shell center: 31,88 in

Nozzle inside diameter, new: 1,503 in

Nozzle nominal wall thickness: 0,436 in

Nozzle corrosion allowance: 0 in

Projection available outside vessel, Lpr: 7,88 in

This nozzle passes through a Category A joint.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for Internal Pressure The attached ASME B16.5 flange limits the nozzle MAWP.

UG-37 Area Calculation Summary (in2)

For P = 1415,28 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

1,4762 1,5136 -- -- -- 1,5136 -- 0,1348 0,4360

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

95.950,20 120.185,00 534.955,50 32.060,80 352.104,66 130.444,80 642.517,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,3052 1,1000 weld size is adequate

Calculations for internal pressure 1415,28 psi @ 150 °F Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0,11405).

Nozzle UCS-66 governing thk: 0,436 in

Nozzle rated MDMT: -155 °F

Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

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AKTEK_ENG_13_P113_EC

Spec.No

EC-100

Sheet

126-286

Rev.

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Date

02.11.2010

FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1415,284*0,7515/(17100*1 - 0,6*1415,284) = 0,0654 in

tr (full area replacement) =0,688 in Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) = 1,4762 in

2

Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations.

A5 = (Dp - d - 2*tn)*te*fr4 = (3,751 - 1,503 - 2*0,436)*1,1*1 = 1,5136 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0 + 0 + 0 + 1,5136 = 1,5136 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

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EC-100

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127-286

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Date

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0654 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5181 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in

The greater of tr2 or tr3: tr5 = 0,5181 in

The lesser of tr4 or tr5: tr6 = 0,1348 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Strength of welded joints: (1) Inner fillet weld in shear

i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

n*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 = 95950,2 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,3354 + 1,5136 + 0 + 0)*65000 = 120185 lbf

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,3354 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 32060,8 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,3354 + 0 + 1,5136 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 130444,8 lbf

Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 32060,8 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 197388,2 = 352104,7 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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EC-100

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129-286

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Date

02.11.2010

FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for MAP The attached ASME B16.5 flange limits the nozzle MAP.

UG-37 Area Calculation Summary (in2)

For P = 1480 psi @ 70 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

1,4762 1,5136 -- -- -- 1,5136 -- 0,1348 0,4360

Weld Failure Path Analysis Summary (lbf) All failure paths are stronger than the applicable weld loads

Weld load W

Weld load W1-1

Path 1-1 strength

Weld load W2-2

Path 2-2 strength

Weld load W3-3

Path 3-3 strength

95.950,20 119.996,50 534.955,50 31.872,31 352.104,66 130.256,30 642.517,25

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,3052 1,1000 weld size is adequate

Calculations for internal pressure 1480 psi @ 70 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0,6*P) = 1480*0,7515/(17100*1 - 0,6*1480) = 0,0686 in

tr (full area replacement) =0,688 in

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Date

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area required per UG-37(c) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631) = 1,4762 in

2

Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations.

A5 = (Dp - d - 2*tn)*te*fr4 = (3,751 - 1,503 - 2*0,436)*1,1*1 = 1,5136 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0 + 0 + 0 + 1,5136 = 1,5136 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

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EC-100

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Date

02.11.2010

FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0686 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0,5415 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in

The greater of tr2 or tr3: tr5 = 0,5415 in

The lesser of tr4 or tr5: tr6 = 0,1348 in

Required per UG-45 is the larger of tr1 or tr6 = 0,1348 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0,74*65000 = 48100 psi

Nozzle wall in shear: 0,7*17100 = 11970 psi

Inner fillet weld in shear: 0,49*17100 = 8379 psi

Outer fillet weld in shear: 0,49*65000 = 31850 psi

Upper groove weld in tension: 0,74*65000 = 48100 psi

Strength of welded joints: (1) Inner fillet weld in shear

i f (2) Outer fillet weld in shear

o f (3) Nozzle wall in shear

zle dia*tn*Sn f (4) Groove weld in tension

w*Sg f (6) Upper groove weld in tension

w*Sg f Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (1,4762 - 0 + 2*0,436*0,2631*(1*0,688 - 1*0,688))*65000 = 95950,2 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv = (0,3325 + 1,5136 + 0 + 0)*65000 = 119996,5 lbf

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Date

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0,3325 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 31872,31 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv = (0,3325 + 0 + 1,5136 + 0 + 0 + 0 + 2*0,436*0,688*0,2631)*65000 = 130256,3 lbf

Load for path 1-1 lesser of W or W1-1 = 95950,2 lbf Path 1-1 through (2) & (3) = 519059,8 + 15895,65 = 534955,5 lbf Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2). Load for path 2-2 lesser of W or W2-2 = 31872,31 lbf Path 2-2 through (1), (4), (6) = 31259,04 + 123457,4 + 197388,2 = 352104,7 lbf Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1). Load for path 3-3 lesser of W or W3-3 = 95950,2 lbf Path 3-3 through (2), (4) = 519059,8 + 123457,4 = 642517,3 lbf Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

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EC-100

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133-286

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Date

02.11.2010

FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Reinforcement Calculations for External Pressure

UG-37 Area Calculation Summary (in2)

For Pe = 125,3 psi @ 150 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required

A available

A1 A2 A3 A5 A

welds treq tmin

0,7381 1,5136 -- -- -- 1,5136 -- 0,0625 0,4360

Weld Failure Path Analysis Summary

Weld strength calculations are not required for external pressure

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in)

Actual weld throat size (in)

Status

Nozzle to pad fillet (Leg41) 0,2500 0,7000 weld size is adequate

Pad to shell fillet (Leg42) 0,3440 0,7000 weld size is adequate

Nozzle to pad groove (Upper) 0,3052 1,1000 weld size is adequate

Calculations for external pressure 125,3 psi @ 150 °F Limits of reinforcement per UG-40

Parallel to the vessel wall: (Rn + tn + t )= 1,8755 in

Normal to the vessel wall outside: 2,5*(t - C) = 1,72 in

Nozzle required thickness per UG-28 trn = 0,0298 in From UG-37(d)(1) required thickness tr = 0,688 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17100, Sv = 65000, Sp = 65000 psi fr1 = lesser of 1 or Sn/Sv = 0,2631 fr2 = lesser of 1 or Sn/Sv = 0,2631 fr3 = lesser of fr2 or Sp/Sv = 0,2631 fr4 = lesser of 1 or Sp/Sv = 1

A = 0,5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) = 0,5*(1,503*0,688*1 + 2*0,436*0,688*1*(1 - 0,2631)) = 0,7381 in

2

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Area available from FIG. UG-37.1 Area A1 is not included in these calculations. Area A2 is not included in these calculations. Weld area A41 has not been included in these calculations.Weld area A42 has not been included in these calculations.

A5 = (Dp - d - 2*tn)*te*fr4 = (3,751 - 1,503 - 2*0,436)*1,1*1 = 1,5136 in

2

Area = A1 + A2 + A41 + A42 + A5 = 0 + 0 + 0 + 0 + 1,5136 = 1,5136 in

2

As Area >= A the reinforcement is adequate. UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0,75 or tn or te = 0,436 in

tc(min) = lesser of 0,25 or 0,7*tmin = 0,25 in

tc(actual) = 0,7*Leg = 0.7*1 = 0,7 in

Outer fillet: tmin = lesser of 0,75 or te or t = 0,688 in

tw(min) = 0,5*tmin = 0,344 in

tw(actual) = 0,7*Leg = 0.7*1 = 0,7 in

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0,0298 in

Wall thickness per UG-45(b)(2): tr2 = 0,0462 in

Wall thickness per UG-16(b): tr3 = 0,0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0,1348 in

The greater of tr2 or tr3: tr5 = 0,0625 in

The lesser of tr4 or tr5: tr6 = 0,0625 in

Required per UG-45 is the larger of tr1 or tr6 = 0,0625 in Available nozzle wall thickness new, tn = 0,436 in The nozzle neck thickness is adequate.

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.104 External Pressure, (Corroded & at 150,00°F) UG-28(c)

L/Do = 7,9094/2,3750 = 3,3303 Do/t = 2,3750/0,029784 = 79,7400

From table G: A = 0,000520

From table CS-2: B = 7493,5347

Pa = 4*B/(3*(Do/t))

= 4*7493,5347/(3*(2,3750/0,029784))

= 125,2995 psi

1.1.1.105 Design thickness for external pressure Pa = 125,2995 psi

= t + Corrosion = 0,029784 + 0,0000 = 0,0298"

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

1.1.1.106 SADDLE #1

Saddle material: ASTM A36

Saddle construction is: Centered web

Saddle allowable stress: Ss = 20.000,00 psi

Saddle yield stress: Sy = 38.000,00 psi

Saddle distance to datum: 55,0000 in

Tangent to tangent length: L = 322,6900 in

Saddle separation: Ls = 212,2800 in

Vessel radius: R = 24,0000 in

Tangent distance left: Al = 52,4100 in

Tangent distance right: Ar = 58,0000 in

Saddle height: Hs = 53,5400 in

Saddle contact angle: θ = 120 °

Wind pressure: 27,1536 psf

Wear plate thickness: tp = 0,6880 in

Wear plate width: Wp = 26,8500 in

Wear plate contact angle: θw = 132 °

Web plate thickness: ts = 0,6880 in

Base plate length: E = 43,3000 in

Base plate width: F = 15,7400 in

Base plate thickness: tb = 1,0000 in

Number of stiffener ribs: n = 6

Largest stiffener rib spacing: di = 8,3850 in

Stiffener rib thickness: tw = 0,3750 in

Saddle width: B = 15,7400 in

Anchor bolt size & type: 1 inch series 8 threaded

Anchor bolt material: ASTM A193

Anchor bolt allowable shear: 15.000,00 psi

Anchor bolt corrosion allowance: 0,0000 in

Anchor bolts per saddle: 4

Base coefficient of friction: 0,45

Weight on left saddle: operating = 26.794,00 lb, test = 26.802,00 lb

Weight on right saddle: operating = 10.857,00 lb, test = 10.850,00 lb

Weight of saddle pair = 2.118,00 lb

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Saddle calculations are based on the method presented in "Stresses in Large Cylindrical Pressure Vessels on Two Saddle Supports" by L.P. Zick. Seismic base shear on vessel Vessel is assumed to be a rigid structure.

Method of seismic analysis: UBC 1997 ground supported

Vertical seismic accelerations considered: Yes

Force Multiplier: 0,4

Minimum Weight Multiplier: 0,2

Seismic zone: 4

Importance factor: I = 1,5

Soil profile: SD

Near source factor: Na = 1

V = 0,7 * Ca * I * W/1,4 = 0,7 * 0,44 * 1,5 * 37.651,00/1,4 = 12.424,83 lb Saddle reactions due to weight + seismic Vv = vertical seismic force acting on right saddle V = horizontal seismic shear acting on right saddle (worst case if not slotted) Seismic longitudinal reaction, Ql (right saddle): Ql = V * Hs / Ls + Vv = 12.424,83 * 53,54 / 212,28 + 2.171,40 = 5.305,117 lb Seismic transverse reaction, Qt (right saddle): Qt = V*Hs/(Ro*Sin( θ /2 )) + Vv = 3.582,81*53,54/(20*Sin( 120 /2 )) + 2.171,40 = 13.246,34 lb Q = Weight on saddle + larger of Qt or Ql Q = W + Qt = 10.857,00 + 13.246,34 = 24.103,34 lb Vv = vertical seismic force acting on left saddle V = horizontal seismic shear acting on left saddle (worst case if not slotted) Seismic longitudinal reaction, Ql (left saddle): Ql = V * Hs / Ls + Vv = 12.424,83 * 53,54 / 212,28 + 5.358,80 = 8.492,517 lb Seismic transverse reaction, Qt (left saddle): Qt = V*Hs/(Ro*Sin( θ /2 )) + Vv = 8.842,02*53,54/(24*Sin( 120 /2 )) + 5.358,80 = 28.135,35 lb Q = Weight on saddle + larger of Qt or Ql Q = W + Qt = 26.794,00 + 28.135,35 = 54.929,35 lb

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Transverse wind shear on vessel Vwt = Pw*G*(Cf(shell)*(Projected shell area) + Cf(saddle)*(Projected saddle area)) = 27,1536*0,85*(0,4*103,8682 + 2*6,894995) = 1.277,215 lb End wind shear on vessel Vwe = Pw*G*(Cf(shell)* o

2 / 144 + Cf(saddle)*(Projected saddle area)) 2 / 144 + 2*10,08516)

= 813,5891 lb Saddle reactions due to weight + wind V = horizontal wind shear acting on right saddle (worst case if not slotted) Wind longitudinal reaction, Ql (right saddle): Ql = V * Hs / Ls = 624,07 * 53,54 / 212,28 = 157,3992 lb Wind transverse reaction, Qt (right saddle): Qt = V*Hs/(Ro*Sin( θ /2 )) = 610,3115*53,54/(20*Sin( 120 /2 )) = 1.886,554 lb Q = Weight on saddle + larger of Qt or Ql Q = W + Qt = 10.857,00 + 1.886,554 = 12.743,55 lb V = horizontal wind shear acting on left saddle (worst case if not slotted) Wind longitudinal reaction, Ql (left saddle): Ql = V * Hs / Ls = 813,5891 * 53,54 / 212,28 = 205,1986 lb Wind transverse reaction, Qt (left saddle): Qt = V*Hs/(Ro*Sin( θ /2 )) = 666,9037*53,54/(24*Sin( 120 /2 )) = 1.717,907 lb Q = Weight on saddle + larger of Qt or Ql Q = W + Qt = 26.794,00 + 1.717,907 = 28.511,91 lb

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Load Vessel

condition

Bending + pressure between saddles (psi)

Bending + pressure at the saddle (psi)

S1 (+)

allow (+)

S1 (-)

allow (-)

S2 (+)

allow (+)

S2 (-)

allow (-)

Seismic Operating 19.679 78.000 1.210 20.274 20.043 78.000 1.574 20.274

Seismic Vacuum 1.210 78.000 1.464 20.274 3.060 78.000 3.270 20.274

Wind Operating 19.097 78.000 628 20.274 19.780 78.000 1.311 20.274

Wind Test 24.599 97.500 603 20.463 25.308 97.500 1.311 20.463

Wind Vacuum 628 78.000 882 20.274 2.550 78.000 2.760 20.274

Load Vessel

condition

Tangential shear (psi)

Circumferential stress (psi)

Stress over saddle (psi)

Splitting (psi)

S3 allow S4

(horns)

S4 (Wear plate)

allow (+/-)

S5 allow S6 allow

Seismic Operating 3.394 52.000 -5.056 -8.459 97.500 3.144 19.000 466 13.333

Seismic Vacuum 3.394 52.000 -5.056 -8.459 97.500 3.144 19.000 466 13.333

Wind Operating 1.587 52.000 -2.624 -4.391 97.500 1.632 19.000 242 13.333

Wind Test 1.504 78.000 -2.519 -4.215 97.500 1.567 34.200 232 34.200

Wind Vacuum 1.587 52.000 -2.624 -4.391 97.500 1.632 19.000 242 13.333

Load Case 1: Seismic ,Operating Longitudinal stress between saddles (Seismic ,Operating, left saddle loading and geometry govern) S1 = +- 3*K1*Q*(L/12) / (

2*t)

2*0,688)

= 1.209,723 psi Sp = P*R/(2*t) = 1.090,137*23,312/(2*0,688) = 18.468,94 psi Maximum tensile stress S1t = S1 + Sp = 19.678,67 psi Maximum compressive stress (shut down) S1c = S1 = 1.209,723 psi Tensile stress is acceptable (<=1,2*S*E = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Longitudinal stress at the left saddle (Seismic ,Operating) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in

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Seismic vertical acceleration coefficient m = 0,6060606*0,33 = 0,2 w = Wt*(1 + m)/Le = 37.651,00*(1 + 0,2)/334,6833 = 134,9969 lb/in Bending moment at the left saddle: Mq = w*(2*H*Al/3 + Al

2/2 - (R

2 - H

2)/4)

= 134,9969*(2*7,44*52,41/3 + 52,412/2 - (24

2 - 7,44

2)/4)

= 202.926,8 lb-in S2 = +- Mq*K1'/ (

2*t)

2*0,688)

= 1.573,681 psi Sp = P*R/(2*t) = 1.090,137*23,312/(2*0,688) = 18.468,94 psi Maximum tensile stress S2t = S2 + Sp = 20.042,63 psi Maximum compressive stress (shut down) S2c = S2 = 1.573,681 psi Tensile stress is acceptable (<=1,2*S = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Tangential shear stress in the shell (left saddle, Seismic ,Operating) Qshear = Q - w*(a + 2*H/3) = 54.929,35 - 134,9969*(52,41 + 2*7,44/3) = 47.184,58 lb S3 = K2,2*Qshear/(R*t) = K2,2*47.184,58/(23,656*0,688) = 3.394,032 psi Tangential shear stress is acceptable (<= 0.8*S = 52.000,00 psi) Circumferential stress at the left saddle horns (Seismic ,Operating) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t

2+tp

2))

= -54.929,35/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*54.929,35/(2*(0,6882+0,688

2))

= -5.056,105 psi Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Seismic ,Operating) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t

2)

= -54.929,35/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*54.929,35/(2*0,6882)

= -8.458,564 psi Circumferential stress at wear plate horns is acceptable (<=1,5*Sa = 97.500,00 psi) Ring compression in shell over left saddle (Seismic ,Operating) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*54.929,35/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 3.144,262 psi Ring compression in shell is acceptable (<= 0,5*Sy = 19.000,00 psi)

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Saddle splitting load (left, Seismic ,Operating) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in

2

S6 = K8*Q / Ae = 0,2035*54.929,35 / 23,9768 = 466,2058 psi Stress in saddle is acceptable (<= (2/3)*Ss = 13.333,33 psi) Load Case 2: Seismic ,Vacuum Longitudinal stress between saddles (Seismic ,Vacuum, left saddle loading and geometry govern) S1 = +- 3*K1*Q*(L/12) / (

2*t)

2*0,688)

= 1.209,723 psi Sp = P*R/(2*t) = 15*23,312/(2*0,688) = 254,1279 psi Maximum tensile stress (shut down) S1t = S1 = 1.209,723 psi Maximum compressive stress S1c = S1 + Sp = 1.463,851 psi Tensile stress is acceptable (<=1,2*S*E = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Longitudinal stress at the right saddle (Seismic ,Vacuum) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in Seismic vertical acceleration coefficient m = 0,6060606*0,33 = 0,2 w = Wt*(1 + m)/Le = 37.651,00*(1 + 0,2)/334,6833 = 134,9969 lb/in Bending moment at the right saddle: Mq = w*(2*H*Ar/3 + Ar

2/2 - (R

2 - H

2)/4)

= 134,9969*(2*10,55*58/3 + 582/2 - (20

2 - 10,55

2)/4)

= 272.391,1 lb-in S2 = +- Mq*K1'/ (

2*t)

2*0,688)

= 3.059,585 psi Sp = P*R/(2*t) = 15*19,312/(2*0,688) = 210,5233 psi

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Maximum tensile stress (shut down) S2t = S2 = 3.059,585 psi Maximum compressive stress S2c = S2 + Sp = 3.270,108 psi Tensile stress is acceptable (<=1,2*S = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Tangential shear stress in the shell (left saddle, Seismic ,Vacuum) Qshear = Q - w*(a + 2*H/3) = 54.929,35 - 134,9969*(52,41 + 2*7,44/3) = 47.184,58 lb S3 = K2,2*Qshear/(R*t) = K2,2*47.184,58/(23,656*0,688) = 3.394,032 psi Tangential shear stress is acceptable (<= 0.8*S = 52.000,00 psi) Circumferential stress at the left saddle horns (Seismic ,Vacuum) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t

2+tp

2))

= -54.929,35/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*54.929,35/(2*(0,6882+0,688

2))

= -5.056,105 psi Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Seismic ,Vacuum) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t

2)

= -54.929,35/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*54.929,35/(2*0,6882)

= -8.458,564 psi Circumferential stress at wear plate horns is acceptable (<=1,5*Sa = 97.500,00 psi) Ring compression in shell over left saddle (Seismic ,Vacuum) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*54.929,35/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 3.144,262 psi Ring compression in shell is acceptable (<= 0,5*Sy = 19.000,00 psi) Saddle splitting load (left, Seismic ,Vacuum) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in

2

S6 = K8*Q / Ae = 0,2035*54.929,35 / 23,9768 = 466,2058 psi Stress in saddle is acceptable (<= (2/3)*Ss = 13.333,33 psi)

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Load Case 3: Wind ,Operating Longitudinal stress between saddles (Wind ,Operating, left saddle loading and geometry govern) S1 = +- 3*K1*Q*(L/12) / (

2*t)

2*0,688)

= 627,9251 psi Sp = P*R/(2*t) = 1.090,137*23,312/(2*0,688) = 18.468,94 psi Maximum tensile stress S1t = S1 + Sp = 19.096,87 psi Maximum compressive stress (shut down) S1c = S1 = 627,9251 psi Tensile stress is acceptable (<=1,2*S*E = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Longitudinal stress at the left saddle (Wind ,Operating) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in w = Wt/Le = 37.651,00/334,6833 = 112,4974 lb/in Bending moment at the left saddle: Mq = w*(2*H*Al/3 + Al

2/2 - (R

2 - H

2)/4)

= 112,4974*(2*7,44*52,41/3 + 52,412/2 - (24

2 - 7,44

2)/4)

= 169.105,7 lb-in S2 = +- Mq*K1'/ (

2*t)

2*0,688)

= 1.311,401 psi Sp = P*R/(2*t) = 1.090,137*23,312/(2*0,688) = 18.468,94 psi Maximum tensile stress S2t = S2 + Sp = 19.780,34 psi Maximum compressive stress (shut down) S2c = S2 = 1.311,401 psi Tensile stress is acceptable (<=1,2*S = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Tangential shear stress in the shell (left saddle, Wind ,Operating) Qshear = Q - w*(a + 2*H/3) = 28.511,91 - 112,4974*(52,41 + 2*7,44/3) = 22.057,93 lb S3 = K2,2*Qshear/(R*t) = K2,2*22.057,93/(23,656*0,688) = 1.586,648 psi Tangential shear stress is acceptable (<= 0.8*S = 52.000,00 psi)

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Circumferential stress at the left saddle horns (Wind ,Operating) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t

2+tp

2))

= -28.511,91/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*28.511,91/(2*(0,6882+0,688

2))

= -2.624,447 psi Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Wind ,Operating) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t

2)

= -28.511,91/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*28.511,91/(2*0,6882)

= -4.390,545 psi Circumferential stress at wear plate horns is acceptable (<=1,5*Sa = 97.500,00 psi) Ring compression in shell over left saddle (Wind ,Operating) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*28.511,91/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 1.632,077 psi Ring compression in shell is acceptable (<= 0,5*Sy = 19.000,00 psi) Saddle splitting load (left, Wind ,Operating) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in

2

S6 = K8*Q / Ae = 0,2035*28.511,91 / 23,9768 = 241,9911 psi Stress in saddle is acceptable (<= (2/3)*Ss = 13.333,33 psi) Load Case 4: Wind ,Test Longitudinal stress between saddles (Wind ,Test, left saddle loading and geometry govern) S1 = +- 3*K1*Q*(L/12) / (

2*t)

2*0,688)

= 602,7526 psi Sp = P*R/(2*t) = 1.416,392*23,312/(2*0,688) = 23.996,32 psi Maximum tensile stress S1t = S1 + Sp = 24.599,07 psi Maximum compressive stress (shut down) S1c = S1 = 602,7526 psi Tensile stress is acceptable (<= 0,9*Sy = 97.500,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.463,34 psi)

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Longitudinal stress at the left saddle (Wind ,Test) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in w = Wt/Le = 37.652,00/334,6833 = 112,5004 lb/in Bending moment at the left saddle: Mq = w*(2*H*Al/3 + Al

2/2 - (R

2 - H

2)/4)

= 112,5004*(2*7,44*52,41/3 + 52,412/2 - (24

2 - 7,44

2)/4)

= 169.110,1 lb-in S2 = +- Mq*K1'/ (

2*t)

2*0,688)

= 1.311,435 psi Sp = P*R/(2*t) = 1.416,392*23,312/(2*0,688) = 23.996,32 psi Maximum tensile stress S2t = S2 + Sp = 25.307,75 psi Maximum compressive stress (shut down) S2c = S2 = 1.311,435 psi Tensile stress is acceptable (<= 0,9*Sy = 97.500,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.463,34 psi) Tangential shear stress in the shell (left saddle, Wind ,Test) Qshear = Q - w*(a + 2*H/3) = 27.368,91 - 112,5004*(52,41 + 2*7,44/3) = 20.914,76 lb S3 = K2,2*Qshear/(R*t) = K2,2*20.914,76/(23,656*0,688) = 1.504,419 psi Tangential shear stress is acceptable (<= 0.8*S = 78.000,00 psi) Circumferential stress at the left saddle horns (Wind ,Test) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t

2+tp

2))

= -27.368,91/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*27.368,91/(2*(0,6882+0,688

2))

= -2.519,238 psi Circumferential stress at saddle horns is acceptable (<= 0,9*Sy = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Wind ,Test) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t

2)

= -27.368,91/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*27.368,91/(2*0,6882)

= -4.214,535 psi Circumferential stress at wear plate horns is acceptable (<= 0,9*Sy = 97.500,00 psi)

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Ring compression in shell over left saddle (Wind ,Test) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*27.368,91/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 1.566,649 psi Ring compression in shell is acceptable (<= 0,5*Sy = 34.200,00 psi) Saddle splitting load (left, Wind ,Test) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in

2

S6 = K8*Q / Ae = 0,2035*27.368,91 / 23,9768 = 232,2901 psi Stress in saddle is acceptable (<= 0,9*Sy = 34.200,00 psi) Load Case 5: Wind ,Vacuum Longitudinal stress between saddles (Wind ,Vacuum, left saddle loading and geometry govern) S1 = +- 3*K1

2*t)

= 3*0,3302*0,688)

= 627,9251 psi Sp = P*R/(2*t) = 15*23,312/(2*0,688) = 254,1279 psi Maximum tensile stress (shut down) S1t = S1 = 627,9251 psi Maximum compressive stress S1c = S1 + Sp = 882,053 psi Tensile stress is acceptable (<=1,2*S*E = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Longitudinal stress at the right saddle (Wind ,Vacuum) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*7,44/3 + 322,69 + 2*10,55/3 = 334,6834 in w = Wt/Le = 37.651,00/334,6833 = 112,4974 lb/in Bending moment at the right saddle: Mq = w*(2*H*Ar/3 + Ar

2/2 - (R

2 - H

2)/4)

= 112,4974*(2*10,55*58/3 + 582/2 - (20

2 - 10,55

2)/4)

= 226.992,6 lb-in S2 = +- Mq*K1'/ (

2*t)

2*0,688)

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= 2.549,654 psi Sp = P*R/(2*t) = 15*19,312/(2*0,688) = 210,5233 psi Maximum tensile stress (shut down) S2t = S2 = 2.549,654 psi Maximum compressive stress S2c = S2 + Sp = 2.760,177 psi Tensile stress is acceptable (<=1,2*S = 78.000,00 psi) Compressive stress is acceptable (<=1,2*Sc = 20.274,21 psi) Tangential shear stress in the shell (left saddle, Wind ,Vacuum) Qshear = Q - w*(a + 2*H/3) = 28.511,91 - 112,4974*(52,41 + 2*7,44/3) = 22.057,93 lb S3 = K2,2*Qshear/(R*t) = K2,2*22.057,93/(23,656*0,688) = 1.586,648 psi Tangential shear stress is acceptable (<= 0.8*S = 52.000,00 psi) Circumferential stress at the left saddle horns (Wind ,Vacuum) S4 = -Q/(4*(t+tp)*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*(t

2+tp

2))

= -28.511,91/(4*(0,688+0,688)*(15,74+1,56*Sqr(24*0,688))) - 3*0,0529*28.511,91/(2*(0,6882+0,688

2))

= -2.624,447 psi Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 97.500,00 psi) Circumferential stress at the left saddle wear plate horns (Wind ,Vacuum) S4 = -Q/(4*t*(b+1,56*Sqr(Ro*t))) - 3*K3*Q/(2*t

2)

= -28.511,91/(4*0,688*(15,74+1,56*Sqr(24*0,688))) - 3*0,0434*28.511,91/(2*0,6882)

= -4.390,545 psi Circumferential stress at wear plate horns is acceptable (<=1,5*Sa = 97.500,00 psi) Ring compression in shell over left saddle (Wind ,Vacuum) S5 = K5*Q/((t + tp)*(ts + 1,56*Sqr(Ro*tc))) = 0,7603*28.511,91/((0,688 + 0,688)*(0,688 + 1,56*Sqr(24*1,376))) = 1.632,077 psi Ring compression in shell is acceptable (<= 0,5*Sy = 19.000,00 psi) Saddle splitting load (left, Wind ,Vacuum) Area resisting splitting force = Web area + wear plate area Ae = Heff*ts + tp*Wp = 8*0,688 + 0,688*26,85 = 23,9768 in

2

S6 = K8*Q / Ae = 0,2035*28.511,91 / 23,9768 = 241,9911 psi Stress in saddle is acceptable (<= (2/3)*Ss = 13.333,33 psi)

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FA0210 Version:00 created 03/98 Dervied of Datasheet File:00135r02.xls

Shear stress in anchor bolting, one end slotted Maximum seismic or wind base shear = 12.424,83 lb Thermal expansion base shear = W* Corroded root area for a 1 inch series 8 threaded bolt = 0,551 in

2 ( 4 per saddle )

Bolt shear stress = 12.533,85/(0,551* 4) = 5686,86 psi Anchor bolt stress is acceptable (<= 15.000,00 psi) Web plate buckling check (Escoe pg 251) Allowable compressive stress Sc is the lesser of 20.000,00 or 225.868,6 psi: (20.000,00) Sc = Ki

2*E/(12*(1 - 0,3

2)*(di/tw)

2)

2*29.000.000/(12*(1 - 0,3

2)*(8,385/0,688)

2)

= 225.868,6 psi Allowable compressive load on the saddle be = di*ts/(di*ts + 2*tw*(b - 1)) = 8,385*0,688/(8,385*0,688 + 2*0,375*(15,74 - 1)) = 0,3428983 Fb = n*(As + 2*be*tw)*Sc = 6*(5,6445 + 2*0,3428983*0,688)*20.000,00 = 733.959,4 lb Saddle loading of 55.988,35 is <= Fb; satisfactory. Primary bending + axial stress in the saddle due to end loads (assumes one saddle slotted)

b = V * (Hs - xo)* y / I + Q / A = 12.424,83 * (53,54 - 16,53987)* 7,87 / 732,2853 + 54.929,35 / 57,70002 = 5.892,677 psi The primary bending + axial stress in the saddle <= 20.000 psi; satisfactory. Secondary bending + axial stress in the saddle due to end loads (includes thermal expansion, assumes one saddle slotted)

b = V * (Hs - xo)* y / I + Q / A = 24.958,68 * (53,54 - 16,53987)* 7,87 / 732,2853 + 54.929,35 / 57,70002 = 10.876,72 psi The secondary bending + axial stress in the saddle < 2*Sy= 76.000 psi; satisfactory. Saddle base plate thickness check (Roark sixth edition, Table 26, case 7a) where a = 8,3850, b = 7,5260 in tb 1*q*b

2/(1,5*Sa))

0,5

= (0,8058*82,14953*7,5262/(1,5*20.000,00))

0,5

= 0,3535 in The base plate thickness of 1,0000 in is adequate.

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Foundation bearing check Sf = Qmax / (F*E) = 55.988,35 / (15,74*43,3) = 82,14953 psi Concrete bearing stress < 750 psi ; satisfactory.

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1.1.1.107 Seismic Code

Seismic calculations are reported in the saddle report.

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1.1.1.108 Wind Code

Wind calculations are reported in the saddle report.

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1.1.1.109 Lifting Lug #1

1.1.1.110 Geometry Inputs

Attached To MAJOR BARREL

Orientation Longitudinal

Length of Lug, L 10,0000"

Height of Lug, B 5,0000"

Thickness of Lug, t 1,0000"

Hole Diameter, d 2,0000"

Load eccentricity, a1 1,0000"

Distance from Load to shell or pad, a2 2,5000"

Weld size, tw 0,2500"

Width of Pad, Bp 6,0000"

Length of Pad, Lp 12,0000"

Pad Thickness, tp 0,5000"

Pad weld size, twp 0,2500"

Load angle normal to vessel, β -20,2800 °

Angular Position 0,00°

Load angle from vertical, υ -20,2800 °

1.1.1.111 Intermediate Values

Load factor 1,5000

Vessel Weight (new, incl. Load Factor), W 34076 lb

Lug Weight (new), Wlug 24 lb

Distance from center of gravity to this lug, x1 63,1254"

Distance from center of gravity to second lug, x2 83,8746"

Allowable stress, tensile, σt 20000 psi

Allowable stress, shear, σs 13500 psi

Allowable stress, bearing, σp 30000 psi

Allowable stress, bending, σb 22000 psi

Allowable stress, weld shear, τallowable 13500 psi

1.1.1.112 Summary Values

Required Lift pin diameter, dreqd 0,9887"

Required Lug thickness, treqd 0,3455"

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Lug Stress Ratio, σratio 0,20

Weld Shear Stress Ratio, τratio 0,74

Lug design Acceptable

Local stresses (WRC 107) Acceptable

1.1.1.113 Lift Forces Fr = force on vessel at lug Fr = [W / cos(υ1)] * (1 - x1 / (x1 + x2)) = (34076,270) / cos(-20,2800) * (1 - 63,125/ (63,125 + 83,875)) = 20728 lbf where 'x1' is the distance between this lug and the center of gravity 'x2' is the distance between the second lift lug and the center of gravity 1.1.1.114 Lug Pin Diameter - Shear stress dreqd = (2*Fr / (π*σs))

0.5

= (2*20728,0039 / (π*13500,0))0.5

= 0,9887" dreqd / d = 0,9887 / 2,0000 = 0,49 Acceptable σ = Fr / A = Fr / (2*(0.25*π*d

2))

= 20728,0039 / (2*(0.25*π*2,00002)) = 3298,9641 psi

σ / σs = 3298,96 / 13500,00 = 0,24 Acceptable 1.1.1.115 Lug Thickness - Tensile stress treqd = Fr / ((L-d)*σt) = 20728,0039 / ((10,0000 - 2,0000)*20000,0) = 0,1296" treqd / t = 0,1296 / 1,0000 = 0,13 Acceptable σ = Fr / A = Fr / ((L - d)*t) = 20728,0039 / ((10,0000 - 2,0000)*1,0000) = 2591,0005 psi σ / σt = 2591,00 / 20000,00 = 0,13 Acceptable 1.1.1.116 Lug Thickness - Bearing stress treqd = Fv / (d*σp) = 20728,0039 / (2,0000*30000,0) = 0,3455" treqd / t = 0,3455 / 1,0000 = 0,35 Acceptable σ = Fv / Abearing = Fv / (d*(t)) = 20728,0039 / (2,0000 *(1,0000)) = 10364,0020 psi σ / σp = 10364,00 / 30000,00 = 0,35 Acceptable 1.1.1.117 Lug Plate Stress Lug stress tensile + bending during lift: σ ratio = Ften / (Aten*σt) + Mbend / (Zbend*σb) ≤ 1.0 = (Fr * cos(α) ) / (t * L * σt) + (6 * abs(Fr * sin(α) * Hght - Fr * cos(α) * a1) ) / (t * L

2 * σb) ≤ 1.0

= 20728*cos(-20,3) / (1,0000*10,0000*20000,0) + 6*abs(20728*sin(-20,3)*2,5000 - 20728*cos(-20,3)*1,0000) / (1,0000*10,0000

2*22000,0)

0,20 Acceptable

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1.1.1.118 Weld Stress Weld stress, tensile, bending and shear during lift: Shear stress at lift angle -20,28°; lift force = 20728,0039 lbf Aweld = (0.707)*h*2*(L + t) = (0.707)*0,2500*2*(10,0000 + 1,0000) = 3,8885 in² τt = Fr * cos(α) / Aweld = 20728 * cos(-20,3) / 3,8885 = 5000,1475 psi τb = M * c / I = 3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * h * L * (3*t + L))

= 3 * abs(20728 * sin(-20,3) * 2,5000 - 20728 * cos(-20,3) * 1,0000) / (22,9775)

= 4883,6011 psi

τs = Fr * sin(α) / Aweld

= 20728 * sin(-20,3) / 3,8885 = -1847,6267 psi

τ ratio = sqr( (τt + τb)

2 + τs

2 ) / τallowable ≤ 1.0

= sqr ( (5000,1475 + 4883,6011)2 + (-1847,6267)

2 ) / 13500,00 = 0,74 Acceptable

Pad Weld Stress, tensile, bending and shear during lift: Shear stress at lift angle -20,28°; lift force = 20728,0039 lbf Aweld = (0.707)*hp*2*(Lp + Bp) = (0.707)*0,2500*2*(12,0000 + 6,0000) = 6,3630 in² τt = Fr * cos(α) / Aweld = 20728 * cos(-20,3) / 6,3630 = 3055,6458 psi τb = M * c / I = 3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * h * Lp * (3*Wp + Lp))

= 3 * abs(20728 * sin(-20,3) * 3,0000 - 20728 * cos(-20,3) * 1,0000) / (63,6300)

= 1932,8885 psi

τs = Fr * sin(α) / Aweld

= 20728 * sin(-20,3) / 6,3630 = -1129,1053 psi

τ ratio = sqr( (τt + τb)

2 + τs

2 ) / τallowable ≤ 1.0

= sqr ( (3055,6458 + 1932,8885)2 + (-1129,1053)

2 ) / 13500,00 = 0,38 Acceptable

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1.1.1.119 WRC 107 Analysis 1.1.1.120 Geometry

Applied Loads

Radial load: Pr = -19.443,07 lbf

Circumferential moment: Mc = 0,00 lbf-in

Circumferential shear: Vc = 0,00 lbf

Longitudinal moment: ML = -2.110,42 lbf-in

Longitudinal shear: VL = -7.184,50 lbf

Torsion moment: Mt = 0,00 lbf-in

Internal pressure: P = 0,000 psi

Mean shell radius: Rm = 23,6560 in

Shell yield stress: Sy = 65.000,00 psi

Maximum stresses due to the applied loads at the lug edge (includes pressure) Rm/t =19,9125 C1 = 0,7500, C2 = 3,0000 in Note: Actual lug C1/C2 < 1/4, C1/C2 = 1/4 used as this is the minimum ratio covered by WRC 107. Local circumferential pressure stress = P*Ri/t = 0 psi Local longitudinal pressure stress = P*Ri/2t = 0 psi Maximum combined stress (PL+Pb+Q) = 20.072,00 psi Allowable combined stress (PL+Pb+Q) = +-3*S = +-195.000,00 psi Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material. The maximum combined stress (PL+Pb+Q) is within allowable limits. Maximum local primary membrane stress (PL) = 2.675,00 psi Allowable local primary membrane (PL) = +-1,5*S = +-97.500,00 psi The maximum local primary membrane stress (PL) is within allowable limits.

Height(radial): 5,0000" Pad Thickness: 0,5000"

Width (circumferential): 1,0000" Pad Width: 6,0000"

Length 10,0000" Pad Length: 12,0000"

Fillet Weld Size: 0,2500" Pad Weld Size: 0,2500"

Location Angle: 0,00°

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Stresses at the lug edge per WRC Bulletin 107

Figure value Au Al Bu Bl Cu Cl Du Dl

3C* 3,5135 0,0938 0 0 0 0 2.431 2.431 2.431 2.431

4C* 3,8176 0,0761 2.641 2.641 2.641 2.641 0 0 0 0

1C 0,2129 0,0558 0 0 0 0 17.598 -17.598

17.598 -17.598

2C-1 0,1768 0,0558 14.614 -14.614

14.614 -14.614

0 0 0 0

3A* 0,1706 0,0503 0 0 0 0 0 0 0 0

1A 0,1067 0,0654 0 0 0 0 0 0 0 0

3B* 1,2733 0,0799 34 34 -34 -34 0 0 0 0

1B-1 0,0588 0,0715 312 -312 -312 312 0 0 0 0

Pressure stress* 0 0 0 0 0 0 0 0

Total circumferential stress 17.601 -12.251

16.909 -11.695

20.029 -15.167

20.029 -15.167

Primary membrane circumferential stress*

2.675 2.675 2.607 2.607 2.431 2.431 2.431 2.431

3C* 3,6687 0,0761 2.538 2.538 2.538 2.538 0 0 0 0

4C* 3,7303 0,0938 0 0 0 0 2.581 2.581 2.581 2.581

1C-1 0,1839 0,0793 15.201 -15.201

15.201 -15.201

0 0 0 0

2C 0,1402 0,0793 0 0 0 0 11.589 -11.589

11.589 -11.589

4A* 0,2297 0,0503 0 0 0 0 0 0 0 0

2A 0,0598 0,0911 0 0 0 0 0 0 0 0

4B* 0,3363 0,0799 16 16 -16 -16 0 0 0 0

2B-1 0,0870 0,0985 335 -335 -335 335 0 0 0 0

Pressure stress* 0 0 0 0 0 0 0 0

Total longitudinal stress 18.090 -12.982

17.388 -12.344

14.170 -9.008 14.170 -9.008

Primary membrane longitudinal stress* 2.554 2.554 2.522 2.522 2.581 2.581 2.581 2.581

Shear from Mt 0 0 0 0 0 0 0 0

Circ shear from Vc 0 0 0 0 0 0 0 0

Long shear from VL 0 0 0 0 504 504 -504 -504

Total Shear stress 0 0 0 0 504 504 -504 -504

Combined stress (PL+Pb+Q) 18.090 -12.982

17.388 -12.344

20.072 -15.208

20.072 -15.208

Note: * denotes primary stress.

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Maximum stresses due to the applied loads at the pad edge (includes pressure) Rm/t =34,3837 C1 = 3,2500, C2 = 6,2500 in Local circumferential pressure stress = P*Ri/t = 0 psi Local longitudinal pressure stress = P*Ri/2t = 0 psi Maximum combined stress (PL+Pb+Q) = 23.981,00 psi Allowable combined stress (PL+Pb+Q) = +-3*S = +-195.000,00 psi Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material. The maximum combined stress (PL+Pb+Q) is within allowable limits. Maximum local primary membrane stress (PL) = 5.739,00 psi Allowable local primary membrane (PL) = +-1,5*S = +-97.500,00 psi The maximum local primary membrane stress (PL) is within allowable limits.

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Stresses at the pad edge per WRC Bulletin 107

Figure value Au Al Bu Bl Cu Cl Du Dl

3C* 2,5429 0,2490 0 0 0 0 3.038 3.038 3.038 3.038

4C* 4,7378 0,2149 5.660 5.660 5.660 5.660 0 0 0 0

1C 0,0849 0,1759 0 0 0 0 20.924 -20.924

20.924 -20.924

2C-1 0,0512 0,1759 12.619 -12.619

12.619 -12.619

0 0 0 0

3A* 1,3452 0,1709 0 0 0 0 0 0 0 0

1A 0,0829 0,1856 0 0 0 0 0 0 0 0

3B* 3,5667 0,2125 79 79 -79 -79 0 0 0 0

1B-1 0,0291 0,1986 166 -166 -166 166 0 0 0 0

Pressure stress* 0 0 0 0 0 0 0 0

Total circumferential stress 18.524 -7.046 18.034 -6.872 23.962 -17.886

23.962 -17.886

Primary membrane circumferential stress*

5.739 5.739 5.581 5.581 3.038 3.038 3.038 3.038

3C* 3,0442 0,2149 3.637 3.637 3.637 3.637 0 0 0 0

4C* 4,3987 0,2490 0 0 0 0 5.255 5.255 5.255 5.255

1C-1 0,0689 0,2210 16.981 -16.981

16.981 -16.981

0 0 0 0

2C 0,0382 0,2210 0 0 0 0 9.415 -9.415 9.415 -9.415

4A* 2,3239 0,1709 0 0 0 0 0 0 0 0

2A 0,0384 0,2264 0 0 0 0 0 0 0 0

4B* 1,4019 0,2125 45 45 -45 -45 0 0 0 0

2B-1 0,0400 0,2350 192 -192 -192 192 0 0 0 0

Pressure stress* 0 0 0 0 0 0 0 0

Total longitudinal stress 20.855 -13.491

20.381 -13.197

14.670 -4.160 14.670 -4.160

Primary membrane longitudinal stress* 3.682 3.682 3.592 3.592 5.255 5.255 5.255 5.255

Shear from Mt 0 0 0 0 0 0 0 0

Circ shear from Vc 0 0 0 0 0 0 0 0

Long shear from VL 0 0 0 0 418 418 -418 -418

Total Shear stress 0 0 0 0 418 418 -418 -418

Combined stress (PL+Pb+Q) 20.855 -13.491

20.381 -13.197

23.981 -17.899

23.981 -17.899

Note: * denotes primary stress.

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1.1.1.121 Lifting Lug #2

1.1.1.122 Geometry Inputs

Attached To MAJOR BARREL

Orientation Longitudinal

Length of Lug, L 10,0000"

Height of Lug, B 5,0000"

Thickness of Lug, t 1,0000"

Hole Diameter, d 2,0000"

Load eccentricity, a1 1,0000"

Distance from Load to shell or pad, a2 2,5000"

Weld size, tw 0,2500"

Width of Pad, Bp 6,0000"

Length of Pad, Lp 12,0000"

Pad Thickness, tp 0,5000"

Pad weld size, twp 0,2500"

Load angle normal to vessel, β 20,2800 °

Angular Position 0,00°

Load angle from vertical, υ 20,2800 °

1.1.1.123 Intermediate Values

Load factor 1,5000

Vessel Weight (new, incl. Load Factor), W 34076 lb

Lug Weight (new), Wlug 24 lb

Distance from center of gravity to this lug, x1 83,8746"

Distance from center of gravity to second lug, x2 63,1254"

Allowable stress, tensile, σt 20000 psi

Allowable stress, shear, σs 13500 psi

Allowable stress, bearing, σp 30000 psi

Allowable stress, bending, σb 22000 psi

Allowable stress, weld shear, τallowable 13500 psi

1.1.1.124 Summary Values

Required Lift pin diameter, dreqd 0,8577"

Required Lug thickness, treqd 0,2600"

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Lug Stress Ratio, σratio 0,08

Weld Shear Stress Ratio, τratio 0,31

Lug design Acceptable

Local stresses (WRC 107) Acceptable

1.1.1.125 Lift Forces Fr = force on vessel at lug Fr = [W / cos(υ1)] * (1 - x1 / (x1 + x2)) = (34076,270) / cos(20,2800) * (1 - 83,875/ (83,875 + 63,125)) = 15600 lbf where 'x1' is the distance between this lug and the center of gravity 'x2' is the distance between the second lift lug and the center of gravity 1.1.1.126 Lug Pin Diameter - Shear stress dreqd = (2*Fr / (π*σs))

0.5

= (2*15600,2559 / (π*13500,0))0.5

= 0,8577" dreqd / d = 0,8577 / 2,0000 = 0,43 Acceptable σ = Fr / A = Fr / (2*(0.25*π*d

2))

= 15600,2559 / (2*(0.25*π*2,00002)) = 2482,8577 psi

σ / σs = 2482,86 / 13500,00 = 0,18 Acceptable 1.1.1.127 Lug Thickness - Tensile stress treqd = Fr / ((L-d)*σt) = 15600,2559 / ((10,0000 - 2,0000)*20000,0) = 0,0975" treqd / t = 0,0975 / 1,0000 = 0,10 Acceptable σ = Fr / A = Fr / ((L - d)*t) = 15600,2559 / ((10,0000 - 2,0000)*1,0000) = 1950,0320 psi σ / σt = 1950,03 / 20000,00 = 0,10 Acceptable 1.1.1.128 Lug Thickness - Bearing stress treqd = Fv / (d*σp) = 15600,2559 / (2,0000*30000,0) = 0,2600" treqd / t = 0,2600 / 1,0000 = 0,26 Acceptable σ = Fv / Abearing = Fv / (d*(t)) = 15600,2559 / (2,0000 *(1,0000)) = 7800,1279 psi σ / σp = 7800,13 / 30000,00 = 0,26 Acceptable

1.1.1.129 Lug Plate Stress Lug stress tensile + bending during lift:

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σ ratio = Ften / (Aten*σt) + Mbend / (Zbend*σb) ≤ 1.0 = (Fr * cos(α) ) / (t * L * σt) + (6 * abs(Fr * sin(α) * Hght - Fr * cos(α) * a1) ) / (t * L

2 * σb) ≤ 1.0

= 15600*cos(20,3) / (1,0000*10,0000*20000,0) + 6*abs(15600*sin(20,3)*2,5000 - 15600*cos(20,3)*1,0000) / (1,0000*10,0000

2*22000,0)

= 0,08 Acceptable 1.1.1.130 Weld Stress Weld stress, tensile, bending and shear during lift: Shear stress at lift angle 20,28°; lift force = 15600,2559 lbf Aweld = (0.707)*h*2*(L + t) = (0.707)*0,2500*2*(10,0000 + 1,0000) = 3,8885 in² τt = Fr * cos(α) / Aweld = 15600 * cos(20,3) / 3,8885 = 3763,1978 psi τb = M * c / I = 3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * h * L * (3*t + L)) = 3 * abs(15600 * sin(20,3) * 2,5000 - 15600 * cos(20,3) * 1,0000) / (22,9775) = 145,6101 psi τs = Fr * sin(α) / Aweld = 15600 * sin(20,3) / 3,8885 = 1390,5560 psi τ ratio = sqr( (τt + τb)

2 + τs

2 ) / τallowable ≤ 1.0

= sqr ( (3763,1978 + 145,6101)2 + (1390,5560)

2 ) / 13500,00 = 0,31 Acceptable

Pad Weld Stress, tensile, bending and shear during lift: Shear stress at lift angle 20,28°; lift force = 15600,2559 lbf Aweld = (0.707)*hp*2*(Lp + Bp) = (0.707)*0,2500*2*(12,0000 + 6,0000) = 6,3630 in² τt = Fr * cos(α) / Aweld = 15600 * cos(20,3) / 6,3630 = 2299,7322 psi τb = M * c / I = 3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * h * Lp * (3*Wp + Lp)) = 3 * abs(15600 * sin(20,3) * 3,0000 - 15600 * cos(20,3) * 1,0000) / (63,6300) = 74,8862 psi τs = Fr * sin(α) / Aweld = 15600 * sin(20,3) / 6,3630 = 849,7842 psi τ ratio = sqr( (τt + τb)

2 + τs

2 ) / τallowable ≤ 1.0

= sqr ( (2299,7322 + 74,8862)2 + (849,7842)

2 ) / 13500,00 = 0,19 Acceptable

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1.1.1.131 WRC 107 Analysis 1.1.1.132 Geometry

Applied Loads

Radial load: Pr = -14.633,20 lbf

Circumferential moment: Mc = 0,00 lbf-in

Circumferential shear: Vc = 0,00 lbf

Longitudinal moment: ML = 30.854,73 lbf-in

Longitudinal shear: VL = 5.407,18 lbf

Torsion moment: Mt = 0,00 lbf-in

Internal pressure: P = 0,000 psi

Mean shell radius: Rm = 23,6560 in

Shell yield stress: Sy = 65.000,00 psi

Maximum stresses due to the applied loads at the lug edge (includes pressure) Rm/t =19,9125 C1 = 0,7500, C2 = 3,0000 in Note: Actual lug C1/C2 < 1/4, C1/C2 = 1/4 used as this is the minimum ratio covered by WRC 107. Local circumferential pressure stress = P*Ri/t = 0 psi Local longitudinal pressure stress = P*Ri/2t = 0 psi Maximum combined stress (PL+Pb+Q) = 18.480,00 psi Allowable combined stress (PL+Pb+Q) = +-3*S = +-195.000,00 psi Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material. The maximum combined stress (PL+Pb+Q) is within allowable limits. Maximum local primary membrane stress (PL) = 2.484,00 psi Allowable local primary membrane (PL) = +-1,5*S = +-97.500,00 psi The maximum local primary membrane stress (PL) is within allowable limits.

Height(radial): 5,0000" Pad Thickness: 0,5000"

Width (circumferential): 1,0000" Pad Width: 6,0000"

Length 10,0000" Pad Length: 12,0000"

Fillet Weld Size: 0,2500" Pad Weld Size: 0,2500"

Location Angle: 0,00°

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Stresses at the lug edge per WRC Bulletin 107

Figure value Au Al Bu Bl Cu Cl Du Dl

3C* 3,5135 0,0938 0 0 0 0 1.829 1.829 1.829 1.829

4C* 3,8176 0,0761 1.988 1.988 1.988 1.988 0 0 0 0

1C 0,2129 0,0558 0 0 0 0 13.244 -13.244

13.244 -13.244

2C-1 0,1768 0,0558 10.999 -10.999

10.999 -10.999

0 0 0 0

3A* 0,1706 0,0503 0 0 0 0 0 0 0 0

1A 0,1067 0,0654 0 0 0 0 0 0 0 0

3B* 1,2733 0,0799 -496 -496 496 496 0 0 0 0

1B-1 0,0588 0,0715 -4.563 4.563 4.563 -4.563 0 0 0 0

Pressure stress* 0 0 0 0 0 0 0 0

Total circumferential stress 7.928 -4.944 18.046 -13.078

15.073 -11.415

15.073 -11.415

Primary membrane circumferential stress*

1.492 1.492 2.484 2.484 1.829 1.829 1.829 1.829

3C* 3,6687 0,0761 1.910 1.910 1.910 1.910 0 0 0 0

4C* 3,7303 0,0938 0 0 0 0 1.942 1.942 1.942 1.942

1C-1 0,1839 0,0793 11.440 -11.440

11.440 -11.440

0 0 0 0

2C 0,1402 0,0793 0 0 0 0 8.722 -8.722 8.722 -8.722

4A* 0,2297 0,0503 0 0 0 0 0 0 0 0

2A 0,0598 0,0911 0 0 0 0 0 0 0 0

4B* 0,3363 0,0799 -233 -233 233 233 0 0 0 0

2B-1 0,0870 0,0985 -4.897 4.897 4.897 -4.897 0 0 0 0

Pressure stress* 0 0 0 0 0 0 0 0

Total longitudinal stress 8.220 -4.866 18.480 -14.194

10.664 -6.780 10.664 -6.780

Primary membrane longitudinal stress* 1.677 1.677 2.143 2.143 1.942 1.942 1.942 1.942

Shear from Mt 0 0 0 0 0 0 0 0

Circ shear from Vc 0 0 0 0 0 0 0 0

Long shear from VL 0 0 0 0 -379 -379 379 379

Total Shear stress 0 0 0 0 -379 -379 379 379

Combined stress (PL+Pb+Q) 8.220 -4.944 18.480 -14.194

15.105 -11.446

15.105 -11.446

Note: * denotes primary stress. Maximum stresses due to the applied loads at the pad edge (includes pressure) Rm/t =34,3837

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C1 = 3,2500, C2 = 6,2500 in Local circumferential pressure stress = P*Ri/t = 0 psi Local longitudinal pressure stress = P*Ri/2t = 0 psi Maximum combined stress (PL+Pb+Q) = 18.986,00 psi Allowable combined stress (PL+Pb+Q) = +-3*S = +-195.000,00 psi Note: The allowable combined stress (PL+Pb+Q) is based on the strain hardening characteristics of this material. The maximum combined stress (PL+Pb+Q) is within allowable limits. Maximum local primary membrane stress (PL) = 5.412,00 psi Allowable local primary membrane (PL) = +-1,5*S = +-97.500,00 psi The maximum local primary membrane stress (PL) is within allowable limits.

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Stresses at the pad edge per WRC Bulletin 107

Figure value Au Al Bu Bl Cu Cl Du Dl

3C* 2,5429 0,2490 0 0 0 0 2.286 2.286 2.286 2.286

4C* 4,7378 0,2149 4.260 4.260 4.260 4.260 0 0 0 0

1C 0,0849 0,1759 0 0 0 0 15.748 -15.748

15.748 -15.748

2C-1 0,0512 0,1759 9.497 -9.497 9.497 -9.497 0 0 0 0

3A* 1,3452 0,1709 0 0 0 0 0 0 0 0

1A 0,0829 0,1856 0 0 0 0 0 0 0 0

3B* 3,5667 0,2125 -1.152 -1.152 1.152 1.152 0 0 0 0

1B-1 0,0291 0,1986 -2.423 2.423 2.423 -2.423 0 0 0 0

Pressure stress* 0 0 0 0 0 0 0 0

Total circumferential stress 10.182 -3.966 17.332 -6.508 18.034 -13.462

18.034 -13.462

Primary membrane circumferential stress*

3.108 3.108 5.412 5.412 2.286 2.286 2.286 2.286

3C* 3,0442 0,2149 2.737 2.737 2.737 2.737 0 0 0 0

4C* 4,3987 0,2490 0 0 0 0 3.955 3.955 3.955 3.955

1C-1 0,0689 0,2210 12.780 -12.780

12.780 -12.780

0 0 0 0

2C 0,0382 0,2210 0 0 0 0 7.086 -7.086 7.086 -7.086

4A* 2,3239 0,1709 0 0 0 0 0 0 0 0

2A 0,0384 0,2264 0 0 0 0 0 0 0 0

4B* 1,4019 0,2125 -655 -655 655 655 0 0 0 0

2B-1 0,0400 0,2350 -2.814 2.814 2.814 -2.814 0 0 0 0

Pressure stress* 0 0 0 0 0 0 0 0

Total longitudinal stress 12.048 -7.884 18.986 -12.202

11.041 -3.131 11.041 -3.131

Primary membrane longitudinal stress* 2.082 2.082 3.392 3.392 3.955 3.955 3.955 3.955

Shear from Mt 0 0 0 0 0 0 0 0

Circ shear from Vc 0 0 0 0 0 0 0 0

Long shear from VL 0 0 0 0 -314 -314 314 314

Total Shear stress 0 0 0 0 -314 -314 314 314

Combined stress (PL+Pb+Q) 12.048 -7.884 18.986 -12.202

18.048 -13.472

18.048 -13.472

Note: * denotes primary stress.

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NOZZLES

( FEA )

FINITE ELEMENT

ANALYSIS

Results were generated with the finite

element program FE/Pipe®. Stress results

are post-processed in accordance with the

rules specified in ASME Section III and

ASME Section VIII, Division 2.

ANALYSIS SOFTWARE

ANSYS 9.0 PREPARED BY : MECH.ENG.IHSAN AKGUN

( PRESSURE VESSELS ENGINEER )

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Tabular Results – KICKER NOZZLE

Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.

Analysis Time Stamp: Sat Sep 23 21:52:43 2006.

Model Notes

Load Case Report

Solution Data

ASME Code Stress Output Plots

ASME Overstressed Areas

Highest Primary Stress Ratios

Highest Secondary Stress Ratios

Highest Fatigue Stress Ratios

Stress Intensification Factors

Allowable Loads

Flexibilities

Graphical Results

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Model Notes Input Echo: Model Type : Cylindrical Shell Parent Outside Diameter : 48.000 in. Thickness : 0.688 in. Fillet Along Shell : 1.000 in. Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 14.000 in. Thickness : 1.406 in. Length : 19.034 in. Nozzle Weld Length : 1.000 in. RePad Width : 6.000 in. RePad Thickness : 1.000 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 78.970 in. Distance from Bottom : 98.030 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in. (NOT USED) Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1089.2 psi Vessel Pressure : 1089.2 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run.

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SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector : 0.000 0.000 1.000 Nozzle Orientation Vector : -1.000 0.000 0.000

Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating (Fatigue Calc Performed) Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial)

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4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion) 7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1 Solution Data Maximum Solution Row Size = 972 Number of Nodes = 2028 Number of Elements = 668 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 570809133121069. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 17771940538827. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # FX FY FZ 1 29191. 0. 1914718. 2 29191. 0. 1914718. 3 0. 0. -2164368. 4 0. 0. 0. 5 0. 0. 0. 6 0. 0. 0. 7 29191. 0. 1914718.

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Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 570809133121069. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 2 69926728300438. 1-to-10% 201 18847533543418. .1-to- 1% 410 1428818046465. .01-to-.1% 300 251646588286. .001-to-.01% 56 25768600257. .0001-TO-.001% 11198 110499319. OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 8 16918108624334. 70-to-90% 31 13930091755029. 50-to-70% 45 10316248571499. 30-to-50% 93 7060982396331. 10-to-30% 516 2980979054368. 1-to-10% 2391 614741686375. .1-to- 1% 8469 58244264347. .01-to-.1% 7898 7931343623. .001-to-.01% 2985 765396589. .0001-TO-.001% 531298 5127749.

ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7

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ASME Overstressed Areas *** NO OVERSTRESSED NODES IN THIS MODEL ***

Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 24,913 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 25% Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 24,824 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 96% Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 8,172 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 31% Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 42,248 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 43% Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 38,192 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 39%

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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 43,493 195,000 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 22% Branch at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 39,358 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 76% Branch Transition Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 9,212 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 17% Pad Outer Edge Weld Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 58,419 195,000 Plot Reference: psi psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 29% Header Outside Pad Area Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 48,561 195,000 Plot Reference: psi psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 24%

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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 29,358 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 22215.8 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 26,567 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 30187.7 4% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 4,606 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 39,433 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 8438.8 6% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 24,280 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 39793.5 4% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2

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Stress Intensification Factors Branch/Nozzle Sif Summary Peak Primary Secondary Axial : 1.279 1.237 1.894 Inplane : 1.324 1.171 1.962 Outplane: 0.494 0.965 0.988 Torsion : 1.956 2.388 2.897 Pressure: 1.038 1.112 1.538 The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 6.380 Inplane 7.825 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 7.825 Inplane 7.825 Outplane 7.825 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.829 Inplane 7.825 Outplane 3.829 Torsional

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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 2125186. 164900. 247350. Inplane Moment (in. lb.) 6126511. 336141. 713062. Outplane Moment (in. lb.) 31475014. 2516291. 5337860. Torsional Moment (in. lb.) 3564401. 276573. 414859. Pressure (psi ) 1419.60 1089.15 1089.15 PRIMARY Maximum Conservative Realistic Load Type: Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 2145783. 23027. 34541. Inplane Moment (in. lb.) 6285948. 47700. 101186. Outplane Moment (in. lb.) 16113937. 280636. 595319. Torsional Moment (in. lb.) 4210393. 45184. 67776. Pressure (psi ) 1125.38 1089.15 1089.15 NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.

Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiff- nesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 14.000 in. Wall Thickness = 1.406 in.

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The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness

Finite Element Model

Finite Element Model

Elements at Discontinuity

1) Pl < 1.5(k)Smh (SUS Membrane) Case 1

2) Qb < 3(Smh) (SUS Bending) Case 1

3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2

4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2

5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2

6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2

7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3

8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4

9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5

10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6

11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7

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Tabular Results – SAFETY VALVE NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.

Analysis Time Stamp: Sat Sep 23 21:58:43 2006.

Model Notes

Load Case Report

Solution Data

ASME Code Stress Output Plots

ASME Overstressed Areas

Highest Primary Stress Ratios

Highest Secondary Stress Ratios

Highest Fatigue Stress Ratios

Stress Intensification Factors

Allowable Loads

Flexibilities

Graphical Results

Model Notes Input Echo: Model Type : Cylindrical Shell Parent Outside Diameter : 48.000 in. Thickness : 0.688 in. Fillet Along Shell : 0.500 in. Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 1.315 in. Thickness : 0.240 in. Length : 8.224 in. Nozzle Weld Length : 0.500 in. RePad Width : 4.000 in. RePad Thickness : 0.688 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 67.160 in. Distance from Bottom : 109.840 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi

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Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in. (NOT USED) Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1088.3 psi Vessel Pressure : 1088.3 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector : 0.000 0.000 1.000 Nozzle Orientation Vector : 0.000 1.000 0.000

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Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating (Fatigue Calc Performed) Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion)

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7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1

Solution Data Maximum Solution Row Size = 1554 Number of Nodes = 9444 Number of Elements = 3140 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 4295943931706271. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 154868293220201. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # FX FY FZ 1 0. -690. 1913428. 2 0. -690. 1913428. 3 0. 0. -3260. 4 0. 0. 0. 5 0. 0. 0. 6 0. 0. 0. 7 0. -690. 1913428. Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 4295943931706271. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 169 72613018143028. .1-to- 1% 505 20362590987501. .01-to-.1% 11 3954054177645. .001-to-.01% 360 164677717581. .0001-TO-.001% 55618 59830311.

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OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 154868293220201. 70-to-90% 0 0. 50-to-70% 8 83061024980278. 30-to-50% 26 58496018324935. 10-to-30% 365 25187989629765. 1-to-10% 2069 5031908829842. .1-to- 1% 2729 642071029000. .01-to-.1% 3695 58547066491. .001-to-.01% 3130 5784637537. .0001-TO-.001% 2601802 4005482.

ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7

ASME Overstressed Areas *** NO OVERSTRESSED NODES IN THIS MODEL ***

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Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 22,045 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 22% Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 16,388 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 63% Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 2,576 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 10% Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 40,422 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 41% Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 38,009 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 38% Branch removed from Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 3,065 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 11%

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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 54,202 195,000 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 27% Branch at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 32,728 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 63% Branch Transition Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 3,454 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 6% Pad Outer Edge Weld Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 58,577 195,000 Plot Reference: psi psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 30% Header Outside Pad Area Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 42,513 195,000 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 21% Branch removed from Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 4,820 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 9%

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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 36,586 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 10898.3 6% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 22,091 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 55243.8 3% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 1,727 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 39,539 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 8371.5 6% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 21,256 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 66876.1 3% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2

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Branch removed from Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,410 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2

Stress Intensification Factors Branch/Nozzle Sif Summary Peak Primary Secondary Axial : 1.480 1.223 2.192 Inplane : 1.489 1.206 2.206 Outplane: 0.278 0.424 0.428 Torsion : 1.997 2.147 2.959 Pressure: 1.042 1.065 1.543 The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 1.354 Inplane 1.689 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 1.689 Inplane 1.689 Outplane 1.689 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 4.842 Inplane 1.689 Outplane 4.842 Torsional

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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 31792. 3837. 5755. Inplane Moment (in. lb.) 7421. 633. 1343. Outplane Moment (in. lb.) 85193. 14656. 31091. Torsional Moment (in. lb.) 3970. 479. 719. Pressure (psi ) 1705.85 1088.28 1088.28 PRIMARY Maximum Conservative Realistic Load Type: Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 35510. 4274. 6411. Inplane Moment (in. lb.) 8267. 704. 1493. Outplane Moment (in. lb.) 43035. 6163. 13075. Torsional Moment (in. lb.) 4475. 539. 808. Pressure (psi ) 1703.36 1088.28 1088.28 NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.

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Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiff- nesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 1.315 in. Wall Thickness = 0.240 in. The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness

Finite Element Model

Finite Element Model

Elements at Discontinuity

1) Pl < 1.5(k)Smh (SUS Membrane) Case 1

2) Qb < 3(Smh) (SUS Bending) Case 1

3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2

4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2

5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2

6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2

7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3

8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4

9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5

10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6

11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7

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Tabular Results – PRESSURE INDICATOR NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.

Analysis Time Stamp: Sat Sep 23 21:56:43 2006.

Model Notes

Load Case Report

Solution Data

ASME Code Stress Output Plots

ASME Overstressed Areas

Highest Primary Stress Ratios

Highest Secondary Stress Ratios

Highest Fatigue Stress Ratios

Stress Intensification Factors

Allowable Loads

Flexibilities

Graphical Results

Model Notes Input Echo: Model Type : Cylindrical Shell Parent Outside Diameter : 48.000 in. Thickness : 0.688 in. Fillet Along Shell : 1.000 in. Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 2.375 in. Thickness : 0.436 in. Length : 8.224 in. Nozzle Weld Length : 1.000 in. RePad Width : 4.000 in. RePad Thickness : 1.100 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 49.450 in. Distance from Bottom : 127.550 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi

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Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in. (NOT USED) Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1088.3 psi Vessel Pressure : 1088.3 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector : 0.000 0.000 1.000 Nozzle Orientation Vector : 0.000 1.000 0.000

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Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating (Fatigue Calc Performed) Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion)

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7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1

Solution Data Maximum Solution Row Size = 1374 Number of Nodes = 5388 Number of Elements = 1788 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 2260959841002897. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 73008354295878. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # FX FY FZ 1 0. -1920. 1913380. 2 0. -1920. 1913380. 3 0. 0. -19315. 4 0. 0. 0. 5 0. 0. 0. 6 0. 0. 0. 7 0. -1920. 1913380. Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 2260959841002897. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 230 40789786900638. .1-to- 1% 284 11204893314808. .01-to-.1% 305 387555834680. .001-to-.01% 56 212116879908. .0001-TO-.001% 31452 124814867.

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OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 73008354295878. 70-to-90% 2 56021239410099. 50-to-70% 14 44699733559599. 30-to-50% 69 26999937560756. 10-to-30% 391 12349623514344. 1-to-10% 2168 2451306080096. .1-to- 1% 2966 257418927152. .01-to-.1% 3902 27272436386. .001-to-.01% 7093 2346311195. .0001-TO-.001% 1469682 4606847.

ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7

ASME Overstressed Areas *** NO OVERSTRESSED NODES IN THIS MODEL ***

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Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 16,573 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 16% Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 13,842 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 53% Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 2,655 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 10% Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 43,451 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 44% Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 37,954 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 38% Branch removed from Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 3,153 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 12%

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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 45,267 195,000 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 23% Branch at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 24,945 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 48% Branch Transition Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 4,074 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 7% Pad Outer Edge Weld Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 58,655 195,000 Plot Reference: psi psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 30% Header Outside Pad Area Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 43,002 195,000 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 22% Branch removed from Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 5,490 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 10%

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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 30,555 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 19649.2 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 16,838 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 172851.5 2% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,037 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 39,592 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 8338.4 6% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 21,501 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 63183.1 3% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2

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Branch removed from Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,745 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2

Stress Intensification Factors Branch/Nozzle Sif Summary Peak Primary Secondary Axial : 1.608 1.251 2.383 Inplane : 1.630 1.234 2.416 Outplane: 0.298 0.488 0.496 Torsion : 2.292 2.150 3.395 Pressure: 1.043 1.145 1.545 The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 1.939 Inplane 2.374 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 2.374 Inplane 2.374 Outplane 2.374 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.745 Inplane 2.374 Outplane 3.745 Torsional

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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 151117. 25878. 38817. Inplane Moment (in. lb.) 63651. 7707. 16350. Outplane Moment (in. lb.) 434539. 79965. 169632. Torsional Moment (in. lb.) 31216. 5346. 8018. Pressure (psi ) 2238.04 1088.28 1088.28 PRIMARY Maximum Conservative Realistic Load Type: Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 161974. 24856. 37284. Inplane Moment (in. lb.) 67811. 7358. 15609. Outplane Moment (in. lb.) 220458. 31735. 67319. Torsional Moment (in. lb.) 34756. 5333. 8000. Pressure (psi ) 2016.70 1088.28 1088.28 NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.

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Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiff- nesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 2.375 in. Wall Thickness = 0.436 in. The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness

Finite Element Model

Finite Element Model

Elements at Discontinuity

1) Pl < 1.5(k)Smh (SUS Membrane) Case 1

2) Qb < 3(Smh) (SUS Bending) Case 1

3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2

4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2

5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2

6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2

7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3

8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4

9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5

10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6

11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7

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Tabular Results – VENT NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.

Analysis Time Stamp: Sat Sep 23 21:55:26 2006.

Model Notes

Load Case Report

Solution Data

ASME Code Stress Output Plots

ASME Overstressed Areas

Highest Primary Stress Ratios

Highest Secondary Stress Ratios

Highest Fatigue Stress Ratios

Stress Intensification Factors

Allowable Loads

Flexibilities

Graphical Results

Model Notes Input Echo: Model Type : Cylindrical Shell Parent Outside Diameter : 48.000 in. Thickness : 0.688 in. Fillet Along Shell : 1.000 in. Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 2.375 in. Thickness : 0.436 in. Length : 8.224 in. Nozzle Weld Length : 1.000 in. RePad Width : 4.000 in. RePad Thickness : 1.100 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 31.740 in. Distance from Bottom : 145.260 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi

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Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in. (NOT USED) Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1088.3 psi Vessel Pressure : 1088.3 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector : 0.000 0.000 1.000 Nozzle Orientation Vector : 0.000 1.000 0.000

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Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating (Fatigue Calc Performed) Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion)

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7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1

Solution Data Maximum Solution Row Size = 1176 Number of Nodes = 5298 Number of Elements = 1758 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 2260959840151130. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 73008354252872. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # FX FY FZ 1 0. -1920. 1913380. 2 0. -1920. 1913380. 3 0. 0. -19315. 4 0. 0. 0. 5 0. 0. 0. 6 0. 0. 0. 7 0. -1920. 1913380. Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 2260959840151130. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 230 40789785583809. .1-to- 1% 284 11204892004910. .01-to-.1% 305 387555834680. .001-to-.01% 56 212116879908. .0001-TO-.001% 30912 126271357.

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OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 73008354252872. 70-to-90% 2 56021239344498. 50-to-70% 14 44699733493634. 30-to-50% 69 26999937240812. 10-to-30% 391 12349622944205. 1-to-10% 2168 2451305982331. .1-to- 1% 2966 257418924999. .01-to-.1% 3902 27272436376. .001-to-.01% 7066 2350575336. .0001-TO-.001% 1444481 4629580.

ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7

ASME Overstressed Areas *** NO OVERSTRESSED NODES IN THIS MODEL ***

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Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 16,523 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 16% Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 13,720 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 53% Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 2,651 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 10% Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 43,445 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 44% Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 37,981 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 38% Branch removed from Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 3,141 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 12%

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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 45,003 195,000 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 23% Branch at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 24,783 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 48% Branch Transition Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 4,051 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 7% Pad Outer Edge Weld Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 59,511 195,000 Plot Reference: psi psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 30% Header Outside Pad Area Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 42,896 195,000 Plot Reference: psi psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 21% Branch removed from Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 5,438 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 10%

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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 30,377 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 20006.4 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 16,728 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 176973.2 2% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,026 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 40,170 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 7987.3 7% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 21,448 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 63962.8 3% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2

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Branch removed from Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,719 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2

Stress Intensification Factors Branch/Nozzle Sif Summary Peak Primary Secondary Axial : 1.617 1.254 2.396 Inplane : 1.639 1.237 2.429 Outplane: 0.298 0.489 0.496 Torsion : 2.302 2.151 3.411 Pressure: 1.058 1.144 1.568 The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 1.939 Inplane 2.374 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 2.374 Inplane 2.374 Outplane 2.374 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.745 Inplane 2.374 Outplane 3.745 Torsional

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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 150769. 25978. 38967. Inplane Moment (in. lb.) 63500. 7737. 16412. Outplane Moment (in. lb.) 434417. 79869. 169427. Torsional Moment (in. lb.) 31219. 5379. 8069. Pressure (psi ) 2252.73 1088.28 1088.28 PRIMARY Maximum Conservative Realistic Load Type: Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 161555. 25047. 37570. Inplane Moment (in. lb.) 67631. 7414. 15728. Outplane Moment (in. lb.) 220353. 31705. 67257. Torsional Moment (in. lb.) 34732. 5385. 8077. Pressure (psi ) 2034.56 1088.28 1088.28 NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.

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Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiff- nesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 2.375 in. Wall Thickness = 0.436 in. The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness

Finite Element Model

Finite Element Model

Elements at Discontinuity

1) Pl < 1.5(k)Smh (SUS Membrane) Case 1

2) Qb < 3(Smh) (SUS Bending) Case 1

3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2

4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2

5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2

6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2

7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3

8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4

9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5

10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6

11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7

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Tabular Results – DREYN NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.

Analysis Time Stamp: Sat Sep 23 21:53:32 2006.

Model Notes

Load Case Report

Solution Data

ASME Code Stress Output Plots

ASME Overstressed Areas

Highest Primary Stress Ratios

Highest Secondary Stress Ratios

Highest Fatigue Stress Ratios

Stress Intensification Factors

Allowable Loads

Flexibilities

Graphical Results

Model Notes Input Echo: Model Type : Cylindrical Shell Parent Outside Diameter : 48.000 in. Thickness : 0.688 in. Fillet Along Shell : 1.000 in. Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 4.500 in. Thickness : 0.674 in. Length : 8.224 in. Nozzle Weld Length : 1.000 in. RePad Width : 4.000 in. RePad Thickness : 1.200 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 14.410 in. Distance from Bottom : 162.590 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi

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Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in. (NOT USED) Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1090.0 psi Vessel Pressure : 1090.0 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector : 0.000 0.000 1.000 Nozzle Orientation Vector : 0.000 -1.000 0.000

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Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed. THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating (Fatigue Calc Performed) Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion)

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7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1

Solution Data Maximum Solution Row Size = 870 Number of Nodes = 3078 Number of Elements = 1018 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 1067930861985906. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 23954670027870. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # FX FY FZ 1 0. 4508. 1916348. 2 0. 4508. 1916348. 3 0. 0. -107195. 4 0. 0. 0. 5 0. 0. 0. 6 0. 0. 0. 7 0. 4508. 1916348. Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 1067930861985906. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 217 25770767440426. .1-to- 1% 162 6738753807609. .01-to-.1% 360 417757334730. .001-to-.01% 220 23442179964. .0001-TO-.001% 17508 106026062.

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OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 4 23820449237183. 70-to-90% 26 18754250496661. 50-to-70% 47 13966185990012. 30-to-50% 154 9172528380065. 10-to-30% 642 4009353278465. 1-to-10% 2024 949099084778. .1-to- 1% 3434 89909508913. .01-to-.1% 7690 7525601847. .001-to-.01% 7535 1048777024. .0001-TO-.001% 823413 3827609.

ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7

ASME Overstressed Areas *** NO OVERSTRESSED NODES IN THIS MODEL ***

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Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 18,168 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 18% Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 14,361 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 55% Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 4,317 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 16% Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 44,297 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 45% Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 39,872 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 40%

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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 46,181 195,000 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 23% Branch at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 27,251 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 53% Branch Transition Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 6,875 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 13% Pad Outer Edge Weld Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 63,783 195,000 Plot Reference: psi psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 32% Header Outside Pad Area Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 63,313 195,000 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 32%

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Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 31,172 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 18477.3 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 18,394 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 125706.0 3% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 3,438 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 43,053 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 6502.6 7% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 31,657 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 17621.2 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2

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Stress Intensification Factors Branch/Nozzle Sif Summary Peak Primary Secondary Axial : 1.638 1.271 2.427 Inplane : 1.675 1.254 2.482 Outplane: 0.375 0.594 0.751 Torsion : 2.403 2.187 3.560 Pressure: 1.132 1.165 1.677 The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 2.997 Inplane 3.669 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 3.669 Inplane 3.669 Outplane 3.669 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.745 Inplane 3.669 Outplane 3.745 Torsional

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Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 424782. 66379. 99568. Inplane Moment (in. lb.) 358275. 39588. 83979. Outplane Moment (in. lb.) 1764885. 322184. 683456. Torsional Moment (in. lb.) 215483. 33673. 50509. Pressure (psi ) 2051.99 1090.02 1090.02 PRIMARY Maximum Conservative Realistic Load Type: Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 438902. 64391. 96587. Inplane Moment (in. lb.) 370939. 38481. 81630. Outplane Moment (in. lb.) 1115420. 155394. 329640. Torsional Moment (in. lb.) 195135. 28628. 42942. Pressure (psi ) 1946.91 1090.02 1090.02 NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.

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Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiff- nesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 4.500 in. Wall Thickness = 0.674 in. The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness

Finite Element Model

Finite Element Model

Elements at Discontinuity

1) Pl < 1.5(k)Smh (SUS Membrane) Case 1

2) Qb < 3(Smh) (SUS Bending) Case 1

3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2

4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2

5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2

6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2

7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3

8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4

9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5

10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6

11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7

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Tabular Results – KICKER NOZZLE 2 Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.

Analysis Time Stamp: Sat Sep 23 21:51:30 2006.

Model Notes

Load Case Report

Solution Data

ASME Code Stress Output Plots

ASME Overstressed Areas

Highest Primary Stress Ratios

Highest Secondary Stress Ratios

Highest Fatigue Stress Ratios

Stress Intensification Factors

Allowable Loads

Flexibilities

Graphical Results

Model Notes Input Echo: Model Type : Cylindrical Shell Parent Outside Diameter : 48.000 in. Thickness : 0.688 in. Fillet Along Shell : 1.000 in. Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 14.000 in. Thickness : 1.406 in. Length : 19.034 in. Nozzle Weld Length : 1.000 in. RePad Width : 6.000 in. RePad Thickness : 1.000 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 138.024 in. Distance from Bottom : 38.976 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi

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Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in. (NOT USED) Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1089.2 psi Vessel Pressure : 1089.2 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector : 0.000 0.000 1.000 Nozzle Orientation Vector : -1.000 0.000 0.000

Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed.

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THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating (Fatigue Calc Performed) Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion) 7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1

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Solution Data Maximum Solution Row Size = 864 Number of Nodes = 2028 Number of Elements = 668 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 570809133119139. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 17771940538827. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # FX FY FZ 1 29191. 0. 1914718. 2 29191. 0. 1914718. 3 0. 0. -2164368. 4 0. 0. 0. 5 0. 0. 0. 6 0. 0. 0. 7 29191. 0. 1914718. Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 570809133119139. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 2 69926728300522. 1-to-10% 201 18847557330940. .1-to- 1% 410 1428819278905. .01-to-.1% 300 251646588286. .001-to-.01% 56 25768600257. .0001-TO-.001% 11198 110503057. OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 8 16918108629091. 70-to-90% 31 13930091981812. 50-to-70% 45 10316249594375. 30-to-50% 93 7060985608352. 10-to-30% 516 2980979810043. 1-to-10% 2391 614741859315. .1-to- 1% 8469 58244265101. .01-to-.1% 7898 7931343623. .001-to-.01% 3033 758503730. .0001-TO-.001% 531125 5104309.

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ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7

ASME Overstressed Areas *** NO OVERSTRESSED NODES IN THIS MODEL ***

Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 24,632 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 25% Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 24,487 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 95%

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Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 7,803 25,650 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 30% Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 42,347 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 43% Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 38,392 97,500 Plot Reference: psi psi 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 39%

Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 42,293 195,000 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 21% Branch at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 38,759 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 75% Branch Transition Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 9,007 51,300 Plot Reference: psi psi 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 17% Pad Outer Edge Weld

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Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 63,431 195,000 Plot Reference: psi psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 32% Header Outside Pad Area Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 48,924 195,000 Plot Reference: psi psi 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 25%

Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 28,548 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 24208.0 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 26,163 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 31643.1 4% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 4,504 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2

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Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 42,816 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 6610.0 7% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 24,462 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 38892.4 4% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2

Stress Intensification Factors Branch/Nozzle Sif Summary Peak Primary Secondary Axial : 1.306 1.249 1.935 Inplane : 1.351 1.183 2.002 Outplane: 0.495 0.966 0.990 Torsion : 1.971 2.393 2.920 Pressure: 1.127 1.115 1.670 The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 48.000 in. Pipe Thk: 0.688 in. Z approx: 1209.541 cu.in. Z exact : 1192.456 cu.in.

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B31.3 Peak Stress Sif .... 0.000 Axial 6.380 Inplane 7.825 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 7.825 Inplane 7.825 Outplane 7.825 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.829 Inplane 7.825 Outplane 3.829 Torsional

Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 2101248. 171222. 256833. Inplane Moment (in. lb.) 6055901. 348936. 740206. Outplane Moment (in. lb.) 31427594. 2597257. 5509615. Torsional Moment (in. lb.) 3548691. 289168. 433753. Pressure (psi ) 1441.55 1089.15 1089.15 PRIMARY Maximum Conservative Realistic Load Type: Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 2122541. 32086. 48129. Inplane Moment (in. lb.) 6216399. 66449. 140959. Outplane Moment (in. lb.) 16106408. 389178. 825571. Torsional Moment (in. lb.) 4191913. 63369. 95053. Pressure (psi ) 1140.89 1089.15 1089.15 NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable.

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4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.

Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiff- nesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 14.000 in. Wall Thickness = 1.406 in. The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness

Finite Element Model

Finite Element Model

Elements at Discontinuity

1) Pl < 1.5(k)Smh (SUS Membrane) Case 1

2) Qb < 3(Smh) (SUS Bending) Case 1

3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2

4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2

5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2

6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2

7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3

8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4

9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5

10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6

11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7

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Tabular Results – PIG SIGNAL NOZZLE Results were generated with the finite element program FE/Pipe®. Stress results are post-processed in accordance with the rules specified in ASME Section III and ASME Section VIII, Division 2.

Analysis Time Stamp: Sat Sep 23 21:51:31 2006.

Model Notes

Load Case Report

Solution Data

ASME Code Stress Output Plots

ASME Overstressed Areas

Highest Primary Stress Ratios

Highest Secondary Stress Ratios

Highest Fatigue Stress Ratios

Stress Intensification Factors

Allowable Loads

Flexibilities

Graphical Results

Model Notes Input Echo: Model Type : Cylindrical Shell Parent Outside Diameter : 40.000 in. Thickness : 0.688 in. Fillet Along Shell : 1.000 in. Parent Properties: Cold Allowable : 65000.0 psi Hot Allowable : 65000.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in.(NOT USED) Nozzle Outside Diameter : 2.375 in. Thickness : 0.436 in. Length : 7.529 in. Nozzle Weld Length : 1.000 in. RePad Width : 4.000 in. RePad Thickness : 1.000 in. Nozzle Tilt Angle : 0.000 deg. Distance from Top : 55.000 in. Distance from Bottom : 55.000 in. Nozzle Properties Cold Allowable : 17100.0 psi Hot Allowable : 17100.0 psi Material ID #2 : Low Alloy Steel Ultimate Tensile (Amb) : 60000.0 psi

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Yield Strength (Amb) : 35000.0 psi Yield Strength (Hot) : 32900.0 psi Elastic Modulus (Amb) : 29400000.0 psi Poissons Ratio : 0.300 Weight Density : 0.283 lb./cu.in. (NOT USED) Design Operating Cycles : 0. Ambient Temperature (Deg.) : 70.00 Nozzle Pressure : 1088.6 psi Vessel Pressure : 1088.6 psi Both ends of the model are "fixed," except that one end is free axially so that longitudinal pressure stresses may be developed in the geometry. Stresses will be calculated in the weld elements surrounding the junction of the nozzle with the parent shell. This is typically done to get accurate values for the pressure stresses on the inside surface of the nozzle in the longitudinal plane. The effect of any external loads will overemphasized (too conservative) in this run. SIF's and allowable loads calculated in this run are for loads through the header. (Usually the SIF calc is for loads through the branch!) One end of the header is fixed and the other will be artificially loaded to reproduce the SIF test. The single end fixed boundary condition will then be used for any branch loading specified. Stresses are NOT averaged. Unstructured Mesh Generation used for this model. Nodal SMOOTHING has been deactivated. Some small geometry distortions may result that may affect solutions dominated by pressure stresses. No pad weld dimensions have been given for the pad connection to the shell. Few correlations have been performed to investigate the sensitivity of peak stresses to this value. Reasonable lengths have been assumed. Vessel Centerline Vector : 0.000 0.000 1.000 Nozzle Orientation Vector : 0.000 1.000 0.000

Load Case Report Inner and outer element temperatures are the same throughout the model. No thermal ratcheting calculations will be performed.

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THE 7 LOAD CASES ANALYZED ARE: 1 Sustained Sustained case run to satisfy Pl<1.5Sm limit, and Qb, the bending stress due to primary loads must be less than 3Smh as per Note 3 of Fig. NB-3222-1, and Table 4-120.1 /-------- Loads in Case 1 Pressure Case 1 2 Operating (Fatigue Calc Performed) Operating case run to compute the extreme operating stress state to be used in the shakedown and peak stress calculations. /-------- Loads in Case 2 Pressure Case 1 3 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 3 Force Case (Axial) 4 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 4 Force Case (Inplane) 5 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 5 Force Case (Outplane) 6 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 6 Force Case (Torsion) 7 Program Generated -- Force Only Case run to compute sif's and flexibilities. /-------- Loads in Case 7 Pressure Case 1

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Solution Data Maximum Solution Row Size = 1188 Number of Nodes = 3738 Number of Elements = 1238 Number of Solution Cases = 7 Largest On-Diagonal Stiffness = 1094857341535433. Smallest On-Diagonal Stiffness = 2. Largest Off-Diagonal Stiffness = 31822879340700. Smallest Off-Diagonal Stiffness = 1. Summation of Loads per Case Case # FX FY FZ 1 0. -1552. 1321342. 2 0. -1552. 1321342. 3 0. 0. -19315. 4 0. 0. 0. 5 0. 0. 0. 6 0. 0. 0. 7 0. -1552. 1321342. Equation Coefficient (Stiffness) Distribution) OnDiagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 1094857341535433. 70-to-90% 0 0. 50-to-70% 0 0. 30-to-50% 0 0. 10-to-30% 0 0. 1-to-10% 226 20637178549270. .1-to- 1% 221 6648541463801. .01-to-.1% 360 223528405812. .001-to-.01% 0 0. .0001-TO-.001% 21620 117408155. OFF Diagonal Number of Average Percentile Coefficients Stiffness 90-to-100% 1 31822879340700. 70-to-90% 4 25732179681041. 50-to-70% 16 18294382104461. 30-to-50% 77 11990350168488. 10-to-30% 495 5385767706974. 1-to-10% 2214 1138166925784. .1-to- 1% 3054 96904740640. .01-to-.1% 3274 11506959077. .001-to-.01% 9109 1109032375. .0001-TO-.001% 1009012 3797905.

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ASME Code Stress Output Plots 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 2) Qb < 3(Smh) (SUS,Bending) Case 1 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 7) Pl+Pb+Q+F < Sa (SIF,Outside) Case 3 8) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4 9) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5 10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6 11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7

ASME Overstressed Areas *** NO OVERSTRESSED NODES IN THIS MODEL ***

Highest Primary Stress Ratios Pad/Header at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 14,167 97,500 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 14% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1

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Branch at Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 11,360 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 44% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 Branch Transition Pl 1.5(k)Smh Primary Membrane Load Case 1 2,629 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 10% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 Pad Outer Edge Weld Pl 1.5(k)Smh Primary Membrane Load Case 1 35,684 97,500 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 36% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 Header Outside Pad Area Pl 1.5(k)Smh Primary Membrane Load Case 1 31,577 97,500 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 32% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1 Branch removed from Junction Pl 1.5(k)Smh Primary Membrane Load Case 1 3,018 25,650 Sect VIII Ref: AD-140, 4-112(i), 4-133, psi psi Fig. 4-130.1, Table 4-120.1 Sect III Ref: NB-3213.8, NB-3113.10, NB-3215 11% NB-3221.3, Table NB-3217-1, Fig. NB-3221-1 Plot Reference: 1) Pl < 1.5(k)Smh (SUS,Membrane) Case 1

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Highest Secondary Stress Ratios Pad/Header at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 37,238 195,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 19% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 Branch at Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 21,043 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 41% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 Branch Transition Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 3,913 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 7% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 Pad Outer Edge Weld Pl+Pb+Q 3(Smavg) Primary+Secondary (Outer) Load Case 2 49,869 195,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 25% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 4) Pl+Pb+Q < 3(Smavg) (OPE,Outside) Case 2

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Header Outside Pad Area Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 36,054 195,000 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 18% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2 Branch removed from Junction Pl+Pb+Q 3(Smavg) Primary+Secondary (Inner) Load Case 2 5,045 51,300 Sect VIII Ref: 4-120(b)(4),4-134,4-136.6, psi psi Fig. 4-130.1(Note 1) Sect III Ref: NB-3213.9, NB-3216, NB-3222.2 9% Fig. NB-3222-1 (Notes 3,4,6) NB-3227.6, NB-3228.4 Plot Reference: 3) Pl+Pb+Q < 3(Smavg) (OPE,Inside) Case 2

Highest Fatigue Stress Ratios Pad/Header at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 25,136 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 35781.1 4% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch at Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 14,204 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 361481.8 2% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2

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Branch Transition Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 1,956 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Pad Outer Edge Weld Pl+Pb+Q+F Sa Primary+Secondary+Peak (Outer) Load Case 2 33,662 568,400 Stress Concentration Factor = 1.350 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 14588.1 5% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 6) Pl+Pb+Q+F < Sa (EXP,Outside) Case 2 Header Outside Pad Area Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 18,027 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 135174.8 3% "B31" Fatigue Stress Allowable = 162500.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2 Branch removed from Junction Pl+Pb+Q+F Sa Primary+Secondary+Peak (Inner) Load Case 2 2,523 568,400 Stress Concentration Factor = 1.000 psi psi Strain Concentration Factor = 1.000 Cycles Allowed for this Stress = 1000000.0 0% "B31" Fatigue Stress Allowable = 42750.0 Markl Fatigue Stress Allowable = 245000.0 Sect VIII Ref: 4-112(l)(2),Fig.4-130.1,4-135 Sect III Ref: NB-3213.11, NB-3216, NB-3224.4 Plot Reference: 5) Pl+Pb+Q+F < Sa (EXP,Inside) Case 2

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Stress Intensification Factors Branch/Nozzle Sif Summary Peak Primary Secondary Axial : 1.596 1.249 2.365 Inplane : 1.620 1.228 2.399 Outplane: 0.341 0.572 0.580 Torsion : 2.276 2.135 3.371 Pressure: 1.064 1.128 1.576 The above stress intensification factors are to be used in a beam-type analysis of the piping system. Inplane, Outplane and Torsional sif's should be used with the matching branch pipe whose diameter and thickness is given below. The axial sif should be used to intensify the axial stress in the branch pipe calculated by F/A. The pressure sif should be used to intensify the nominal pressure stress in the PARENT or HEADER, calculated from PD/2T. Pipe OD : 40.000 in. Pipe Thk: 0.688 in. Z approx: 835.080 cu.in. Z exact : 820.968 cu.in. B31.3 Peak Stress Sif .... 0.000 Axial 1.767 Inplane 2.145 Outplane 1.000 Torsional B31.1 Peak Stress Sif .... 0.000 Axial 2.145 Inplane 2.145 Outplane 2.145 Torsional WRC 330 Peak Stress Sif .... 0.000 Axial 3.384 Inplane 2.145 Outplane 3.384 Torsional

Allowable Loads SECONDARY Maximum Conservative Realistic Load Type (Range): Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 150888. 29665. 44497. Inplane Moment (in. lb.) 63697. 8855. 18784. Outplane Moment (in. lb.) 371554. 71402. 151467. Torsional Moment (in. lb.) 31664. 6225. 9338. Pressure (psi ) 2653.77 1088.57 1088.57

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PRIMARY Maximum Conservative Realistic Load Type: Individual Simultaneous Simultaneous Occuring Occuring Occuring Axial Force (lb. ) 156944. 29146. 43718. Inplane Moment (in. lb.) 65798. 8640. 18329. Outplane Moment (in. lb.) 188188. 29991. 63620. Torsional Moment (in. lb.) 34211. 6353. 9530. Pressure (psi ) 2457.95 1088.57 1088.57 NOTES: 1) Maximum Individual Occuring Loads are the maximum allowed values of the respective loads if all other load components are zero, i.e. the listed axial force may be applied if the inplane, outplane and torsional moments, and the pressure are zero. 2) The Conservative Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A conservative stress combination equation is used that typically produces stresses within 50-70% of the allowable stress. 3) The Realistic Allowable Simultaneous loads are the maximum loads that can be applied simultaneously. A more realistic stress combination equation is used based on experience at Paulin Research. Stresses are typically produced within 80-105% of the allowable. 4) Secondary allowable loads are limits for expansion and operating piping loads. 5) Primary allowable loads are limits for weight, primary and sustained type piping loads.

Flexibilities The following stiffnesses should be used in a piping, "beam-type" analysis of the intersection. The stiff- nesses should be inserted at the surface of the branch/header or nozzle/vessel junction. The general characteristics used for the branch pipe should be: Outside Diameter = 2.375 in. Wall Thickness = 0.436 in. The following stiffness(es) were not generated because of errors in input or because the finite element model is stiffer than the piping model. Axial Translational Stiffness Inplane Rotational Stiffness Outplane Rotational Stiffness Torsional Rotational Stiffness

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Finite Element Model

Finite Element Model

Elements at Discontinuity

1) Pl < 1.5(k)Smh (SUS Membrane) Case 1

2) Qb < 3(Smh) (SUS Bending) Case 1

3) Pl+Pb+Q < 3(Smavg) (OPE Inside) Case 2

4) Pl+Pb+Q < 3(Smavg) (OPE Outside) Case 2

5) Pl+Pb+Q+F < Sa (EXP Inside) Case 2

6) Pl+Pb+Q+F < Sa (EXP Outside) Case 2

7) Pl+Pb+Q+F < Sa (SIF Outside) Case 3

8) Pl+Pb+Q+F < Sa (SIF Outside) Case 4

9) Pl+Pb+Q+F < Sa (SIF Outside) Case 5

10) Pl+Pb+Q+F < Sa (SIF Outside) Case 6

11) Pl+Pb+Q+F < Sa (SIF Outside) Case 7

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Index of Revisions

Rev.

Prepared, revised Checked Approved Remark, kind of revision

Name Date Name Name Date Status

0 HC 10-2006 IA TLT 10-2006 IFI FOR APPROVED