28714-07-01 Rev 1 Calculo FIMA

Table Of ContentsSettings Summary1.

Revision History2.

Pressure Summary3.

Thickness Summary4.

Weight Summary5.

Hydrostatic Test6.

Nozzle Summary7.

Nozzle Schedule8.

Seismic Code9.

Wind Code10.

Cylinder #111.

Cylinder #212.

Cylinder #313.

F&D Head #114.

Straight Flange on F&D Head #115.

F&D Head #216.

Air Inlet, Air Outlet, Press. Safety Valve, Vent w/Valve, Drain (N1, N2, S1, V1, D1)17.

Pressure Transmiter, Pressure Indicator (P1, P2)18.

Manhole (MH)19.

Level Gauge, Level Gauge (LI, L2)20.

Saddle21.

Lifting Lug22.

TAGs: HYI-V-1712 / BAI-V-8712 Doc. N° 28714-07

Rev. 1 1/70

Settings Summary

COMPRESS Build 6258

Units: U.S. Customary

Datum Line Location: 0.00" from right seam

Design

ASME Section VIII Division 1, 2007 Edition

Design or Rating: Get Thickness from PressureMinimum thickness: 1/16" per UG-16(b)Design for cold shut down only: NoDesign for lethal service (full radiography required): NoDesign nozzles for: Design P, find nozzle MAWP and MAPCorrosion weight loss: 100% of theoretical lossUG-23 Stress Increase: 1.00Skirt/legs stress increase: 1.0Minimum nozzle projection: 2.0000"Juncture calculations for α > 30 only: YesPreheat P-No 1 Materials > 1.25&#34 and <= 1.50" thick: NoButt welds are tapered per Figure UCS-66.3(a).

Hydro/Pneumatic Test

Shop Hydrotest Pressure: 1.3 times design PTest liquid specific gravity: 1.00Maximum stress during test: 90% of yield

Required Marking - UG-116

UG-116 (e) Radiography: RT3UG-116 (f) Postweld heat treatment: None

Code Cases\Interpretations

Use Code Case 2547: NoApply interpretation VIII-1-83-66: YesApply interpretation VIII-1-86-175: YesApply interpretation VIII-1-83-115: YesApply interpretation VIII-1-01-37: YesDisallow UG-20(f) exemptions: No

UG-22 Loadings

UG-22 (a) Internal or External Design Pressure : YesUG-22 (b) Weight of the vessel and normal contents under operating or test conditions: YesUG-22 (c) Superimposed static reactions from weight of attached equipment (external loads): No


Rev. 1 2/70

UG-22 (d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: YesUG-22 (f) Wind reactions: YesUG-22 (f) Seismic reactions: YesNote: UG-22 (b),(c) and (f) loads only considered when supports are present.


Rev. 1 3/70

Revision History

No. Date Operator Notes

0 9/12/2008 CHuillca New vessel created ASME Section VIII Division 1 [Build 6258]

1 10/14/2008 CHuillca Heads modified like As Built


Rev. 1 4/70

Pressure Summary

Pressure Summary for Chamber bounded by F&D Head #2 and F&D Head #1

IdentifierP

Design( psi)

T

Design(°F)

MAWP( psi)

MAP( psi)

MDMT(°F)

MDMTExemption

Total

Corrosion

Allowance(in)

ImpactTest

F&D Head #1 190.0 221.0 190.04 229.50 -27.0 Note 1 0.063 No

Straight Flange on F&D Head #1 190.0 221.0 237.98 275.48 -27.0 Note 2 0.063 No

Cylinder #1 190.0 221.0 201.85 234.16 -26.9 Note 3 0.063 No

Cylinder #2 190.0 221.0 201.85 234.16 -26.9 Note 3 0.063 No

Cylinder #3 190.0 221.0 201.85 234.16 -26.9 Note 3 0.063 No

F&D Head #2 190.0 221.0 193.73 235.41 -45.0 Note 4 0.063 No

Saddle 190.0 221.0 190.04 N/A N/A N/A N/A N/A

Level Gauge, Level Gauge (LI, L2) 190.0 221.0 249.65 300.32 -155.0 Note 5 0.063 No

Manhole (MH) 190.0 221.0 226.97 258.33 -39.0 Nozzle Note 6; PadNote 7 0.063 No

Air Inlet, Air Outlet, Press. Safety Valve, Vent w/Valve, Drain(N1, N2, S1, V1, D1) 190.0 221.0 240.59 275.47 -53.3 Note 8 0.063 No

Pressure Transmiter, Pressure Indicator (P1, P2) 190.0 221.0 240.59 275.47 -155.0 Note 9 0.063 No

Chamber design MDMT is -20.00°FChamber rated MDMT is -26.90°F @ 190.04 psi

Chamber MAWP hot & corroded is 190.04 psi @ 221.0°F

Chamber MAP cold & new is 229.50 psi @ 70.0°F

This pressure chamber is not designed for external pressure.

Notes for MDMT Rating:

Note # Exemption Details

1. Straight Flange governs MDMT

2. Material impact test exemption temperature from Fig UCS-66 Curve B = -7 °FFig UCS-66.1 MDMT reduction = 20 °F, (coincident ratio = 0.7998)

UCS-66 governing thickness =0.5 in

3. Material impact test exemption temperature from Fig UCS-66 Curve B = -7 °FFig UCS-66.1 MDMT reduction = 19.9 °F, (coincident ratio = 0.8006225)


4. Material impact test exemption temperature from Fig UCS-66 Curve B = -19.53 °FFig UCS-66.1 MDMT reduction = 25.5 °F, (coincident ratio = 0.7452073)


5. Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0.0198).

6. Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -13 °FFig UCS-66.1 MDMT reduction = 26 °F, (coincident ratio = 0.74016)

UCS-66 governing thickness =0.4375 in.

7. Pad impact test exemption temperature from Fig UCS-66 Curve B = -13 °FFig UCS-66.1 MDMT reduction = 26 °F, (coincident ratio = 0.74016)

UCS-66 governing thickness =0.4375 in.

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

9. Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0.01701).

Design notes are available on the Settings Summary page.


Rev. 1 5/70

Thickness Summary

ComponentIdentifier

Material Diameter(in)

Length(in)

Nominal t(in)

Design t(in)

JointE

Load

F&D Head #1 SA-516 70 72.00 ID 19.57 0.3923* 0.3923 1.0000 Internal

Straight Flange on F&D Head #1 SA-516 70 72.00 ID 0.59 0.5000 0.4124 1.0000 Internal

Cylinder #1 SA-516 70 72.00 ID 48.78 0.5000 0.4746 0.8500 Internal



F&D Head #2 SA-516 70 72.00 ID 20.13 0.3792* 0.3732 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


Rev. 1 6/70

Weight Summary

ComponentWeight ( lb) Contributed by Vessel Elements

MetalNew*

Metal

Corroded*Insulation &

Supports Lining Piping+ Liquid

OperatingLiquid

TestLiquid

F&D Head #1 654.72 552.21 0.00 0.00 0.00 1,897.75 1,876.83

Cylinder #1 1,571.48 1,376.23 0.00 0.00 0.00 7,194.49 7,169.52

Cylinder #2 3,806.55 3,333.60 0.00 0.00 0.00 17,418.92 17,358.60

Cylinder #3 3,806.38 3,333.45 0.00 0.00 0.00 17,418.96 17,358.62

F&D Head #2 579.60 485.15 0.00 0.00 0.00 1,864.17 1,843.18

Saddle 944.00 944.00 0.00 0.00 0.00 0.00 0.00

TOTAL: 11,362.72 10,024.65 0.00 0.00 0.00 45,794.29 45,606.73

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

Component

Weight ( lb) Contributed by Attachments

Body Flanges Nozzles &Flanges Packed

BedsTrays &

SupportsRings &

ClipsVerticalLoads

New Corroded New Corroded

F&D Head #1 0.00 0.00 1.51 1.27 0.00 0.00 0.00 0.00

Cylinder #1 0.00 0.00 9.54 8.95 0.00 0.00 13.41 0.00

Cylinder #2 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00

Cylinder #3 0.00 0.00 0.62 0.50 0.00 0.00 13.41 0.00

F&D Head #2 0.00 0.00 594.84 588.11 0.00 0.00 0.00 0.00

TOTAL: 0.00 0.00 606.51 598.84 0.00 0.00 26.82 0.00

Vessel operating weight, Corroded: 56,445 lbVessel operating weight, New: 57,790 lbVessel empty weight, Corroded: 10,650 lbVessel empty weight, New: 11,996 lbVessel test weight, New: 57,603 lb

Vessel center of gravity location - from datum - lift condition

Vessel Lift Weight, New: 11,996 lbCenter of Gravity: 134.81"

Vessel Capacity

Vessel Capacity** (New): 5,464 US galVessel Capacity** (Corroded): 5,486 US gal**The vessel capacity does not include volume of nozzle, piping or other attachments.


Rev. 1 7/70

Hydrostatic Test

Shop test pressure determination for Chamber bounded by F&D Head #2 and F&D Head #1 based on design Pper UG-99(b)

Shop hydrostatic test gauge pressure is 247 psi at 70 °F (the chamber design P = 190 psi)

The shop test is performed with the vessel in the horizontal position.

Identifier

Localtest

pressurepsi

Testliquidstaticheadpsi

UG-99stressratio

UG-99pressure

factor

Stressduring

testpsi

Allowabletest

stresspsi

Stressexcessive?

F&D Head #1 (1) 249.894 2.894 1 1.30 16,616 34,200 No

Straight Flange on F&D Head #1 249.894 2.894 1 1.30 18,117 34,200 No

Cylinder #1 249.894 2.894 1 1.30 18,117 34,200 No

Cylinder #2 249.894 2.894 1 1.30 18,117 34,200 No

Cylinder #3 249.894 2.894 1 1.30 18,117 34,200 No

F&D Head #2 249.894 2.894 1 1.30 16,086 34,200 No

Air Inlet, Air Outlet, Press. Safety Valve, Ventw/Valve, Drain (N1, N2, S1, V1, D1) 247.277 0.277 1 1.30 20,146 47,250 No

Level Gauge, Level Gauge (LI, L2) 249.608 2.608 1 1.30 17,961 48,600 No

Manhole (MH) 248.937 1.937 1 1.30 19,546 47,250 No

Pressure Transmiter, Pressure Indicator (P1, P2) 247.277 0.277 1 1.30 17,912 48,600 No

Notes:(1) F&D Head #1 limits the UG-99 stress ratio.(2) PL stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399, pages 77-82.(3) VIII-2, AD-151.1(b) used as the basis for nozzle allowable test stress.(4) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-mostflange.

The field test condition has not been investigated for the Chamber bounded by F&D Head #2 and F&D Head #1.

The test temperature of 70 °F is warmer than the minimum recommended temperature of 3.1 °F so the brittle fractureprovision of UG-99(h) has been met.


Rev. 1 8/70

Nozzle Summary

Nozzlemark

OD(in)

tn

(in)Req t

n(in)

A1? A2?Shell Reinforcement

Pad Corr(in)

Aa/A

r(%)

Nom t(in)

Design t(in)

User t(in)

Width(in)

tpad(in)

LI, L2 1.75 0.3500 0.1250 Yes Yes 0.3923* N/A N/A N/A 0.0625 Exempt

MH 20.00 0.5000 0.4464 Yes Yes 0.3792* 0.3157 4.0000 0.5000 0.0625 100.0

N1, N2, S1, V1, D1 2.38 0.3440 0.2254 Yes Yes 0.5000 N/A N/A N/A 0.0625 Exempt

P1, P2 1.25 0.2875 0.1250 Yes Yes 0.5000 N/A N/A N/A 0.0625 Exempt

tn: Nozzle thicknessReq tn: Nozzle thickness required per UG-45/UG-16Nom t: Vessel wall thicknessDesign t: Required vessel wall thickness due to pressure + corrosion allowance per UG-37User t: Local vessel wall thickness (near opening)Aa: Area available per UG-37, governing conditionAr: Area required per UG-37, governing conditionCorr: Corrosion allowance on nozzle wall* Head minimum thickness after forming


Rev. 1 9/70

Nozzle Schedule

Nozzlemark

Service SizeMaterials

Nozzle Impact Norm FineGrain Pad Impact Norm Fine

Grain Flange

LI, L2 Level Gauge, Level Gauge 0.750" Class6000 - threaded SA-105 No No No N/A N/A N/A N/A N/A

MH Manhole 20" Sch 30 (XS) SA-106 BSmls pipe No No No SA-516

70 No No No

WNA105Class150

N1, N2, S1,V1, D1

Air Inlet, Air Outlet, Press.Safety Valve, Vent w/Valve,Drain

2" Sch 160 SA-106 BSmls pipe No No No N/A N/A N/A N/A

WNA105Class150

P1, P2 Pressure Transmiter, PressureIndicator

0.375" Class6000 - threaded SA-105 No No No N/A N/A N/A N/A N/A


Rev. 1 10/70

Seismic Code

Seismic calculations are reported in the saddle report.


Rev. 1 11/70

Wind Code

Wind calculations are reported in the saddle report.


Rev. 1 12/70

Cylinder #1


Component: CylinderMaterial specification: SA-516 70 (II-D p. 18, ln. 22)Material impact test exemption temperature from Fig UCS-66 Curve B = -7 °FFig UCS-66.1 MDMT reduction = 19.9 °F, (coincident ratio = 0.8006225)UCS-66 governing thickness = 0.5 in

Internal design pressure: P = 190 psi @ 221°F

Static liquid head:

Ps =2.8963 psi (SG=1.0000, Hs=80.2357" Operating head)Pth =2.8940 psi (SG=1.0000, Hs=80.1732", Horizontal test head)

Corrosion allowance: Inner C = 0.0625" Outer C = 0.0000"

Design MDMT = -20.00°F No impact test performedRated MDMT = -26.90°F Material is not normalized

Material is not produced to Fine Grain PracticePWHT is not performed

Radiography: Longitudinal joint - Spot UW-11(b) Type 1Left circumferential joint - Full UW-11(a) Type 1Right circumferential joint - Spot UW-11(b) Type 1

Estimated weight: New = 1572.1055 lb corr = 1376.7781 lbCapacity: New = 859.7660 gal corr = 862.7538 galID = 72.0000"Length Lc = 48.7795"t = 0.5000"

Design thickness, (at 221.00°F) UG-27(c)(1)

t = P*R/(S*E - 0.60*P) + Corrosion= 192.90*36.0625/(20000*0.85 - 0.60*192.90) + 0.0625= 0.4746"

Maximum allowable working pressure, (at 221.00°F) UG-27(c)(1)

P = S*E*t/(R + 0.60*t) - Ps= 20000*0.85*0.4375 / (36.0625 + 0.60*0.4375) - 2.8963= 201.8525 psi

Maximum allowable pressure, (at 70.00°F) UG-27(c)(1)

P = S*E*t/(R + 0.60*t)= 20000*0.85*0.5000 / (36.0000 + 0.60*0.5000)= 234.1598 psi

% Extreme fiber elongation - UCS-79(d)

= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 0.5000 / 36.2500) * (1 - 36.2500 / ∞)= 0.6897 %


Rev. 1 13/70

Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2)A = 0.125 / (Ro / t)

= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHC = 13809.5254 psi

Allowable Compressive Stress, Hot and New- ScHN, (table CS-2)A = 0.125 / (Ro / t)

= 0.125 / (36.5000 / 0.5000)= 0.001712

B = 14347.6934 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHN = 14347.6934 psi

Allowable Compressive Stress, Cold and New- ScCN, (table CS-2)A = 0.125 / (Ro / t)

= 0.125 / (36.5000 / 0.5000)= 0.001712

B = 14347.6934 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCN = 14347.6934 psi

Allowable Compressive Stress, Cold and Corroded- ScCC, (table CS-2)A = 0.125 / (Ro / t)

= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCC = 13809.5254 psi

Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2)A = 0.125 / (Ro / t)

= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi


Rev. 1 14/70

ScVC = 13809.5254 psi


Rev. 1 15/70

Cylinder #2




Static liquid head:





Radiography: Longitudinal joint - Spot UW-11(b) Type 1Left circumferential joint - Spot UW-11(b) Type 1Right circumferential joint - Spot UW-11(b) Type 1





P = S*E*t/(R + 0.60*t) - Ps= 20000*0.85*0.4375 / (36.0625 + 0.60*0.4375) - 2.8963= 201.8525 psi


P = S*E*t/(R + 0.60*t)= 20000*0.85*0.5000 / (36.0000 + 0.60*0.5000)= 234.1598 psi


= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 0.5000 / 36.2500) * (1 - 36.2500 / ∞)= 0.6897 %


Rev. 1 16/70


= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHC = 13809.5254 psi


= 0.125 / (36.5000 / 0.5000)= 0.001712

B = 14347.6934 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHN = 14347.6934 psi


= 0.125 / (36.5000 / 0.5000)= 0.001712

B = 14347.6934 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCN = 14347.6934 psi


= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCC = 13809.5254 psi


= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi


Rev. 1 17/70

ScVC = 13809.5254 psi


Rev. 1 18/70

Cylinder #3




Static liquid head:





Radiography: Longitudinal joint - Spot UW-11(b) Type 1Left circumferential joint - Spot UW-11(b) Type 1Right circumferential joint - Full UW-11(a) Type 1





P = S*E*t/(R + 0.60*t) - Ps= 20000*0.85*0.4375 / (36.0625 + 0.60*0.4375) - 2.8963= 201.8525 psi


P = S*E*t/(R + 0.60*t)= 20000*0.85*0.5000 / (36.0000 + 0.60*0.5000)= 234.1598 psi


= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 0.5000 / 36.2500) * (1 - 36.2500 / ∞)= 0.6897 %


Rev. 1 19/70


= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHC = 13809.5254 psi


= 0.125 / (36.5000 / 0.5000)= 0.001712

B = 14347.6934 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHN = 14347.6934 psi


= 0.125 / (36.5000 / 0.5000)= 0.001712

B = 14347.6934 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCN = 14347.6934 psi


= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCC = 13809.5254 psi


= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi


Rev. 1 20/70

ScVC = 13809.5254 psi


Rev. 1 21/70

F&D Head #1

ASME Section VIII, Division 1, 2007 Edition

Component: F&D HeadMaterial Specification: SA-516 70 (II-D p.18, ln. 22)Straight Flange governs MDMT

Internal design pressure: P = 190 psi @ 221 °F

Static liquid head:

Ps= 2.8963 psi (SG=1, Hs=80.2357" Operating head)Pth= 2.894 psi (SG=1, Hs=80.1732" Horizontal test head)

Corrosion allowance: Inner C = 0.0625" Outer C = 0"

Design MDMT = -20°F No impact test performedRated MDMT = -27°F Material is not normalized

Material is not produced to fine grain practicePWHT is not performedDo 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 = 654.7 lb corr = 552.2 lbCapacity*: new = 225.1 US gal corr = 226.6 US gal* includes straight flange

Inner diameter = 72"Crown radius L = 52.17"Knuckle radius r = 10.43"Minimum head thickness = 0.3923"Straight flange length Lsf = 0.59"Nominal straight flange thickness tsf = 0.5"Results Summary

The governing condition is internal pressure.Minimum thickness per UG-16 = 0.0625" + 0.0625" = 0.125"Design thickness due to internal pressure (t) = 0.3923"Maximum allowable working pressure (MAWP) = 190.04 psiMaximum allowable pressure (MAP) = 229.5 psi

M (Corroded)

M=1/4*[3 + (L/r)1/2]=1/4*[3 + (52.2325/10.4925)1/2]=1.30779

M (New)

M=1/4*[3 + (L/r)1/2]=1/4*[3 + (52.17/10.43)1/2]=1.309124


Rev. 1 22/70

Design thickness for internal pressure, (Corroded at 221 °F) Appendix 1-4(d)

t = P*L*M / (2*S*E - 0.2*P) + Corrosion= 192.9*52.2325*1.3078 / (2*20,000*1 - 0.2*192.9) + 0.0625= 0.3922"

The head internal pressure design thickness is 0.3923".

Maximum allowable working pressure, (Corroded at 221 °F) Appendix 1-4(d)

P = 2*S*E*t / (L*M + 0.2*t) - Ps= 2*20,000*1*0.3298 / (52.2325*1.3078 + 0.2*0.3298) - 2.9= 190.04 psi

The maximum allowable working pressure (MAWP) is 190.04 psi.

Maximum allowable pressure, (New at 70 °F) Appendix 1-4(d)

P = 2*S*E*t / (L*M + 0.2*t) - Ps= 2*20,000*1*0.3923 / (52.17*1.3091 + 0.2*0.3923) - 0= 229.5 psi

The maximum allowable pressure (MAP) is 229.5 psi.


= (75*t / Rf)*(1 - Rf / Ro)= (75*0.5 / 10.68)*(1 - 10.68 / ∞)= 3.5112%

The extreme fiber elongation does not exceed 5%.


Rev. 1 23/70

Straight Flange on F&D Head #1


Component: Straight FlangeMaterial specification: SA-516 70 (II-D p. 18, ln. 22)Material impact test exemption temperature from Fig UCS-66 Curve B = -7 °FFig UCS-66.1 MDMT reduction = 20 °F, (coincident ratio = 0.7998)UCS-66 governing thickness = 0.5 in


Static liquid head:





Radiography: Longitudinal joint - Seamless No RTCircumferential joint - Full UW-11(a) Type 1





P = S*E*t/(R + 0.60*t) - Ps= 20000*1.00*0.4375 / (36.0625 + 0.60*0.4375) - 2.8963= 237.9847 psi


P = S*E*t/(R + 0.60*t)= 20000*1.00*0.5000 / (36.0000 + 0.60*0.5000)= 275.4821 psi


= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 0.5000 / 36.2500) * (1 - 36.2500 / ∞)= 0.6897 %


Rev. 1 24/70


= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHC = 13809.5254 psi


= 0.125 / (36.5000 / 0.5000)= 0.001712

B = 14347.6934 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHN = 14347.6934 psi


= 0.125 / (36.5000 / 0.5000)= 0.001712

B = 14347.6934 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCN = 14347.6934 psi


= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCC = 13809.5254 psi


= 0.125 / (36.5000 / 0.4375)= 0.001498

B = 13809.5254 psi

S = 20000.0000 / 1.0000= 20000.0000 psi


Rev. 1 25/70

ScVC = 13809.5254 psi


Rev. 1 26/70

F&D Head #2

ASME Section VIII, Division 1, 2007 Edition

Component: F&D HeadMaterial Specification: SA-516 70 (II-D p.18, ln. 22)Material impact test exemption temperature from Fig UCS-66 Curve B = -19.53 °FFig UCS-66.1 MDMT reduction = 25.5 °F, (coincident ratio = 0.7452073)UCS-66 governing thickness = 0.3792 in

Internal design pressure: P = 190 psi @ 221 °F

Static liquid head:

Ps= 2.8963 psi (SG=1, Hs=80.2357" Operating head)Pth= 2.894 psi (SG=1, Hs=80.1732" Horizontal test head)

Corrosion allowance: Inner C = 0.0625" Outer C = 0"

Design MDMT = -20°F No impact test performedRated MDMT = -45.03°F Material is not normalized

Material is not produced to fine grain practicePWHT is not performedDo 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 = 579.6 lb corr = 485.2 lbCapacity: new = 215.5 US gal corr = 218.2 US gal

Inner diameter = 72"Crown radius L = 48.82"Knuckle radius r = 9.45"Minimum head thickness = 0.3792"Results Summary

The governing condition is internal pressure.Minimum thickness per UG-16 = 0.0625" + 0.0625" = 0.125"Design thickness due to internal pressure (t) = 0.3732"Maximum allowable working pressure (MAWP) = 193.73 psiMaximum allowable pressure (MAP) = 235.41 psi

M (Corroded)

M=1/4*[3 + (L/r)1/2]=1/4*[3 + (48.8825/9.5125)1/2]=1.316721

M (New)

M=1/4*[3 + (L/r)1/2]=1/4*[3 + (48.82/9.45)1/2]=1.318228


Rev. 1 27/70

Design thickness for internal pressure, (Corroded at 221 °F) Appendix 1-4(d)

t = P*L*M / (2*S*E - 0.2*P) + Corrosion= 192.9*48.8825*1.3167 / (2*20,000*1 - 0.2*192.9) + 0.0625= 0.3732"

The head internal pressure design thickness is 0.3732".

Maximum allowable working pressure, (Corroded at 221 °F) Appendix 1-4(d)

P = 2*S*E*t / (L*M + 0.2*t) - Ps= 2*20,000*1*0.3167 / (48.8825*1.3167 + 0.2*0.3167) - 2.9= 193.73 psi

The maximum allowable working pressure (MAWP) is 193.73 psi.

Maximum allowable pressure, (New at 70 °F) Appendix 1-4(d)

P = 2*S*E*t / (L*M + 0.2*t) - Ps= 2*20,000*1*0.3792 / (48.82*1.3182 + 0.2*0.3792) - 0= 235.41 psi

The maximum allowable pressure (MAP) is 235.41 psi.


= (75*t / Rf)*(1 - Rf / Ro)= (75*0.3792 / 9.6396)*(1 - 9.6396 / ∞)= 2.9503%

The extreme fiber elongation does not exceed 5%.


Rev. 1 28/70

Air Inlet, Air Outlet, Press. Safety Valve, Vent w/Valve, Drain (N1, N2, S1, V1, D1)


tw(lower) = 0.5 inLeg41 = 0.3543 in

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

Located on: Cylinder #1Liquid static head included: 0.277 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 14, ln. 5)Nozzle longitudinal joint efficiency: 1Nozzle description: 2" Sch 160Flange description: 2 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -53.3°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 253.7 psi @ 221°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FNozzle orientation: 0°Local vessel minimum thickness: 0.5 inNozzle center line offset to datum line: 252.7513 inEnd of nozzle to shell center: 44.1732 inNozzle inside diameter, new: 1.687 inNozzle nominal wall thickness: 0.344 inNozzle corrosion allowance: 0.0625 inProjection available outside vessel, Lpr: 6.9232 inProjection available outside vessel to flange face, Lf: 7.6732 in


Rev. 1 29/70

Reinforcement Calculations for Internal Pressure

The vessel wall thickness governs the MAWP of this nozzle.

UG-37 Area Calculation Summary(in2)

For P = 240.87 psi @ 221 °F

UG-45 NozzleWall

ThicknessSummary (in)The nozzle passes

UG-45

Arequired

Aavailable A1 A2 A3 A5

Awelds treq tmin

This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0.1973 0.301

Weld Failure Path Analysis Summary

The nozzle is exempt from weld strengthcalculations per UW-15(b)(2)

UW-16 Weld Sizing Summary

Weld description Required weldthroat size (in)

Actual weldthroat size (in) Status

Nozzle to shell fillet (Leg41) 0.1971 0.248 weld size is adequate

Calculations for internal pressure 240.87 psi @ 221 °F

Fig UCS-66.2 general note (1) applies.

Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0.04256).

Nozzle UCS-66 governing thk: 0.301 inNozzle rated MDMT: -155 °F

Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 1.812 inNormal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.7038 in

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

trn = P*Rn/(Sn*E - 0.6*P)= 240.8718*0.906/(17,100*1 - 0.6*240.8718)= 0.0129 in

Required thickness tr from UG-37(a)

tr = P*R/(S*E - 0.6*P)


Rev. 1 30/70

= 240.8718*36.0625/(20,000*1 - 0.6*240.8718)= 0.4375 in

This opening does not require reinforcement per UG-36(c)(3)(a)

UW-16(c) Weld Check

Fillet weld: tmin = lesser of 0.75 or tn or t = 0.2815 intc(min) = lesser of 0.25 or 0.7*tmin = 0.1971 intc(actual) = 0.7*Leg = 0.7*0.3543 = 0.248 in

The fillet weld size is satisfactory.

Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (c-e).

UG-45 Nozzle Neck Thickness Check

Wall thickness per UG-45(a): tr1 = 0.0754 in (E =1)Wall thickness per UG-45(b)(1): tr2 = 0.5 inWall thickness per UG-16(b): tr3 = 0.125 inStandard wall pipe per UG-45(b)(4): tr4 = 0.1973 inThe greater of tr2 or tr3: tr5 = 0.5 inThe lesser of tr4 or tr5: tr6 = 0.1973 in


Rev. 1 31/70

Required per UG-45 is the larger of tr1 or tr6 = 0.1973 in

Available nozzle wall thickness new, tn = 0.875*0.344 = 0.301 in

The nozzle neck thickness is adequate.

Reinforcement Calculations for MAP

The vessel wall thickness governs the MAP of this nozzle.


For P = 275.47 psi @ 70 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin










Parallel to the vessel wall: (Rn + tn + t )= 1.6875 inNormal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.86 in


trn = P*Rn/(Sn*E - 0.6*P)= 275.4723*0.8435/(17,100*1 - 0.6*275.4723)= 0.0137 in


tr = P*R/(S*E - 0.6*P)= 275.4723*36/(20,000*1 - 0.6*275.4723)= 0.5 in


Rev. 1 32/70


UW-16(c) Weld Check










Rev. 1 33/70

Pressure Transmiter, Pressure Indicator (P1, P2)


tw(lower) = 0.5 inLeg41 = 0.3125 in


Located on: Cylinder #3Liquid static head included: 0.277 psiNozzle material specification: SA-105 (II-D p. 18, ln. 8)Nozzle longitudinal joint efficiency: 1Nozzle description: 0.375" Class 6000 - threadedNozzle orientation: 0°Local vessel minimum thickness: 0.5 inNozzle center line offset to datum line: 90.55 inEnd of nozzle to shell center: 38.5 inNozzle inside diameter, new: 0.675 inNozzle nominal wall thickness: 0.2875 inNozzle corrosion allowance: 0.0625 inProjection available outside vessel, Lpr: 2 in


Rev. 1 34/70




For P = 240.87 psi @ 221 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin














trn = P*Rn/(Sn*E - 0.6*P)= 240.8718*0.4/(20,000*1 - 0.6*240.8718)= 0.0049 in


tr = P*R/(S*E - 0.6*P)= 240.8718*36.0625/(20,000*1 - 0.6*240.8718)= 0.4375 in


Rev. 1 35/70


UW-16(c) Weld Check




ASME B16.11 Coupling Wall Thickness Check

Wall thickness req'd per ASME B16.11 2.1.1: tr1 = 0.07 in (E =1)Wall thickness per UG-16(b): tr3 = 0.125 in


Rev. 1 36/70

Available nozzle wall thickness new, tn = 0.2875 in





For P = 275.47 psi @ 70 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin












trn = P*Rn/(Sn*E - 0.6*P)= 275.4723*0.3375/(20,000*1 - 0.6*275.4723)= 0.0047 in


tr = P*R/(S*E - 0.6*P)= 275.4723*36/(20,000*1 - 0.6*275.4723)= 0.5 in



Rev. 1 37/70

UW-16(c) Weld Check









Rev. 1 38/70

Manhole (MH)


tw(lower) = 0.3792 inLeg41 = 0.3937 intw(upper) = 0.5 inLeg42 = 0.375 inDp = 28 inte = 0.5 in


Located on: F&D Head #2Liquid static head included: 1.5945 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 14, ln. 5)Nozzle longitudinal joint efficiency: 1Nozzle description: 20" Sch 30 (XS)Pad material specification: SA-516 70 (II-D p. 18, ln. 22)Pad diameter: 28 inFlange description: 20 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -52.8°F(UCS-66(b)(1)(b))Liquid static head on flange: 1.5945 psiASME B16.5 flange rating MAWP: 253.7 psi @ 221°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FNozzle orientation: 0°Calculated as hillside: noLocal vessel minimum thickness: 0.3792 inEnd of nozzle to datum line: -30.315 inNozzle inside diameter, new: 19 inNozzle nominal wall thickness: 0.5 inNozzle corrosion allowance: 0.0625 inProjection available outside vessel, Lpr: 9.5233 inProjection available outside vessel to flange face, Lf: 11.2133 inDistance to head center, R: 0 inPad is split: no


Rev. 1 39/70


Available reinforcement per UG-37 governs the MAWP of this nozzle.

UG-37 Area Calculation Summary (in2)For P = 228.57 psi @ 221 °F

The opening is adequately reinforced

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin

5.3836 5.3861 0.7041 0.4178 -- 4 0.2642 0.3906 0.4375

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

Weld loadW

Weld loadW1-1

Path 1-1strength

Weld loadW2-2

Path 2-2strength

Weld loadW3-3

Path 3-3strength

94,144.39 93,640 322,557.31 15,566.62 483,364.59 98,378.63 308,886.44


Weld description Required weldsize (in)

Actual weldsize (in) Status

Nozzle to pad fillet (Leg41) 0.25 0.2756 weld size is adequate

Pad to shell fillet (Leg42) 0.1583 0.2625 weld size is adequate

Nozzle to pad groove (Upper) 0.3063 0.5 weld size is adequate


Fig UCS-66.2 general note (1) applies.

Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -13 °FFig UCS-66.1 MDMT reduction = 26 °F, (coincident ratio = 0.74016).

Pad impact test exemption temperature from Fig UCS-66 Curve B = -13 °FFig UCS-66.1 MDMT reduction = 26 °F, (coincident ratio = 0.74016).

Nozzle UCS-66 governing thk: 0.4375 inNozzle rated MDMT: -39 °FPad UCS-66 governing thickness: 0.4375 inPad rated MDMT: -39 °F


Parallel to the vessel wall: d = 19.125 inNormal to the vessel wall outside: 2.5*(t - C) = 0.7918 in



Rev. 1 40/70

trn = P*Rn/(Sn*E - 0.6*P)= 228.5676*9.5625/(17,100*1 - 0.6*228.5676)= 0.1289 in

Required thickness tr from UG-37(a)(a)

tr = P*L*M/(2*S*E - 0.2*P)= 228.5676*48.8825*1/(2*20,000*1 - 0.2*228.5676)= 0.2796 in

Area required per UG-37(c)

Allowable stresses: Sn = 17,100, Sv = 20,000, Sp = 20,000 psi

fr1 = lesser of 1 or Sn/Sv = 0.855fr2 = lesser of 1 or Sn/Sv = 0.855fr3 = lesser of fr2 or Sp/Sv = 0.855fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1)= 19.125*0.2796*1 + 2*0.4375*0.2796*1*(1 - 0.855)= 5.3836 in2

Area available from FIG. UG-37.1

A1 = larger of the following= 0.7041 in2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 19.125*(1*0.3167 - 1*0.2796) - 2*0.4375*(1*0.3167 - 1*0.2796)*(1 - 0.855)= 0.7041 in2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 2*(0.3167 + 0.4375)*(1*0.3167 - 1*0.2796) - 2*0.4375*(1*0.3167 - 1*0.2796)*(1 - 0.855)= 0.0512 in2

A2 = smaller of the following= 0.4178 in2

= 5*(tn - trn)*fr2*t= 5*(0.4375 - 0.1289)*0.855*0.3167= 0.4178 in2

= 2*(tn - trn)*(2.5*tn + te)*fr2= 2*(0.4375 - 0.1289)*(2.5*0.4375 + 0.5)*0.855= 0.841 in2

A41 = Leg2*fr3= 0.38032*0.855= 0.1236 in2


Rev. 1 41/70

(Part of the weld is outside of the limits)A42 = Leg2*fr4

= 0.3752*1= 0.1406 in2

A5 = (Dp - d - 2*tn)*te*fr4= (28 - 19.125 - 2*0.4375)*0.5*1= 4 in2

Area = A1 + A2 + A41 + A42 + A5

= 0.7041 + 0.4178 + 0.1236 + 0.1406 + 4= 5.3861 in2

As Area >= A the reinforcement is adequate.

UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0.75 or tn or te = 0.4375 intc(min) = lesser of 0.25 or 0.7*tmin = 0.25 intc(actual) = 0.7*Leg = 0.7*0.3937 = 0.2756 in

Outer fillet: tmin = lesser of 0.75 or te or t = 0.3167 intw(min) = 0.5*tmin = 0.1584 intw(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in


Interpretation VIII-1-83-66 has been applied.





Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0.74*20,000 = 14,800 psiNozzle wall in shear: 0.7*17,100 = 11,970 psiInner fillet weld in shear: 0.49*17,100 = 8,379 psiOuter fillet weld in shear: 0.49*20,000 = 9,800 psi


Rev. 1 42/70

Upper groove weld in tension: 0.74*20,000 = 14,800 psi

Strength of welded joints:

(1) Inner fillet weld in shear(π/2)*Nozzle OD*Leg*Si = (π/2)*20*0.3937*8,379 = 103,635.25 lbf

(2) Outer fillet weld in shear(π/2)*Pad OD*Leg*So = (π/2)*28*0.375*9,800 = 161,634.95 lbf

(3) Nozzle wall in shear(π/2)*Mean nozzle dia*tn*Sn = (π/2)*19.5625*0.4375*11,970 = 160,922.38 lbf

(4) Groove weld in tension(π/2)*Nozzle OD*tw*Sg = (π/2)*20*0.3167*14,800 = 147,251.48 lbf

(6) Upper groove weld in tension(π/2)*Nozzle OD*tw*Sg = (π/2)*20*0.5*14,800 = 232,477.86 lbf

Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv

= (5.3836 - 0.7041 + 2*0.4375*0.855*(1*0.3167 - 1*0.2796))*20,000= 94,144.39 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv

= (0.4178 + 4 + 0.1236 + 0.1406)*20,000= 93,640 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv

= (0.4178 + 0 + 0.1236 + 0 + 2*0.4375*0.3167*0.855)*20,000= 15,566.62 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv

= (0.4178 + 0 + 4 + 0.1236 + 0.1406 + 0 + 2*0.4375*0.3167*0.855)*20,000= 98,378.63 lbf


Rev. 1 43/70

Load for path 1-1 lesser of W or W1-1 = 93640 lbfPath 1-1 through (2) & (3) = 161,635 + 160,922.4 = 322,557.31 lbfPath 1-1 is stronger than W1-1 so it is acceptable per UG-41(b)(1).

Load for path 2-2 lesser of W or W2-2 = 15566.62 lbfPath 2-2 through (1), (4), (6) = 103,635.3 + 147,251.5 + 232,477.9 = 483,364.59 lbfPath 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 = 94144.39 lbfPath 3-3 through (2), (4) = 161,635 + 147,251.5 = 308,886.44 lbfPath 3-3 is stronger than W so it is acceptable per UG-41(b)(2).


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

UG-37 Area Calculation Summary (in2)For P = 258.33 psi @ 70 °F

The opening is adequately reinforced

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin

6.0441 6.0462 1.1973 0.5758 -- 4 0.2731 0.3281 0.4375

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

Weld loadW

Weld loadW1-1

Path 1-1strength

Weld loadW2-2

Path 2-2strength

Weld loadW3-3

Path 3-3strength

98,021.38 96,978 344,958.69 20,650.32 512,424.31 103,462.32 337,946.19


Weld description Required weldsize (in)

Actual weldsize (in) Status

Nozzle to pad fillet (Leg41) 0.25 0.2756 weld size is adequate

Pad to shell fillet (Leg42) 0.1896 0.2625 weld size is adequate

Nozzle to pad groove (Upper) 0.35 0.5 weld size is adequate



Parallel to the vessel wall: d = 19 inNormal to the vessel wall outside: 2.5*(t - C) = 0.948 in



Rev. 1 44/70

trn = P*Rn/(Sn*E - 0.6*P)= 258.3329*9.5/(17,100*1 - 0.6*258.3329)= 0.1448 in


tr = P*L*M/(2*S*E - 0.2*P)= 258.3329*48.82*1/(2*20,000*1 - 0.2*258.3329)= 0.3157 in

Area required per UG-37(c)

Allowable stresses: Sn = 17,100, Sv = 20,000, Sp = 20,000 psi

fr1 = lesser of 1 or Sn/Sv = 0.855fr2 = lesser of 1 or Sn/Sv = 0.855fr3 = lesser of fr2 or Sp/Sv = 0.855fr4 = lesser of 1 or Sp/Sv = 1

A = d*tr*F + 2*tn*tr*F*(1 - fr1)= 19*0.3157*1 + 2*0.5*0.3157*1*(1 - 0.855)= 6.0441 in2

Area available from FIG. UG-37.1

A1 = larger of the following= 1.1973 in2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 19*(1*0.3792 - 1*0.3157) - 2*0.5*(1*0.3792 - 1*0.3157)*(1 - 0.855)= 1.1973 in2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 2*(0.3792 + 0.5)*(1*0.3792 - 1*0.3157) - 2*0.5*(1*0.3792 - 1*0.3157)*(1 - 0.855)= 0.1025 in2

A2 = smaller of the following= 0.5758 in2

= 5*(tn - trn)*fr2*t= 5*(0.5 - 0.1448)*0.855*0.3792= 0.5758 in2

= 2*(tn - trn)*(2.5*tn + te)*fr2= 2*(0.5 - 0.1448)*(2.5*0.5 + 0.5)*0.855= 1.0629 in2

A41 = Leg2*fr3= 0.39372*0.855= 0.1325 in2


Rev. 1 45/70

A42 = Leg2*fr4= 0.3752*1= 0.1406 in2

A5 = (Dp - d - 2*tn)*te*fr4= (28 - 19 - 2*0.5)*0.5*1= 4 in2

Area = A1 + A2 + A41 + A42 + A5

= 1.1973 + 0.5758 + 0.1325 + 0.1406 + 4= 6.0462 in2

As Area >= A the reinforcement is adequate.

UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0.75 or tn or te = 0.5 intc(min) = lesser of 0.25 or 0.7*tmin = 0.25 intc(actual) = 0.7*Leg = 0.7*0.3937 = 0.2756 in

Outer fillet: tmin = lesser of 0.75 or te or t = 0.3792 intw(min) = 0.5*tmin = 0.1896 intw(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in







Allowable stresses in joints UG-45(c) and UW-15(c)

Groove weld in tension: 0.74*20,000 = 14,800 psiNozzle wall in shear: 0.7*17,100 = 11,970 psiInner fillet weld in shear: 0.49*17,100 = 8,379 psiOuter fillet weld in shear: 0.49*20,000 = 9,800 psiUpper groove weld in tension: 0.74*20,000 = 14,800 psi


Rev. 1 46/70

Strength of welded joints:

(1) Inner fillet weld in shear(π/2)*Nozzle OD*Leg*Si = (π/2)*20*0.3937*8,379 = 103,635.25 lbf

(2) Outer fillet weld in shear(π/2)*Pad OD*Leg*So = (π/2)*28*0.375*9,800 = 161,634.95 lbf

(3) Nozzle wall in shear(π/2)*Mean nozzle dia*tn*Sn = (π/2)*19.5*0.5*11,970 = 183,323.72 lbf

(4) Groove weld in tension(π/2)*Nozzle OD*tw*Sg = (π/2)*20*0.3792*14,800 = 176,311.22 lbf

(6) Upper groove weld in tension(π/2)*Nozzle OD*tw*Sg = (π/2)*20*0.5*14,800 = 232,477.86 lbf

Loading on welds per UG-41(b)(1)

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv

= (6.0441 - 1.1973 + 2*0.5*0.855*(1*0.3792 - 1*0.3157))*20,000= 98,021.38 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv

= (0.5758 + 4 + 0.1325 + 0.1406)*20,000= 96,978 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv

= (0.5758 + 0 + 0.1325 + 0 + 2*0.5*0.3792*0.855)*20,000= 20,650.32 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv

= (0.5758 + 0 + 4 + 0.1325 + 0.1406 + 0 + 2*0.5*0.3792*0.855)*20,000= 103,462.3 lbf

Load for path 1-1 lesser of W or W1-1 = 96978 lbfPath 1-1 through (2) & (3) = 161,635 + 183,323.7 = 344,958.69 lbfPath 1-1 is stronger than W1-1 so it is acceptable per UG-41(b)(1).

Load for path 2-2 lesser of W or W2-2 = 20650.32 lbfPath 2-2 through (1), (4), (6) = 103,635.3 + 176,311.2 + 232,477.9 = 512,424.31 lbfPath 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 = 98021.38 lbfPath 3-3 through (2), (4) = 161,635 + 176,311.2 = 337,946.19 lbfPath 3-3 is stronger than W so it is acceptable per UG-41(b)(2).


Rev. 1 47/70

Level Gauge, Level Gauge (LI, L2)


tw(lower) = 0.3923 inLeg41 = 0.3543 in


Located on: F&D Head #1Liquid static head included: 2.5894 psiNozzle material specification: SA-105 (II-D p. 18, ln. 8)Nozzle longitudinal joint efficiency: 1Nozzle description: 0.750" Class 6000 - threadedNozzle orientation: 180°Calculated as hillside: yesLocal vessel minimum thickness: 0.3923 inEnd of nozzle to datum line: 299.8837 inNozzle inside diameter, new: 1.05 inNozzle nominal wall thickness: 0.35 inNozzle corrosion allowance: 0.0625 inOpening chord length: 1.382 inProjection available outside vessel, Lpr: 2 inDistance to head center, R: 27.56 in


Rev. 1 48/70




For P = 252.24 psi @ 221 °F

UG-45Nozzle WallThicknessSummary

(in)The nozzle

passes UG-45

Arequired


Awelds treq tmin












Parallel to the vessel wall: d = 1.382 inNormal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.7188 in


trn = P*Rn/(Sn*E - 0.6*P)= 252.2404*0.5875/(20,000*1 - 0.6*252.2404)= 0.0075 in


tr = P*L*M/(2*S*E - 0.2*P)= 252.2404*52.2325*1/(2*20,000*1 - 0.2*252.2404)


Rev. 1 49/70

= 0.3298 in


UW-16(c) Weld Check








Rev. 1 50/70






For P = 300.32 psi @ 70 °F

UG-45Nozzle WallThicknessSummary

(in)The nozzle

passes UG-45

Arequired


Awelds treq tmin












trn = P*Rn/(Sn*E - 0.6*P)= 300.3206*0.525/(20,000*1 - 0.6*300.3206)= 0.008 in


tr = P*L*M/(2*S*E - 0.2*P)= 300.3206*52.17*1/(2*20,000*1 - 0.2*300.3206)= 0.3923 in


Rev. 1 51/70


UW-16(c) Weld Check










Rev. 1 52/70

Saddle

Saddle material: SA516 Gr70 /SA36

Saddle construction is: Centered webSaddle allowable stress: Ss = 20,000 psiSaddle yield stress: Sy = 38,000 psiSaddle distance to datum: 30 inTangent to tangent length: L = 285.5899 inSaddle separation: Ls = 210.9403 inVessel radius: R = 36.5 inTangent distance left: Al = 44.6496 inTangent distance right: Ar = 30 inSaddle height: Hs = 57.87 inSaddle contact angle: θ = 120 °Wind pressure: 20.82 psfWeb plate thickness: ts = 0.4724 inBase plate length: E = 67.1653 inBase plate width: F = 9.8425 inBase plate thickness: tb = 0.6299 inNumber of stiffener ribs: n = 4Largest stiffener rib spacing: di = 21.5968 inStiffener rib thickness: tw = 0.4724 inSaddle width: B = 7.874 in

Anchor bolt size & type: 1 inch series 8threaded

Anchor bolt material: SA36Anchor bolt allowable shear: 15,000 psiAnchor bolt corrosion allowance: 0 inAnchor bolts per saddle: 2Base coefficient of friction: µ = 0.45

Weight on left saddle: operating corr =29,259 lb, test new =29,845 lbWeight on right saddle: operating corr =26,242 lb, test new =26,814 lbWeight of saddle pair =944 lb

Notes:(1) Saddle calculations are based on the method presented in "Stresses in Large Cylindrical Pressure Vessels onTwo Saddle Supports" by L.P. Zick.

Seismic base shear on vessel

Vessel is assumed to be a rigid structure.Method of seismic analysis: ASCE 7-05 ground supportedVertical seismic accelerations considered: YesForce Multiplier: 0.3333Minimum Weight Multiplier: 0.2Importance factor: I = 1Site Class: DShort period spectral response acceleration: Ss = 150percent of gFrom Table 11.4-1: Fa = 1


Rev. 1 53/70

SMS = Fa*Ss = 1*1.5 = 1.5SDS = (2/3)*SMS = 1

Fp = 0.3*SDS*I*W*0.7= 0.3*1*1*55,501*0.7= 11,655.21 lbf

Saddle reactions due to weight + seismic

Vv = vertical seismic force acting on right saddleV = horizontal seismic shear acting on right saddle (worst case if not slotted)

Seismic longitudinal reaction, Ql (right saddle):

Ql = V * Hs / Ls + Vv= 11,655.21 * 57.87 / 210.9403 + 5,248.4= 8,445.93 lbf

Seismic transverse reaction, Qt (right saddle):

Qt = V*Hs/(Ro*Sin( θ /2 )) + Vv= 5,510.82*57.87/(36.5*Sin( 120 /2 )) + 5,248.4= 15,337.36 lbf

Q = Weight on saddle + larger of Qt or QlQ = W + Qt = 26,242 + 15,337.36 = 41,579.36 lbf

Vv = vertical seismic force acting on left saddleV = horizontal seismic shear acting on left saddle (worst case if not slotted)

Seismic longitudinal reaction, Ql (left saddle):

Ql = V * Hs / Ls + Vv= 11,655.21 * 57.87 / 210.9403 + 5,851.8= 9,049.33 lbf

Seismic transverse reaction, Qt (left saddle):

Qt = V*Hs/(Ro*Sin( θ /2 )) + Vv= 6,144.39*57.87/(36.5*Sin( 120 /2 )) + 5,851.8= 17,100.67 lbf


Transverse wind shear on vessel

Vwt = Pw*G*(Cf(shell)*(Projected shell area) + Cf(saddle)*(Projected saddle area))= 20.82*0.85*(0.85*205.2031 + 2*2.337)= 3,169.13 lbf

End wind shear on vessel

Vwe = Pw*G*(Cf(shell)*π*Ro2 / 144 + Cf(saddle)*(Projected saddle area))

= 20.82*0.85*(0.5*π*44.92 / 144 + 2*12.55)


Rev. 1 54/70

= 833.23 lbf

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= 833.23 * 57.87 / 210.9403= 228.59 lbf

Wind transverse reaction, Qt (right saddle):

Qt = V*Hs/(Ro*Sin( θ /2 ))= 1,516.7*57.87/(36.5*Sin( 120 /2 ))= 2,776.7 lbf


V = horizontal wind shear acting on left saddle (worst case if not slotted)

Wind longitudinal reaction, Ql (left saddle):

Ql = V * Hs / Ls= 833.23 * 57.87 / 210.9403= 228.59 lbf

Wind transverse reaction, Qt (left saddle):

Qt = V*Hs/(Ro*Sin( θ /2 ))= 1,652.43*57.87/(36.5*Sin( 120 /2 ))= 3,025.19 lbf


Load Vesselcondition

Bending + pressurebetween saddles

(psi)

Bending + pressure atthe saddle

(psi)

S1(+)

allow(+)

S1(-)

allow(-)

S2(+)

allow(+)

S2(-)

allow(-)

Seismic Operating 8,796 17,000 845 13,810 9,437 20,000 1,485 13,810

Wind Operating 8,541 17,000 589 13,810 9,189 20,000 1,238 13,810

Wind Test 9,490 29,070 494 13,810 10,104 34,200 1,107 13,810

Load Vesselcondition

Tangentialshear (psi)

Circumferentialstress (psi)

Stress oversaddle (psi)

Splitting(psi)

S3 allow S5 allow S6 allow


Rev. 1 55/70

S4(horns)

allow(+/-)

Seismic Operating 2,511 16,000 -21,410 30,000 12,013 17,250 1,641 13,333

Wind Operating 1,624 16,000 -14,910 30,000 8,366 17,250 1,143 13,333

Wind Test 1,316 27,360 -11,002 34,200 6,572 34,200 1,092 34,200

Load Case 1: Seismic ,Operating

Longitudinal stress between saddles (Seismic ,Operating, right saddle loading and geometry govern)

S1 = +- 3*K1*Q*(L/12) / (π*R2*t)= 3*0.5147*41,579.36*(285.5899/12) / (π*36.28132*0.4375)= 845 psi

Sp = P*R/(2*t)= 192.94*36.0625/(2*0.4375)= 7,952 psi

Maximum tensile stress S1t = S1 + Sp = 8,796 psiMaximum compressive stress (shut down) S1c = S1 = 845 psi

Tensile stress is acceptable (<=1*S*E = 17,000 psi)Compressive stress is acceptable (<=1*Sc = 13,810 psi)

Longitudinal stress at the left saddle (Seismic ,Operating)

Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3= 2*19.5714/3 + 285.5899 + 2*20.1287/3= 312.0566 in

Seismic vertical acceleration coefficient m = 0.9524*0.21 = 0.2

w = Wt*(1 + m)/Le = 55,501*(1 + 0.2)/312.0566 = 213.43 lb/in

Bending moment at the left saddle:

Mq = w*(2*H*Al/3 + Al2/2 - (R2 - H2)/4)

= 213.43*(2*19.5714*44.6496/3 + 44.64962/2 - (36.52 - 19.57142)/4)= 286,431.5 lb-in

S2 = +- Mq*K1'/ (π*R2*t)= 286,431.5*9.3799/ (π*36.28132*0.4375)= 1,485 psi

Sp = P*R/(2*t)= 192.94*36.0625/(2*0.4375)= 7,952 psi

Maximum tensile stress S2t = S2 + Sp = 9,437 psiMaximum compressive stress (shut down) S2c = S2 = 1,485 psi

Tensile stress is acceptable (<=1*S = 20,000 psi)Compressive stress is acceptable (<=1*Sc = 13,810 psi)

Tangential shear stress in the shell (left saddle, Seismic ,Operating)


Rev. 1 56/70

Qshear = Q - w*(a + 2*H/3)= 46,359.66 - 213.43*(44.6496 + 2*19.5714/3)= 34,045.54 lbf

S3 = K2.2*Qshear/(R*t)= 1.1707*34,045.54/(36.2813*0.4375)= 2,511 psi

Tangential shear stress is acceptable (<= 0.8*S = 16,000 psi)

Circumferential stress at the left saddle horns (Seismic ,Operating)

S4 = -Q/(4*t*(b+1.56*Sqr(Ro*t))) - 12*K3*Q*R/(L*t2)= -46,359.66/(4*0.4375*(7.874+1.56*Sqr(36.5*0.4375))) - 12*0.0529*46,359.66*36.2813/(285.5899*0.43752)= -21,410 psi

Circumferential stress at saddle horns is acceptable (<=1.5*Sa = 30,000 psi)

Ring compression in shell over left saddle (Seismic ,Operating)

S5 = K5*Q/((t)*(ts + 1.56*Sqr(Ro*tc)))= 0.7603*46,359.66/((0.4375)*(0.4724 + 1.56*Sqr(36.5*0.4375)))= 12,013 psi

Ring compression in shell is acceptable (<= 0.5*Sy = 17,250 psi)

Saddle splitting load (left, Seismic ,Operating)

Area resisting splitting force = Web area + wear plate area

Ae = Heff*ts + tp*Wp= 12.1667*0.4724 + 0*0= 5.7475 in2

S6 = K8*Q / Ae= 0.2035*46,359.66 / 5.7475= 1,641 psi

Stress in saddle is acceptable (<= (2/3)*Ss = 13,333 psi)

Load Case 2: Wind ,Operating

Longitudinal stress between saddles (Wind ,Operating, right saddle loading and geometry govern)

S1 = +- 3*K1*Q*(L/12) / (π*R2*t)= 3*0.5147*29,018.7*(285.5899/12) / (π*36.28132*0.4375)= 589 psi

Sp = P*R/(2*t)= 192.94*36.0625/(2*0.4375)= 7,952 psi


Tensile stress is acceptable (<=1*S*E = 17,000 psi)


Rev. 1 57/70

Compressive stress is acceptable (<=1*Sc = 13,810 psi)

Longitudinal stress at the left saddle (Wind ,Operating)


w = Wt/Le = 55,501/312.0566 = 177.86 lb/in


Mq = w*(2*H*Al/3 + Al2/2 - (R2 - H2)/4)

= 177.86*(2*19.5714*44.6496/3 + 44.64962/2 - (36.52 - 19.57142)/4)= 238,692.9 lb-in

S2 = +- Mq*K1'/ (π*R2*t)= 238,692.9*9.3799/ (π*36.28132*0.4375)= 1,238 psi

Sp = P*R/(2*t)= 192.94*36.0625/(2*0.4375)= 7,952 psi

Maximum tensile stress S2t = S2 + Sp = 9,189 psiMaximum compressive stress (shut down) S2c = S2 = 1,238 psi

Tensile stress is acceptable (<=1*S = 20,000 psi)Compressive stress is acceptable (<=1*Sc = 13,810 psi)

Tangential shear stress in the shell (left saddle, Wind ,Operating)

Qshear = Q - w*(a + 2*H/3)= 32,284.19 - 177.86*(44.6496 + 2*19.5714/3)= 22,022.43 lbf

S3 = K2.2*Qshear/(R*t)= 1.1707*22,022.43/(36.2813*0.4375)= 1,624 psi

Tangential shear stress is acceptable (<= 0.8*S = 16,000 psi)

Circumferential stress at the left saddle horns (Wind ,Operating)


Circumferential stress at saddle horns is acceptable (<=1.5*Sa = 30,000 psi)

Ring compression in shell over left saddle (Wind ,Operating)




Rev. 1 58/70

Saddle splitting load (left, Wind ,Operating)


Ae = Heff*ts + tp*Wp= 12.1667*0.4724 + 0*0= 5.7475 in2

S6 = K8*Q / Ae= 0.2035*32,284.19 / 5.7475= 1,143 psi

Stress in saddle is acceptable (<= (2/3)*Ss = 13,333 psi)

Load Case 3: Wind ,Test

Longitudinal stress between saddles (Wind ,Test, right saddle loading and geometry govern)

S1 = +- 3*K1*Q*(L/12) / (π*R2*t)= 3*0.5147*27,730.31*(285.5899/12) / (π*36.252*0.5)= 494 psi

Sp = P*R/(2*t)= 249.89*36/(2*0.5)= 8,996 psi


Tensile stress is acceptable (<= 0.9*Sy = 29,070 psi)Compressive stress is acceptable (<=1*Sc = 13,810 psi)

Longitudinal stress at the left saddle (Wind ,Test)


w = Wt/Le = 56,659/312.0566 = 181.57 lb/in


Mq = w*(2*H*Al/3 + Al2/2 - (R2 - H2)/4)

= 181.57*(2*19.5714*44.6496/3 + 44.64962/2 - (36.52 - 19.57142)/4)= 243,673.1 lb-in

S2 = +- Mq*K1'/ (π*R2*t)= 243,673.1*9.3799/ (π*36.252*0.5)= 1,107 psi

Sp = P*R/(2*t)= 249.89*36/(2*0.5)= 8,996 psi

Maximum tensile stress S2t = S2 + Sp = 10,104 psi


Rev. 1 59/70

Maximum compressive stress (shut down) S2c = S2 = 1,107 psi

Tensile stress is acceptable (<= 0.9*Sy = 34,200 psi)Compressive stress is acceptable (<=1*Sc = 13,810 psi)

Tangential shear stress in the shell (left saddle, Wind ,Test)

Qshear = Q - w*(a + 2*H/3)= 30,843.31 - 181.57*(44.6496 + 2*19.5714/3)= 20,367.44 lbf

S3 = K2.2*Qshear/(R*t)= 1.1707*20,367.44/(36.25*0.5)= 1,316 psi

Tangential shear stress is acceptable (<= 0.8*(0.9*Sy) = 27,360 psi)

Circumferential stress at the left saddle horns (Wind ,Test)


Circumferential stress at saddle horns is acceptable (<= 0.9*Sy = 34,200 psi)

Ring compression in shell over left saddle (Wind ,Test)



Saddle splitting load (left, Wind ,Test)


Ae = Heff*ts + tp*Wp= 12.1667*0.4724 + 0*0= 5.7475 in2

S6 = K8*Q / Ae= 0.2035*30,843.31 / 5.7475= 1,092 psi

Stress in saddle is acceptable (<= 0.9*Sy = 34,200 psi)

Shear stress in anchor bolting, one end slotted

Maximum seismic or wind base shear = 11,655.21 lbf

Thermal expansion base shear = W*µ = 29,731 * 0.45= 13,378.95 lbf

Corroded root area for a 1 inch series 8 threaded bolt = 0.551 in2 ( 2 per saddle )

Bolt shear stress = 13,378.95/(0.551*2) = 12,141 psi


Rev. 1 60/70

Anchor bolt stress is acceptable (<= 15,000 psi)

Web plate buckling check (Escoe pg 251)

Allowable compressive stress Sc is the lesser of 20,000 or 16,052 psi: (16,052)

Sc = Ki*π2*E/(12*(1 - 0.32)*(di/tw)2)= 1.28*π2*29E+06/(12*(1 - 0.32)*(21.5968/0.4724)2)= 16,052 psi

Allowable compressive load on the saddle

be = di*ts/(di*ts + 2*tw*(b - 1))= 21.5968*0.4724/(21.5968*0.4724 + 2*0.4724*(7.874 - 1))= 0.611

Fb = n*(As + 2*be*tw)*Sc= 4*(3.4965 + 2*0.611*0.4724)*16,052= 261,570.72 lbf

Saddle loading of 46,831.66 lbf is <= Fb; satisfactory.

Primary bending + axial stress in the saddle due to end loads (assumes one saddle slotted)σb = V * (Hs - xo)* y / I + Q / A= 11,655.21 * (57.87 - 30.1853)* 3.937 / 77.04 + 46,359.66 / 43.8511= 17,547 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 onesaddle slotted)σb = V * (Hs - xo)* y / I + Q / A= 25,034.16 * (57.87 - 30.1853)* 3.937 / 77.04 + 46,359.66 / 43.8511= 36,475 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 = 21.5968, b = 4.6851 in

tb = (β1*q*b2/(1.5*Sa))0.5

= (3*71*4.68512/(1.5*20,000))0.5

= 0.3943 in

The base plate thickness of 0.6299 in is adequate.

Foundation bearing check

Sf = Qmax / (F*E)= 46,831.66 / (9.8425*67.1653)= 71 psi

Concrete bearing stress < 1,658 psi ; satisfactory.


Rev. 1 61/70

Lifting Lug

Geometry Inputs

Attached To Cylinder #3

Material A36

Orientation Longitudinal

Distance of Lift Point From Datum 9.0000"

Angular Position 0.00°

Length of Lug, L 7.8740"

Height of Lug, H 5.9055"

Thickness of Lug, t 0.6299"

Hole Diameter, d 2.0000"

Load Eccentricity, a1 1.3780"

Distance from Load to Shell or Pad, a2 3.3465"

Weld Size, tw 0.3540"

Width of Pad, Bp 3.9370"

Length of Pad, Lp 8.6614"

Pad Thickness, tp 0.5000"

Pad Weld Size, twp 0.3937"

Load Angle Normal to Vessel, β 45.0000 °

Load Angle from Vertical, φ 45.0000 °

Intermediate Values

Load Factor 1.5000

Vessel Weight (new, incl. Load Factor), W 17994 lb

Lug Weight (new), Wlug 13 lb

Distance from Center of Gravity to this lug, x1 125.8080"


Rev. 1 62/70

Distance from Center of Gravity to second lug, x2 127.1323"

Allowable Stress, Tensile, σt 19980 psi

Allowable Stress, Shear, σs 13320 psi

Allowable Stress, Bearing, σp 29970 psi

Allowable Stress, Bending, σb 22201 psi

Allowable Stress, Weld Shear, τallowable 13320 psi

Allowable Stress set to 1/3 Sy per ASME B30.20 No

Summary Values

Required Lift Pin Diameter, dreqd 0.7819"

Required Lug Thickness, treqd 0.2134"

Lug Stress Ratio, σratio 0.21

Weld Shear Stress Ratio, τratio 0.40

Lug Design Acceptable

Local Stresses Acceptable

Lift Forces

Fr = force on vessel at lugFr = [W / cos(φ1)] * (1 - x1 / (x1 + x2))

= (17994.066) / cos(45.0000) * (1 - 125.808/ (125.808 +127.132))

= 12790 lbfwhere 'x1' is the distance between this lug and the center of gravity

'x2' is the distance between the second lift lug and the center ofgravity

Lug Pin Diameter - Shear stress

dreqd = (2 * Fr / (π * σs))0.5

= (2 * 12790.3 / (π * 13320.0))0.5 = 0.7819"

dreqd / d = 0.7819 / 2.0000 = 0.39 Acceptable

σ = Fr / A= Fr / (2*(0.25*π*d2))= 12790.3 / (2 * (0.25 * π * 2.00002)) = 2035.6464 psi

σ / σs = 2035.65 / 13320.00 = 0.15 Acceptable


Rev. 1 63/70

Lug Thickness - Tensile stress

treqd = Fr / ((L - d) * σt)= 12790.3 / ((7.8740 - 2.0000)*19980.0) = 0.1090"

treqd / t = 0.1090 / 0.6299 = 0.17 Acceptable

σ = Fr / A= Fr / ((L - d) * t)= 12790.3 / ((7.8740 - 2.0000)*0.6299) = 3456.8193 psi

σ / σt = 3456.82 / 19980.00 = 0.17 Acceptable

Lug Thickness - Bearing stress

treqd = Fv / (d * σp)= 12790.3 / (2.0000 * 29970.0) = 0.2134"


σ = Fv / Abearing

= Fv / (d * (t))= 12790.3 / (2.0000 *(0.6299)) = 10152.6787 psi

σ / σp = 10152.68 / 29970.00 = 0.34 Acceptable

Lug Thickness - Shear stress

treqd = [Fv / σs] / (2*Lshear)= (12790.3 / 13320.0) / (2*2.5590) = 0.1876"


τ = Fv / Ashear

= Fv / (2 * Lshear * t)= 12790.3 / (2*2.5590*0.6299) = 3967.4397 psi

τ / σs = 3967.44 / 13320.00 = 0.30 Acceptable

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 * L2 * σb)] ≤ 1.0=


Rev. 1 64/70

12790*cos(45.0) / (0.6299*7.8740*19980.0) + 6*abs(12790*sin(45.0)*3.3465 - 12790*cos(45.0)*1.3780)/ (0.6299*7.87402*22201.1)

= 0.21 Acceptable

Weld Stress

Weld stress, tensile, bending and shear during lift:

Direct shear:

Shear stress at lift angle 45.00°; lift force = 12790.3438 lbf

Aweld = 2*(0.707)*tw*(L + t)= 2*(0.707)*0.3540*(7.8740 + 0.6299) = 4.2567 in²

τt = Fr * cos(α) / Aweld

= 12790 * cos(45.0) / 4.2567 = 2124.6941 psi

τs = Fr * sin(α) / Aweld

= 12790 * sin(45.0) / 4.2567 = 2124.6941 psi

τb = M * c / I= 3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * h * L * (3*t + L))= 3 * abs(12790 * sin(45.0) * 3.3465 - 12790 * cos(45.0) * (1.3780)) / (19.2412)= 2775.8203 psi

τ ratio = sqr( (τt + τb)2 + τs2 ) / τallowable ≤ 1.0

= sqr ( (2124.6941 + 2775.8203)2 + (2124.6941)2 ) / 13320.00= 0.40 Acceptable

Pad Weld Stress, tensile, bending and shear during lift:

Direct shear:

Shear stress at lift angle 45.00°; lift force = 12790.3438 lbf

Aweld = 2*(0.707)*twp*(Lp + Bp)= 2*(0.707)*0.3937*(8.6614 + 3.9370) = 7.0134 in²

τt = Fr * cos(α) / Aweld

= 12790 * cos(45.0) / 7.0134 = 1289.5460 psi

τs = Fr * sin(α) / Aweld

= 12790 * sin(45.0) / 7.0134 = 1289.5460 psi

τb = M * c / I= 3 * (Fr * sin(α) * Hght - Fr * cos(α) * a1) / (0.707 * hp * Lp * (3*Wp + Lp))= 3 * abs(12790 * sin(45.0) * 3.8465 - 12790 * cos(45.0) * (1.3780)) / (49.3562)= 1357.0001 psi


Rev. 1 65/70

τ ratio = sqr( (τt + τb)2 + τs2 ) / τallowable ≤ 1.0

= sqr ( (1289.5460 + 1357.0001)2 + (1289.5460)2 ) / 13320.00= 0.22 Acceptable

WRC 107 Analysis

Geometry

Height(radial): 5.9055" Pad Thickness: 0.5000"

Width (circumferential): 0.6299" Pad Width: 3.9370"

Length 7.8740" Pad Length: 8.6614"

Fillet Weld Size: 0.3540" Pad Weld Size: 0.3937"

Location Angle: 0.00°

Applied Loads

Radial load: Pr = -9,044.14 lbfCircumferential moment: Mc = 0 lbf-inCircumferential shear: Vc = 0 lbfLongitudinal moment: ML = 47,251.11lbf-inLongitudinal shear: VL = 9,044.14 lbfTorsion moment: Mt = 0 lbf-inInternal pressure: P = 0 psiMean shell radius: Rm = 36.25 inShell yield stress: Sy = 38,000 psi


Rev. 1 66/70

Maximum stresses due to the applied loads at the lug edge (includes pressure)

Rm/t =36.25

C1 = 0.669, C2 = 2.6758 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+P

b+Q) = 27,166 psi

Allowable combined stress (PL+P

b+Q) = +-3*S = +-60,000 psi

The maximum combined stress (PL+P

b+Q) is within allowable limits.

Maximum local primary membrane stress (PL) = 2,623 psi

Allowable local primary membrane (PL) = +-1.5*S = +-30,000 psi

The maximum local primary membrane stress (PL) is within allowable limits.

Stresses at the lug edge per WRC Bulletin 107

Figure value β Au Al Bu Bl Cu Cl Du Dl

3C* 6.6666 0.0546 0 0 0 0 1,663 1,663 1,663 1,663

4C* 6.9996 0.0443 1,746 1,746 1,746 1,746 0 0 0 0

1C 0.247 0.0325 0 0 0 0 13,403 -13,403 13,403 -13,403

2C-1 0.1955 0.0325 10,609 -10,609 10,609 -10,609 0 0 0 0

3A* 0.2338 0.0293 0 0 0 0 0 0 0 0

1A 0.1066 0.0371 0 0 0 0 0 0 0 0

3B* 1.7788 0.0465 -877 -877 877 877 0 0 0 0

1B-1 0.0609 0.0407 -11,696 11,696 11,696 -11,696 0 0 0 0

Pressure stress* 0 0 0 0 0 0 0 0

Total circumferential stress -218 1,956 24,928 -19,682 15,066 -11,740 15,066 -11,740

Primary membranecircumferential stress* 869 869 2,623 2,623 1,663 1,663 1,663 1,663

3C* 6.893 0.0443 1,720 1,720 1,720 1,720 0 0 0 0

4C* 6.8894 0.0546 0 0 0 0 1,719 1,719 1,719 1,719

1C-1 0.2117 0.0461 11,488 -11,488 11,488 -11,488 0 0 0 0

2C 0.1653 0.0461 0 0 0 0 8,970 -8,970 8,970 -8,970

4A* 0.2984 0.0293 0 0 0 0 0 0 0 0

2A 0.0622 0.05 0 0 0 0 0 0 0 0

4B* 0.4486 0.0465 -402 -402 402 402 0 0 0 0

2B-1 0.0975 0.0563 -13,556 13,556 13,556 -13,556 0 0 0 0


Total longitudinal stress -750 3,386 27,166 -22,922 10,689 -7,251 10,689 -7,251

Primary membranelongitudinal stress* 1,318 1,318 2,122 2,122 1,719 1,719 1,719 1,719

Shear from Mt 0 0 0 0 0 0 0 0


Rev. 1 67/70

Circ shear from Vc 0 0 0 0 0 0 0 0

Long shear from VL 0 0 0 0 -845 -845 845 845

Total Shear stress 0 0 0 0 -845 -845 845 845

Combined stress (PL+Pb+Q) -750 3,386 27,166 -22,922 15,223 -11,894 15,223 -11,894


Rev. 1 68/70

Note: * denotes primary stress.

Maximum stresses due to the applied loads at the pad edge (includes pressure)

Rm/t =72.5

C1 = 2.3622, C2 = 4.7244 in

Local circumferential pressure stress = P*Ri/t =0 psi

Local longitudinal pressure stress = P*Ri/2t =0 psi

Maximum combined stress (PL+P

b+Q) = 42,394 psi

Allowable combined stress (PL+P

b+Q) = +-3*S = +-60,000 psi

The maximum combined stress (PL+P

b+Q) is within allowable limits.

Maximum local primary membrane stress (PL) = 10,523 psi

Allowable local primary membrane (PL) = +-1.5*S = +-30,000 psi

The maximum local primary membrane stress (PL) is within allowable limits.

Stresses at the pad edge per WRC Bulletin 107

Figure value β Au Al Bu Bl Cu Cl Du Dl

3C* 8.2706 0.1216 0 0 0 0 4,127 4,127 4,127 4,127

4C* 11.6876 0.1044 5,832 5,832 5,832 5,832 0 0 0 0

1C 0.1166 0.0848 0 0 0 0 25,309 -25,309 25,309 -25,309

2C-1 0.0818 0.0848 17,755 -17,755 17,755 -17,755 0 0 0 0

3A* 2.338 0.0821 0 0 0 0 0 0 0 0

1A 0.0927 0.0872 0 0 0 0 0 0 0 0

3B* 8.1635 0.1034 -4,691 -4,691 4,691 4,691 0 0 0 0

1B-1 0.0405 0.0938 -13,511 13,511 13,511 -13,511 0 0 0 0


Total circumferential stress 5,385 -3,103 41,789 -20,743 29,436 -21,182 29,436 -21,182

Primary membranecircumferential stress* 1,141 1,141 10,523 10,523 4,127 4,127 4,127 4,127

3C* 9.2675 0.1044 4,624 4,624 4,624 4,624 0 0 0 0

4C* 11.1674 0.1216 0 0 0 0 5,572 5,572 5,572 5,572

1C-1 0.0968 0.1075 21,011 -21,011 21,011 -21,011 0 0 0 0

2C 0.063 0.1075 0 0 0 0 13,675 -13,675 13,675 -13,675

4A* 3.4993 0.0821 0 0 0 0 0 0 0 0

2A 0.0463 0.1057 0 0 0 0 0 0 0 0

4B* 2.6533 0.1034 -2,202 -2,202 2,202 2,202 0 0 0 0

2B-1 0.0523 0.1124 -14,557 14,557 14,557 -14,557 0 0 0 0


Total longitudinal stress 8,876 -4,032 42,394 -28,742 19,247 -8,103 19,247 -8,103

Primary membranelongitudinal stress* 2,422 2,422 6,826 6,826 5,572 5,572 5,572 5,572

Shear from Mt 0 0 0 0 0 0 0 0


Rev. 1 69/70

Circ shear from Vc 0 0 0 0 0 0 0 0

Long shear from VL 0 0 0 0 -957 -957 957 957

Total Shear stress 0 0 0 0 -957 -957 957 957

Combined stress (PL+Pb+Q) 8,876 -4,032 42,394 -28,742 29,525 -21,252 29,525 -21,252

Note: * denotes primary stress.


Rev. 1 70/70

28714-07-01 Rev 1 Calculo FIMA

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