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Codeware, Inc.

Houston, TX, USA

www.codeware.com

COMPRESS Pressure Vessel Design Calculations

Item: Split Stream Dearator

Vessel No: V-1234Customer: Magaladon Oil Venture

Contract: C-45490-R56

Designer: John Doe

Date: April 1, 2001

You can edit this page by selecting Cover Page settings... in the reportmenu.

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Deficiencies Summary

Deficiencies for Dished Cover #1The Rated MDMT of -40.00C is warmer than the Design MDMT of -46.00C.

Deficiencies for End ClosureThe flange rated MDMT (-40 C) is less than the target MDMT (-46 C)

Deficiencies for Temporary Cover

Entry for head diameter D does not agree with the adjacent cylinder diameterThe Rated MDMT of 17.00C is warmer than the Design MDMT of -46.00C.

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Pressure Summary

Pressure Summary for Chamber bounded by Dished Cover #1 and Temporary Cover

Identifier

P

Design

( kPa)

T

Design

(C)

MAWP

( kPa)

MAP

( kPa)

MAEP

( kPa)

Te

external

(C)

MDMT

(C)

MDMT

Exemption

Total Corrosion

Allowance

(mm)

Impact

Test

Temporary Cover 11900.0 85.0 11915.30 12620.44 11624.76 85.0 17.0 Note 1 3.00 No

Cylinder #1 11900.0 85.0 13574.09 14479.64 7686.54 85.0 -53.2 Note 2 3.00 Yes


Transition #1 11900.0 85.0 12793.34 13645.29 984.08 85.0 -50.1 Note 3 3.00 Yes


Dished Cover #1 11900.0 85.0 14019.64 13526.32 23220.59 85.0 -40.0 Note 5 3.00 Yes

End Closure 11900.0 85.0 12055.32 14036.16 1088.07 85.0 -40.0 Note 6 3.00 Yes

End Closure - Flange Hub 11900.0 85.0 12320.93 13176.07 6709.92 85.0 -48.0 Note 7 3.00 Yes

Saddle #1 11900.0 85.0 11915.30 N/A N/A N/A N/A N/A N/A N/A

Chamber design MDMT is -46.00C

Chamber rated MDMT is 17.00C @ 11915.30 kPa

Chamber MAWP hot & corroded is 11915.30 kPa @ 85.0C

Chamber MAP cold & new is 12620.44 kPa @ 21.1C

Chamber MAEP is 984.08 kPa @ 85.0C

Vacuum rings did not govern the external pressure rating.

Notes for MDMT Rating:

Note # Exemption Details

1. Head impact test exemption temperature from Fig UCS-66M Curve B = 17 C UCS-66 governing thickness = 50 mm.

2. Material is impact tested per UG-84 to -46 C UCS-66(i) reduction of 7.2 C applied (ratio = 0.870568).



5. Bolts rated MDMT per Fig UCS-66 note (e) = -40 C Bolting limits MDMT rating.

6.UCS-66(b)(1)(b) has been applied.Flange is impact tested per UG-84 to -46 C

UCS-66(i) reduction of 8.5 C applied (ratio = 0.8489).

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

7. Material is impact tested per UG-84 to -46 C UCS-66(i) reduction of 2 C applied (ratio = 0.96513).

Design notes are available on the Settings Summary page.

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Revision History

No. Date Operator Notes

0 6/16/2011 waqas.haider New vessel created ASME Section VIII Division 1 [Build 6258]

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Settings Summary

COMPRESS Build 6258

Units: SI

Datum Line Location: 0.00 mm from right seam

Design

ASME Section VIII Division 1, 2007 Edition Metric

Design or Rating: Get Thickness from Pressure

Minimum thickness: 1.50 mm 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: 152.40 mm

Juncture calculations for > 30 only: Yes

Preheat P-No 1 Materials > 1.25" and

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

UG-22 (f) Wind reactions: No

UG-22 (f) Seismic reactions: No

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

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Thickness Summary

Component

IdentifierMaterial Diameter

(mm)

Length

(mm)

Nominal t

(mm)

Design t

(mm)

Joint

ELoad

Temporary Cover SA-516 65 924.00 OD 164.00 164.00* 163.78 1.0000 Internal

Cylinder #1 SA-516 65 824.00 ID 1800.00 50.00 43.86 1.0000 Internal


Transition #1 SA-516 65 824.00/875.00 ID 610.00 50.00 46.52 1.0000 Internal


Flange - Dished Cover #1 SA-516 65 875.00 ID 180.00 180.00 172.29 1.0000 Internal

Dished Cover #1 SA-516 65 1119.00 OD 249.14 164.00* 55.50 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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Weight Summary

Component

Weight ( kg) Contributed by Vessel Elements

Metal

New*

Metal

Corroded*Insulation &

SupportsLining

Piping+ Liquid

OperatingLiquid

TestLiquid

Temporary Cover 861.40 845.65 0.00 0.00 0.00 0.00 0.00

Cylinder #1 1,935.67 1,825.79 0.00 0.00 0.00 0.00 959.08

Cylinder #2 2,795.97 2,637.25 0.00 0.00 0.00 0.00 1,385.33

Transition #1 677.60 639.08 0.00 0.00 0.00 0.00 345.55

Cylinder #3 6,857.20 6,466.71 0.00 0.00 0.00 0.00 3,842.23

Dished Cover #1 1,391.09 1,376.25 0.00 0.00 0.00 0.00 50.58

Saddle #1 189.60 189.60 0.00 0.00 0.00 0.00 0.00

TOTAL: 14,708.54 13,980.33 0.00 0.00 0.00 0.00 6,582.78

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

Component

Weight ( kg) Contributed by Attachments

Body FlangesNozzles &

FlangesPackedBeds

Trays &Supports

Rings &Clips

VerticalLoads

New Corroded New Corroded

Temporary Cover 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00

Cylinder #1 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00

Cylinder #2 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00

Transition #1 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00

Cylinder #3 625.75 601.77 0.00 0.00 0.00 0.00 0.00 0.00

Dished Cover #1 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00

TOTAL: 625.75 601.77 0.00 0.00 0.00 0.00 0.00 0.00

Vessel operating weight, Corroded: 14,582 kg

Vessel operating weight, New: 15,334 kg

Vessel empty weight, Corroded: 14,582 kg

Vessel empty weight, New: 15,334 kgVessel test weight, New: 21,917 kg

Vessel center of gravity location - from datum - lift condition

Vessel Lift Weight, New: 15,334 kg

Center of Gravity: 5,375.51 mm

Vessel Capacity

Vessel Capacity** (New): 6,366 liters

Vessel Capacity** (Corroded): 6,456 liters**The vessel capacity does not include volume of nozzle, piping or other attachments.

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Hydrostatic Test

Shop test pressure determination for Chamber bounded by Dished Cover #1 and Temporary Cover based onMAWP per UG-99(b)

Shop hydrostatic test gauge pressure is 15,489.88 kPa at 21.11 C (the chamber MAWP = 11,915.3 kPa)

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

IdentifierLocal testpressure

kPa

Test liquidstatic head

kPa

UG-99stressratio

UG-99pressure

factor

Stressduring test

MPa

Allowabletest stress

MPa

Stressexcessive?

Cylinder #1 (1) 15,497.96 8.07 1 1.30 135.304 216 No

Cylinder #2 15,497.96 8.07 1 1.30 135.304 216 No

Transition #1 15,498.46 8.57 1 1.30 136.085 216 No

Cylinder #3 15,498.46 8.57 1 1.30 143.221 216 No

Dished Cover #1 15,498.46 8.57 1 1.30 37.21 216 No

Temporary Cover 15,497.96 8.07 1 1.30 162.347 324 No

End Closure 15,498.46 8.57 1 1.30 172.453 324 No

Notes:(1) Cylinder #1 limits the UG-99 stress ratio.

(2) VIII-2, AD-151.1(b) used as the basis for nozzle allowable test stress.(3) 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 Dished Cover #1 and Temporary

Cover .

Warning! UG-99(h): The test temperature of 21.11 degrees C is colder than the minimum recommendedtemperature of 34 degrees C

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Vacuum Summary

Component Line of Support

Elevation

above Datum

(mm)

Length

Le

(mm)

Temporary Cover - 11569.00 N/A

- 1/3 depth of Temporary Cover 11405.00 N/A

Cylinder #1 Top - 11405.00 4400.00

Cylinder #1 Bottom - 9605.00 4400.00

Cylinder #2 Top - 9605.00 4400.00

Cylinder #2 Bottom - 7005.00 4400.00

Transition #1 Top - 7005.00 594.05

- Transition #1 Top 7005.00 594.05

- Transition #1 Bottom 6395.00 594.05

Transition #1 Bottom - 6395.00 594.05

Cylinder #3 Top - 6395.00 6395.00

Cylinder #3 Bottom - 370.00 6395.00

- End Closure 0.00 N/A

- Flange - Dished Cover #1 -0.00 N/A

- 1/3 depth of Dished Cover #1 -29.38 N/A

Dished Cover #1 - -249.14 N/A

Note

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

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Cylinder #1


Component: Cylinder

Material specification: SA-516 65 (II-D Metric p. 14, ln. 34)Material is impact tested per UG-84 to -46 C


Internal design pressure: P = 11900 kPa @ 85CExternal design pressure: Pe = 103.421 kPa @ 85C

Static liquid head:

Pth =8.0739 kPa (SG=1.0000, Hs=824.00 mm, Horizontal test head)

Corrosion allowance: Inner C = 3.00 mm Outer C = 0.00 mm

Design MDMT = -46.00C Impact test performed

Rated MDMT = -53.20C Material is normalizedMaterial is not produced to Fine Grain Practice

PWHT is performed

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

Right circumferential joint - Full UW-11(a) Type 1

Estimated weight: New = 1935.6730 kg corr = 1825.7887 kg

Capacity: New = 959.8797 liters corr = 973.9081 litersID = 824.00 mm

Length Lc = 1800.00 mmt = 50.00 mm

Design thickness, (at 85.00C) UG-27(c)(1)

t = P*R/(S*E - 0.60*P) + Corrosion= 11900.00*415.00/(128000*1.00 - 0.60*11900.00) + 3.00

= 43.8633 mm

Maximum allowable working pressure, (at 85.00C) UG-27(c)(1)

P = S*E*t/(R + 0.60*t) - Ps= 128000*1.00*47.0003 / (415.00 + 0.60*47.0003) - 0.0000= 13574.0869 kPa

Maximum allowable pressure, (at 21.11C) UG-27(c)(1)

P = S*E*t/(R + 0.60*t)= 128000*1.00*50.0000 / (412.00 + 0.60*50.0000)

= 14479.6396 kPa

External Pressure, (Corroded & at 85.00C) UG-28(c)

L/Do = 4400.0005/924.0000 = 4.7619Do/t = 924.0000/5.702012 = 162.0481

From table G: A = 0.000127

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From table CS-2 Metric: B = 12.5694 MPa

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

= 4*12.5694/(3*(924.0000/5.702012))

= 103.4213 kPa

Design thickness for external pressure Pa = 103.4213 kPa

= t + Corrosion = 5.702012 + 3.00 = 8.70 mm

Maximum Allowable External Pressure, (Corroded & at 85.00C) UG-28(c)

L/Do = 4400.0005/924.00 = 4.7619

Do/t = 924.00/47.0003 = 19.6595



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

= 4*113.3350/(3*(924.00/47.0003))

= 7686.5415 kPa

% Extreme fiber elongation - UCS-79(d)

= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 50.00 / 437.0000) * (1 - 437.0000 /)

= 5.7208 %

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

A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 47.0003)= 0.012717

B = 120.1559 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScHC = 120.1559 MPa

Allowable Compressive Stress, Hot and New- ScHN, (table CS-2 Metric)

A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 50.0000)

= 0.013528B = 120.2329 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScHN = 120.2329 MPa

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

A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 50.0000)

= 0.013528

B = 120.2329 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScCN = 120.2329 MPa

Allowable Compressive Stress, Cold and Corroded- ScCC, (table CS-2 Metric)

A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 47.0003)

= 0.012717

B = 120.1559 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScCC = 120.1559 MPa

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

A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 47.0003)

= 0.012717

B = 120.1559 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScVC = 120.1559 MPa

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Cylinder #2


Component: Cylinder




Static liquid head:




Rated MDMT = -53.20C Material is normalizedMaterial is produced to Fine Grain Practice

PWHT is performed





Length Lc = 2600.00 mmt = 50.00 mm



= 43.8633 mm


P = S*E*t/(R + 0.60*t) - Ps= 128000*1.00*47.0003 / (415.00 + 0.60*47.0003) - 0.0000= 13574.0869 kPa


P = S*E*t/(R + 0.60*t)= 128000*1.00*50.0000 / (412.00 + 0.60*50.0000)

= 14479.6396 kPa


L/Do = 4400.0005/924.0000 = 4.7619Do/t = 924.0000/5.702012 = 162.0481


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

= 4*12.5694/(3*(924.0000/5.702012))

= 103.4213 kPa


= t + Corrosion = 5.702012 + 3.00 = 8.70 mm


L/Do = 4400.0005/924.00 = 4.7619

Do/t = 924.00/47.0003 = 19.6595



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

= 4*113.3350/(3*(924.00/47.0003))

= 7686.5415 kPa


= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 50.00 / 437.0000) * (1 - 437.0000 /)

= 5.7208 %


A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 47.0003)= 0.012717

B = 120.1559 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScHC = 120.1559 MPa


A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 50.0000)

= 0.013528B = 120.2329 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScHN = 120.2329 MPa

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A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 50.0000)

= 0.013528

B = 120.2329 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScCN = 120.2329 MPa


A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 47.0003)

= 0.012717

B = 120.1559 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScCC = 120.1559 MPa


A = 0.125 / (Ro / t)

= 0.125 / (462.0000 / 47.0003)

= 0.012717

B = 120.1559 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScVC = 120.1559 MPa

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Transition #1


Component: Transition



Internal design pressure: P = 11900.0000 kPa @ 85.00CExternal design pressure: Pe = 103.4214 kPa @ 85.00C

Static liquid head:

Pth =8.0739 kPa (SG=1.0000, Hs=824.00 mm, Horizontal test head at small end)Pth =8.5736 kPa (SG=1.0000, Hs=875.00 mm, Horizontal test head at large end)


Design MDMT = -46.00C Impact test performedRated MDMT = -50.10C Material is normalized

Material is produced to Fine Grain Practice

PWHT is performed

Radiography: Category A joints - Full UW-11(a) Type 1

Circ. joint top/left - Full UW-11(a) Type 1Circ. joint right/bottom - Full UW-11(a) Type 1

Estimated weight: New = 677.6 kg corr = 639.1 kgCapacity: New = 345.8 liters corr = 350.8 liters

Axial length = 610.00 mmLarge End ID = 875.0000 mm

Small End ID = 824.0000 mmCone tc = 50.00 mm

Design thickness, (at 85.00C) UG-32(g) (Large End)

t = P*D / (2*Cos()*(S*E - 0.60*P)) + C

=11900.0000*881.0203 / (2*Cos(4.779)*(128000*1.00 - 0.60*11900.0000))

+ 2.9997= 46.52 mm

Small End design thickness (t = 44.00 mm) does not govern.

MAWP, (Corroded at 85.00C) UG-32(g) (Large End)

P = 2*S*E*t*Cos() / (D + 1.20*t*Cos()) - Ps

=2*128000*1.00*47.0003*Cos(4.779) / (881.0203 + 1.20*47.0003*Cos(4.779)) -

0.0000= 12793.34 kPa

Small End MAWP (13529.5664 kPa) does not govern.

MAP, (New at 21.11C) UG-32(g) (Large End)

P = 2*S*E*t*Cos() / (D + 1.20*t*Cos()) - Ps=

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2*128000*1.00*50.0000*Cos(4.779) / (875.0000 + 1.20*50.0000*Cos(4.779)) -0.0000

= 13645.29 kPa

Small End MAP (14432.7021 kPa) does not govern.

External Pressure, (Corroded & at 85.00C) UG-33(f)

DL

= 975.35 mm

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

= (610.0000/2)*(1+924.3489/975.3489)

= 594.05 mm

te = t * Cos()

= 2.542863

Le/DL = 594.0519/975.3489 = 0.6091

DL/te = 975.3489/2.542863 = 383.5633



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

= 4*29.7511/(3*(975.3489/2.542863))

= 103.4201 kPa


= te/Cos() + Corrosion = 2.542863/Cos() + 3.00 = 5.55 mm

Maximum Allowable External Pressure, (Corroded & at 85.00C) UG-33(f)

te = t*Cos() = 46.84 mm

Le/DL = 594.0519/975.3489 = 0.6091DL/te = 975.3489/46.8368 = 20.8244



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

= 4*121.0000/(3*(975.3489/46.8368))

= 7747.3252 kPa


= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 50.1744 / 437.0872) * (1 - 437.0872 /)= 5.7396 %

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Cone juncture large end calculations, P =12,793.34 kPaAppendix 1-5(d)

Loading

Area check

required

( < )

U-2(g)

analysis

required

f1(N /cm)

QL

(N /cm)

ArL

(cm2)

AeL

(cm2)

Ring

area (cm2)Status

Pressure No No 0 28,177.31 0 0.24 none OK

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Cone large end calculations per Appendix 1-5(d), pressure, corroded

f1 = -Wl/(*2*Rm) + 12*Ml/(*Rm2)

= -0/(*2*18.2677) + 12*0/(*18.26772)= 0 lb/in (0 N/cm)

P*RL/2 = 16,089.66 lb/in (28,177.31 N/cm)

|f1| = no additional reinforcement is required.

Cone juncture small end calculations P = 12,793.34 kPaAppendix 1-5(e)

Loading

Area check

required( < )

U-2(g)

analysisrequired

f2(N /cm) Qs(N /cm) Ars(cm2) Aes(cm2)Ring

area (cm2) Status


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Cone small end calculations per Appendix 1-5(e), pressure, corroded

f2 = -Ws/(*2*Rm) + 12*Ms/(*Rm2)

= -0/(*2*17.2638) + 12*0/(*17.26382)= 0 lb/in (0 N/cm)

P*Rs/2 = 15,158.25 lb/in (26,546.16 N/cm)


Cone large end calculations for external pressure of 984.08 kPaAppendix 1-8(b)

Loading

Area

checkreq'd

<

U-2(g)

analysis

req'df1

(N /cm)QL

(N /cm)ArL

(cm2)AeL(cm2)

Ringarea (cm2)

Areastatus

I's(cm4)

I'(cm4)

Istatus

Vacuum No No 0 2,398.69 0.07 110.87 none OK 214.5756 214.5798 OK

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Cone large end calculations per Appendix 1-8(b), weight + external pressure

f1 = Wl/(*2*Rm) + 12*Ml/(*Rm2)

= 0/(*2*18.2677) + 12*0/(*18.26772)= 0 lb/in (0 N/cm)

P*RL/2 = 1,369.689 lb/in (2,398.692 N/cm)

f1 + P*RL/2 is in compression so a U-2(g) analysis is not required.

P/(Ss*E1) = 142.7286/(18,564.83*1) = 0.007688

From table 1-8.1 = 8.61

As >= no additional reinforcement is required.M = -R

L*tan()/2 + L

L/2 + (R

L

2 - Rs2)/(3*R

L*tan())

= -19.1929*tan(4.7792)/2 + 251.7717/2 + (19.19292 - 18.1892)/(3*19.1929*tan(4.7792))= 132.8794

Lc = (L2 + (R

L- Rs)

2)0.5

= (24.01572 + (19.1929 - 18.189)2)0.5= 24.03672

ATL

= LL*ts/2 + Lc * tc/2 + As

= 251.7717*1.8504/2 + 24.0367 * 1.8504/2 + 0= 255.1785

FL

= P*M + f1*tan()

= 142.7286*132.8794 + 0*tan(4.7792)= 18,965.69

B = 0.75*FL*D

L/A

TL

= 0.75*18,965.6895*38.3858/255.1785

= 2,139.719

From Table CS-2 Metric: A = 0.000149 (shell, 85C)

I's

= A*DL

2*ATL/10.9

= 0.0001494467*38.38582*255.1785/10.9= 5.1552 in4 (214.5756 cm4)

The calculated I'for the combined shell-cone cross section is 5.1553 in4 (214.5798 cm4)

As I'>= I's

the large end is adequately stiffened per Appendix 1-8(b).

Cone small end calculations for external pressure of 984.08 kPaAppendix 1-8(c)

Loading

U-2(g)

analysis

req'd

f2(N /cm)

Qs

(N /cm)

Ars

(cm2)

Aes

(cm2)

Ring

area (cm2)

Area

statusI's

(cm4)I'

(cm4)

I

status

Vacuum No 0 2,273.22 0.69 85.15 none OK 125.798 208.3196 OK

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Cone small end calculations per Appendix 1-8(c), weight + external pressure

f2 = Ws/(*2*Rm) + 12*Ms/(*Rm2)

= 0/(*2*17.2638) + 12*0/(*17.26382)= 0 lb/in (0 N/cm)

P*Rs/2 = 1,298.044 lb/in (2,273.222 N/cm)

f2 + P*Rs/2 is in compression so a U-2(g) analysis is not required.

Qs = P*Rs/2 + f2= 1,298.0436 + 0

= 1,298.044 lb/in (2,273.222 N/cm)

Ars = (k*Qs*Rs*tan()/(Ss*E1))= (1*1,298.0436*18.189*tan(4.7792)/(18,564.832*1))

= 0.1063278 in2 (0.6859843 cm2)

Aes = 0.55*(Ds*ts)0.5*((ts - t) + (tc - tr)/cos())

= 0.55*(36.378*1.8504)0.5*((1.8504 - 0.5588952) + (1.8504 - 0.2226677)/cos(4.7792))

= 13.19866 in2 (85.15244 cm2)

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

N = Rs*tan()/2 + Ls/2 + (RL2 - Rs

2)/(6*Rs*tan())= 18.189*tan(4.7792)/2 + 173.2284/2 + (19.19292 - 18.1892)/(6*18.189*tan(4.7792))

= 91.48763

Lc = (L2 + (R

L- Rs)

2)0.5

= (24.01572 + (19.1929 - 18.189)2)0.5

= 24.03672

Ats = Ls*ts/2 + Lc * tc/2 + As

= 173.2284*1.8504/2 + 24.0367 * 1.8504/2 + 0= 182.51

Fs = P*N + f2*tan()

= 142.7286*91.4876 + 0*tan(4.7792)= 13,057.90

B = 0.75*Fs*Ds/Ats= 0.75*13,057.9014*36.378/182.51

= 1,952.028

From Table CS-2 Metric: A = 0.000136 (shell, 85C)

I's

= A*Ds2*Ats/10.9

= 0.0001363963*36.3782*182.51/10.9

= 3.02231 in4 (125.798 cm4)

The calculated I'for the combined shell-cone cross section is 5.0049 in4 (208.3196 cm4)

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As I'>= I's

the small end is adequately stiffened per Appendix 1-8(c).

MAP Cone juncture large end calculations, P =13,645.29 kPaAppendix 1-5(d)

Loading

Area check

required

( < )

U-2(g)

analysis

required

f1(N /cm)

QL

(N /cm)

ArL

(cm2)

AeL

(cm2)

Ring

area (cm2)Status


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Cone large end calculations per Appendix 1-5(d), pressure, new

f1 = -Wl/(*2*Rm) + 12*Ml/(*Rm2)

= -0/(*2*18.2087) + 12*0/(*18.20872)= 0 lb/in (0 N/cm)

P*RL/2 = 17,044.26 lb/in (29,849.06 N/cm)


MAP Cone juncture small end calculations P = 13,645.29 kPaAppendix 1-5(e)

Loading

Area check

required( < )

U-2(g)

analysisrequired

f2(N /cm) Qs(N /cm) Ars(cm2) Aes(cm2)Ring

area (cm2) Status


Cone small end calculations per Appendix 1-5(e), pressure, new

f2 = -Ws/(*2*Rm) + 12*Ms/(*Rm2)

= -0/(*2*17.2047) + 12*0/(*17.20472)= 0 lb/in (0 N/cm)

P*Rs/2 = 16,050.82 lb/in (28,109.29 N/cm)


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Cylinder #3


Component: Cylinder




Static liquid head:




Rated MDMT = -50.30C Material is not normalizedMaterial is not produced to Fine Grain Practice

PWHT is performed





Length Lc = 6025.00 mmt = 50.00 mm



= 46.3728 mm


P = S*E*t/(R + 0.60*t) - Ps= 128000*1.00*47.0003 / (440.50 + 0.60*47.0003) - 0.0000= 12835.5771 kPa


P = S*E*t/(R + 0.60*t)= 128000*1.00*50.0000 / (437.50 + 0.60*50.0000)

= 13689.8408 kPa


L/Do = 6395.0000/975.0000 = 6.5590Do/t = 975.0000/6.970780 = 139.8696


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

= 4*10.8491/(3*(975.0000/6.970780))

= 103.4213 kPa


= t + Corrosion = 6.970780 + 3.00 = 9.97 mm


L/Do = 6395.0000/975.00 = 6.5590

Do/t = 975.00/47.0003 = 20.7446



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

= 4*110.0567/(3*(975.00/47.0003))

= 7073.7676 kPa


= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 50.00 / 462.5000) * (1 - 462.5000 /)

= 5.4054 %


A = 0.125 / (Ro / t)

= 0.125 / (487.5000 / 47.0003)= 0.012051

B = 120.0891 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScHC = 120.0891 MPa


A = 0.125 / (Ro / t)

= 0.125 / (487.5000 / 50.0000)

= 0.012821B = 120.1661 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScHN = 120.1661 MPa

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A = 0.125 / (Ro / t)

= 0.125 / (487.5000 / 50.0000)

= 0.012821

B = 120.1661 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScCN = 120.1661 MPa


A = 0.125 / (Ro / t)

= 0.125 / (487.5000 / 47.0003)

= 0.012051

B = 120.0891 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScCC = 120.0891 MPa


A = 0.125 / (Ro / t)

= 0.125 / (487.5000 / 47.0003)

= 0.012051

B = 120.0891 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScVC = 120.0891 MPa

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Temporary Cover


Component: Welded Cover

Material specification: SA-516 65 (II-D Metric p. 14, ln. 34)Head impact test exemption temperature from Fig UCS-66M Curve B = 17 C

UCS-66 governing thickness = 50 mm.

Internal design pressure: P = 11900.0000 kPa @ 85.00CExternal design pressure: Pe = 103.4214 kPa @ 85.00C

Static liquid head:

Pth =4.0370 kPa (SG=1.0000, Hs=412.00 mm,Horizontal test head)


Design MDMT = -46.00C No impact test performed

Rated MDMT = 17.00C Material is not normalizedMaterial is not produced to Fine Grain Practice

PWHT is performed

Radiography: Category A joints - Seamless No RT

Estimated weight: New = 861.4 kg corr = 845.6 kgHead outside diameter = 924.00 mmCover thickness = 164.00 mm

Factor C from Fig. UG-34, sketch (b-2), (e through g)

C = 0.33*tr/ts = 0.33*1.8025/1.8504 = 0.3215

Design thickness, (at 85 C) UG-34 (c)(2)

t = d*Sqr(C*P/(S*E)) + Corrosion

= 36.6142*Sqr(0.3215*1,725.9491/(18,564.83*1)) + 0.1181= 6.4482 in (163.78 mm)

Maximum allowable working pressure, (at 85 C )

C = 0.33*tr/ts = 0.33*1.805/1.8504 = 0.3219

P = (S*E/C)*(t/d)2 - Ps= (18,564.83*1/0.3219267)*(6.3386/36.6142)2 - 0

= 1,728.168 psi (11,915.3 kPa)

Maximum allowable pressure, (At 21.11 C )

C = 0.33*tr/ts = 0.33*1.9061/1.9685 = 0.3195

P = (S*E/C)*(t/d)2

= (18,564.83*1/0.3195)*(6.4567/36.378)2

= 1,830.44 psi (12,620.44 kPa)

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Design thickness for external pressure, (at 85 C) UG-34(c)(2)

t = d*Sqr(C*Pe/(S*E)) + Corrosion= 36.6142*Sqr(0.33*15/(18,564.83*1)) + 0.1181

= 0.716 in (18.19 mm)

Maximum allowable external pressure, (At 85 C )

P = (S*E/C)*(t/d)2

= (18,564.83*1/0.33)*(6.3386/36.6142)2

= 1,686.028 psi (11,624.76 kPa)

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Dished Cover #1

ASME Section VIII, Division 1, 2007 Edition Metric

Component Dished Cover Figure 1-6 Sketch (b)

Internal design pressure, P 11,900 kPa @ 85 C

External design pressure, Pe 103.4214 kPa @ 85 C

Design MDMT -46 C

Rated MDMT -40 C

Component Properties Head Flange

Material specification SA-516 65 SA-516 65 (II-D Metric p. 14, ln. 34)

Inside crown radius, L 674.6 mm

Thickness (note 1) 164 mm 180 mm

Inner diameter, B 875 mm

Outer diameter, A 1,119 mm

Bolt circle, C 980 mm

Bolting 12 - 3.25 in dia

Bolt materialSA-193 B7 Bolt 64 < t

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Corrosion allowance outer/flange 0 mm 0 mm

Impact tested -46 C -46 C

Normalized Yes Yes

PWHT Yes Yes

Optimize MDMT/Find MAWP No No

Bolting Holes Slotted No1

Flange thickness does not include consideration of the flange facing.

Liquid Specific gravity Liquid HeightStatic liquidpressure

Operating Internal 1 0 mm 0 kPa

Horizontal test 1 875 mm 8.5736 kPa

Vertical test 1 11,490.14 mm 0 kPa

Head Flange

Estimated weightNew 852.3191 kg 538.7727 kg

Corroded 849.141 kg 527.1065 kg

CapacityNew 50.6267 liters 0 liters

Corroded 51.8524 liters 0 liters

MDMT Rating:

Flange is impact tested per UG-84 to -46 CUCS-66(i) reduction of 3.3 C applied (ratio = 0.9413244).

Flange MDMT Rating = -49.3 C

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

Head is impact tested per UG-84 to -46 C

UCS-66(i) reduction of 80 C applied (ratio = 0.3264827).Head MDMT Rating = -105 C

Head Design Thickness per Appendix 1-6(e)(1)(a):

tr = 5*P*L / (6*S) + Corrosion

= 5*11,900*677.6 / (6*128,000) + 3

= 55.5 mm

Head Design Thickness per Appendix 1-6(e)(1)(b):

Equivalent outside spherical radius (Ro)

= Outside crown radius= 838.6 mm

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A = 0.125 / (Ro/t)= 0.125 / (838.6/2.42)

= 0.000361

From Table CS-2 Metric: B=35.7978 MPa

Pa = B/(Ro/t)

= 35,797.83/(838.6/2.42)= 103.4213 kPa

te = 2.42 + 3 = 5.42 mm

Flange Required Thickness per Appendix 1-6(e)(2):

Tr = ((Mo / (S*B))*(A + B) / (A - B))1/2

Operating, Hot &

Corr

Operating

Mo385,234.9

N-m

Tr = ((385,234.9 / (128,000*881))*(1,119 + 881) / (1,119 -881))1/2 *103

169.43mm

Gasket Seating

Mo

= Mg

395,944.1

N-m

Tr = ((395,944.1 / (128,000*881))*(1,119 + 881) / (1,119 -

881))1/2 *103171.77

mm

Vacuum, Hot & Corr

OperatingMo 190.3 N-m

Tr = ((190.3 / (128,000*881))*(1,119 + 881) / (1,119 - 881))1/2

*1033.77 mm

Gasket SeatingMo = Mg

218,184.2

N-m

Tr = ((218,184.2 / (128,000*881))*(1,119 + 881) / (1,119 -881))1/2 *103

127.51mm

Flange Design Thickness = 172.29 + 0 =172.29mm

Head MAWP per Appendix 1-6(e)(1)(a):

MAWP = 6*S*t / (5*L) - Ps

= 6*128,000*161 / (5*677.6) - 0

= 36,495.94 kPa

FlangeMAWP perAppendix1-6(e)(2):

MAWP =14,019.64

kPa

Head MAP per Appendix 1-6(e)(1)(a):

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MAP = 6*S*t / (5*L) - Ps

= 6*128,000*164 / (5*674.6) - 0

= 37,341.24 kPa

Flange MAPperAppendix

1-6(e)(2):

MAP =

13,526.32kPa

Head MAEP per Appendix 1-6(e)(1)(b):

Equivalent outside spherical radius (Ro)

= Outside crown radius= 838.6 mm

A = 0.125 / (Ro/t)

= 0.125 / (838.6/161)= 0.023998

From Table CS-2 Metric: B=120.9488 MPa

Pa = B/(Ro/t)= 120,948.8/(838.6/161)= 23,220.59 kPa

MAEP = 23,220.59 kPa

Flange

MAEP perAppendix1-6(e)(2):

MAEP =236,235.3

kPa


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

= (75*164 / 756.6)*(1 - 756.6 /)

= 16.2569%

Flange calculations for Internal Pressure + Weight Only

Gasket details from facing sketch 6, Column I

Ring gasket width w = 7 mm

b0 = w/8 = 0.88 mm

Effective gasket seating width, b = b0 = 0.88 mm

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G = (gasket OD + gasket ID) / 2 = 887 mm

hG = (C - G)/2 = (980 - 887)/2 = 46.5 mm

hD = (C - B)/2 = (980 - 881)/2 = 49.5 mm

hT = (hD + hG)/2 = (49.5 + 46.5)/2 = 48 mm

Hp = 2*b*3.14*G*m*P

= 2*0.88*3.14*887*2*11.9= 116,002.9 N

H = 0.785*G2*P= 0.785*8872*11.9

= 7,349,602.31 N

HD = 0.785*B2*P

= 0.785*8812*11.9= 7,250,500.37 N

HT = H - HD= 7,349,603 - 7,250,501

= 99,101.94 N

Wm1 = H + Hp= 7,349,603 + 116,002.9= 7,465,605.27 N

Per VIII-1, Appendix 2-5(a)(2): Wm1 from the mating flange governs so Wm1 = 7,813,614.16 N

Wm2 = 3.14*b*G*y= 3.14*0.88*887*17.2369

= 42,006.93 N

Per VIII-1, Appendix 2-5(a)(2): Wm2

from the mating flange governs so Wm2

= 168,027.7 N

Required bolt area, Am = greater of Am1, Am2 = 491.4222 cm2

Am1 = Wm1/Sb = 7,813,614/(100*159) = 491.4222 cm2

Am2 = Wm2/Sa = 168,027.7/(100*159) = 10.5678 cm2

Total area for 12- 3.25 in dia bolts, corroded, Ab = 579.6376 cm2

W = (Am + Ab)*Sa/2= (49,142.22 + 57,963.75)*159/2

= 8,514,926.98 N

MD = HD*hD = 7,250,501*0.0495 = 358,901.5 N-m

MT = HT*hT = 99,101.94*0.048 = 4,756.9 N-m

HG = Wm1 - H = 7,813,614 - 7,349,603 = 464,011.8 N

MG = HG*hG = 464,011.8*0.0465 = 21,576.6 N-m

Mo = MD + MT + MG = 358,901.5 + 4,756.9 + 21,576.6 = 385,234.9 N-m

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Mg = W*hG = 8,514,927*0.0465 = 395,944.1 N-m

Flange calculations for External Pressure + Weight Only per VIII-1, Appendix 2-11

Gasket details from facing sketch 6, Column I

Ring gasket width w = 7 mm

b0 = w/8 = 0.88 mm


G = (gasket OD + gasket ID) / 2 = 887 mm

hG = (C - G)/2 = (980 - 887)/2 = 46.5 mm

hD = (C - B)/2 = (980 - 881)/2 = 49.5 mm

hT = (hD + hG)/2 = (49.5 + 46.5)/2 = 48 mm

Hp = 2*b*3.14*G*m*P= 2*0.88*3.14*887*2*0.1034

= 1,008.17 N

H = 0.785*G2*P= 0.785*8872*0.1034

= 63,874.44 N

HD = 0.785*B2*P

= 0.785*8812*0.1034= 63,013.16 N

HT = H - HD= 63,874.44 - 63,013.16

= 861.28 N

Wm1 = H + Hp= 63,874.44 + 1,008.17

= 64,882.61 N

Per VIII-1, Appendix 2-5(a)(2): Wm1 from the mating flange governs so Wm1 = 67,907.11 N

Wm2 = 3.14*b*G*y= 3.14*0.88*887*17.2369= 42,006.93 N

Per VIII-1, Appendix 2-5(a)(2): Wm2 from the mating flange governs so Wm2 = 168,027.7 N


Am1 = 0.785*G2*(Pm - Pr)/Sb = 0/(100*159) = 0 cm

2

Am2 = Wm2/Sa = 168,027.7/(100*159) = 10.5678 cm2


W = (Am2 + Ab)*Sa/2

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= (1,056.778 + 57,963.75)*159/2= 4,692,133.19 N

Mo = HD*(hD - hG) + HT*(hT - hG)= 63,013.16*(0.0495 - 0.0465) + 861.28*(0.048 - 0.0465)

= 190.3 N-m

Mg = W*hG = 4,692,133*0.0465 = 218,184.2 N-m

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End Closure

ASME VIII-1, 2007 Edition Metric, Appendix 2 Flange Calculations

Flange is attached to: Cylinder #3 (Right)

Flange type: Weld neck integralFlange material specification: SA-516 65 (II-D Metric p. 14, ln. 34)

Bolt material specification: SA-193 B7 Bolt 64 < t

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Note: this flange is calculated as an integral type.

Determination of Flange MDMT

UCS-66(b)(1)(b) has been applied.Flange is impact tested per UG-84 to -46 C

UCS-66(i) reduction of 8.5 C applied (ratio = 0.8489).Bolts rated MDMT per Fig UCS-66 note (e) = -40 C

The rated flange MDMT is -40 C

Flange calculations for Internal Pressure + Weight Only

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Gasket details from facing sketch 1(a) or (b), Column II

Gasket width N = 7 mm

b0 = N/2 = 3.5 mm


G = (OD of contact face + gasket ID) / 2 = 887 mm

hG = (C - G)/2 = (980 - 887)/2 = 46.5 mm

hD = R + g1/2 = 2.5 + 47/2 = 26 mm

hT = (R + g1 + hG)/2 = (2.5 + 47 + 46.5)/2 = 48 mm

Hp = 2*b*3.14*G*m*P= 2*3.5*3.14*887*2*11.9= 464,011.6 N

H = 0.785*G2*P

= 0.785*8872*11.9

= 7,349,602.31 N

HD = 0.785*B2*P

= 0.785*8812*11.9= 7,250,500.37 N

HT = H - HD= 7,349,603 - 7,250,501

= 99,101.94 N

Wm1 = H + Hp= 7,349,603 + 464,011.6= 7,813,614.16 N

Wm2 = 3.14*b*G*y

= 3.14*3.5*887*17.2369= 168,027.7 N


Am1 = Wm1/Sb = 7,813,614/(100*159) = 491.4222 cm2

Am2 = Wm2/Sa = 168,027.7/(100*159) = 10.5678 cm2


W = (Am + Ab)*Sa/2

= (49,142.22 + 57,963.75)*159/2= 8,514,926.98 N

MD = HD*hD = 7,250,501*0.026 = 188,513.8 N-m

MT = HT*hT = 99,101.94*0.048 = 4,756.9 N-m

HG = Wm1 - H = 7,813,614 - 7,349,603 = 464,011.8 N

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MG = HG*hG = 464,011.8*0.0465 = 21,576.6 N-m

Mo = MD + MT + MG = 188,513.8 + 4,756.9 + 21,576.6 = 214,847.3 N-m

Mg = W*hG = 8,514,927*0.0465 = 395,944.1 N-m

Hub and Flange Factors

h0 = (B*g0)1/2 = (881*45)1/2 = 199.11 mm

From FIG. 2-7.1, where K = A/B = 1,119/881 = 1.2701

T = 1.81 Z = 4.2612 Y = 8.2558U =9.0723

h/h0 = 0.339 g1/g0 = 1.0444

F = 0.9038 V = 0.5217 e = F/h0 = 0.1153

d = (U/V)*h0*g02= (9.072305/0.5217)*19.9111*4.52

= 7,012.3359 cm3

Stresses at operating conditions - VIII-1, Appendix 2-7

f = 1

L = (t*e + 1)/T + t3/d

= (11.6*0.0454 + 1)/1.810018 + 11.63/7,012.3359= 1.065981

SH = f*Mo/(L*g12*B)

= 1e3*1*214,847.3/(1.065981*472*881)= 103.563 MPa

SR = (1.33*t*e + 1)*Mo/(L*t2*B)

= (1.33*116*0.0045 + 1)*1e3*214,847.3/(1.065981*1162*881)

= 28.908 MPa

ST = Y*Mo/(t2*B) - Z*SR

= 1e3*8.2558*214,847.3/(1162*881) - 4.2612*28.908= 26.442 MPa

Allowable stress Sfo = 128 MPa

Allowable stress Sno = 128 MPa

ST does not exceed SfoSH does not exceed Min[ 1.5*Sfo, 2.5*Sno ] = 192 MPaSR does not exceed Sfo0.5(S

H+ S

R) = 66.235 MPa does not exceed S

fo0.5(SH + ST) = 65.002 MPa does not exceed Sfo

Stresses at gasket seating - VIII-1, Appendix 2-7

SH = f*Mg/(L*g12*B)

= 1e3*1*395,944.1/(1.065981*472*881)

= 190.857 MPa

SR = (1.33*t*e + 1)*Mg/(L*t2*B)

= (1.33*116*0.0045 + 1)*1e3*395,944.1/(1.065981*1162*881)

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= 53.275 MPa

ST = Y*Mg/(t2*B) - Z*SR

= 8.2558*1e3*395,944.1/(1162*881) - 4.2612*53.275= 48.729 MPa

Allowable stress Sfa = 128 MPa

Allowable stress Sna = 128 MPa

ST does not exceed SfaSH does not exceed Min[ 1.5*Sfa, 2.5*Sna ] = 192 MPaSR does not exceed Sfa0.5(SH + SR) = 122.066 MPa does not exceed Sfa0.5(SH + ST) = 119.793 MPa does not exceed Sfa

Flange rigidity per VIII-1, Appendix 2-14

J = 52.14*V*Mo/(L*E*g02*KI*h0)

= 1e3*52.14*0.5217*395,944.1/(1.066*202,272.218*452*0.3*199.11)= 0.4129076

The flange rigidity index J does not exceed 1; satisfactory.

Flange calculations for External Pressure + Weight Only per VIII-1, Appendix 2-11

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Gasket details from facing sketch 1(a) or (b), Column II

Gasket width N = 7 mm

b0 = N/2 = 3.5 mm


G = (OD of contact face + gasket ID) / 2 = 887 mm

hG = (C - G)/2 = (980 - 887)/2 = 46.5 mm

hD = R + g1/2 = 2.5 + 47/2 = 26 mm

hT = (R + g1 + hG)/2 = (2.5 + 47 + 46.5)/2 = 48 mm

Hp = 2*b*3.14*G*m*P= 2*3.5*3.14*887*2*0.1034= 4,032.66 N

H = 0.785*G2*P

= 0.785*8872*0.1034

= 63,874.44 N

HD = 0.785*B2*P

= 0.785*8812*0.1034= 63,013.16 N

HT = H - HD= 63,874.44 - 63,013.16

= 861.28 N

Wm1 = H + Hp= 63,874.44 + 4,032.66= 67,907.11 N

Wm2 = 3.14*b*G*y

= 3.14*3.5*887*17.2369= 168,027.7 N


Am1 = 0.785*G2*(Pm - Pr)/Sb = 0/(100*159) = 0 cm

2

Am2 = Wm2/Sa = 168,027.7/(100*159) = 10.5678 cm2


W = (Am2 + Ab)*Sa/2

= (1,056.778 + 57,963.75)*159/2= 4,692,133.19 N

Mo = HD*(hD - hG) + HT*(hT - hG)

= 63,013.16*(0.026 - 0.0465) + 861.28*(0.048 - 0.0465)= 1,290.5 N-m

Mg = W*hG = 4,692,133*0.0465 = 218,184.2 N-m

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Hub and Flange Factors

h0 = (B*g0)1/2 = (881*45)1/2 = 199.11 mm

From FIG. 2-7.1, where K = A/B = 1,119/881 = 1.2701

T = 1.81 Z = 4.2612 Y = 8.2558U =9.0723

h/h0 = 0.339 g1/g0 = 1.0444

F = 0.9038 V = 0.5217 e = F/h0 = 0.1153

d = (U/V)*h0*g02= (9.072305/0.5217)*19.9111*4.52

= 7,012.3359 cm3

Stresses at operating conditions - VIII-1, Appendix 2-7

f = 1

L = (t*e + 1)/T + t3/d

= (11.6*0.0454 + 1)/1.810018 + 11.63/7,012.3359

= 1.065981

SH = f*Mo/(L*g12*B)

= 1e3*1*1,290.5/(1.065981*472*881)

= 0.622 MPa

SR = (1.33*t*e + 1)*Mo/(L*t2*B)

= (1.33*116*0.0045 + 1)*1e3*1,290.5/(1.065981*1162*881)

= 0.174 MPa

ST = Y*Mo/(t2*B) - Z*SR

= 1e3*8.2558*1,290.5/(1162*881) - 4.2612*0.174= 0.159 MPa

Allowable stress Sfo = 128 MPa

Allowable stress Sno = 128 MPa

ST does not exceed SfoSH does not exceed Min[ 1.5*Sfo, 2.5*Sno ] = 192 MPaSR does not exceed Sfo0.5(SH + SR) = 0.398 MPa does not exceed Sfo0.5(SH + ST) = 0.39 MPa does not exceed Sfo

Stresses at gasket seating - VIII-1, Appendix 2-7

SH

= f*Mg/(L*g

1

2*B)= 1e3*1*218,184.2/(1.065981*472*881)

= 105.171 MPa

SR = (1.33*t*e + 1)*Mg/(L*t2*B)

= (1.33*116*0.0045 + 1)*1e3*218,184.2/(1.065981*1162*881)= 29.357 MPa

ST = Y*Mg/(t2*B) - Z*SR

= 8.2558*1e3*218,184.2/(1162*881) - 4.2612*29.357= 26.852 MPa

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Allowable stress Sfa = 128 MPa

Allowable stress Sna = 128 MPa

ST does not exceed SfaSH does not exceed Min[ 1.5*Sfa, 2.5*Sna ] = 192 MPaSR does not exceed Sfa0.5(SH + SR) = 67.264 MPa does not exceed Sfa0.5(SH + ST) = 66.012 MPa does not exceed Sfa

Flange rigidity per VIII-1, Appendix 2-14

J = 52.14*V*Mo/(L*E*g02*KI*h0)

= 1e3*52.14*0.5217*218,184.2/(1.066*202,272.218*452*0.3*199.11)

= 0.2275319

The flange rigidity index J does not exceed 1; satisfactory.

End Closure - Flange hub


Component: Flange hubMaterial specification: SA-516 65 (II-D Metric p. 14, ln. 34)Material is impact tested per UG-84 to -46 C

UCS-66(i) reduction of 2 C applied (ratio = 0.96513).

Internal design pressure: P = 11900 kPa @ 85C

External design pressure: Pe = 103.421 kPa @ 85C

Static liquid head:

Not Considered



Rated MDMT = -48.00C Material is normalizedMaterial is produced to Fine Grain Practice

PWHT is performed

Radiography: Longitudinal joint - Seamless No RT

Left circumferential joint - Full UW-11(a) Type 1Right circumferential joint - N/A


Capacity: New = 40.5894 liters corr = 41.1479 liters

ID = 875.00 mmLength Lc = 67.50 mm

t = 48.00 mm


t = P*R/(S*E - 0.60*P) + Corrosion= 11900.00*440.50/(128000*1.00 - 0.60*11900.00) + 3.00= 46.3728 mm

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P = S*E*t/(R + 0.60*t) - Ps= 128000*1.00*45.0003 / (440.50 + 0.60*45.0003) - 0.0000= 12320.9297 kPa


P = S*E*t/(R + 0.60*t)

= 128000*1.00*48.0000 / (437.50 + 0.60*48.0000)= 13176.0664 kPa


L/Do = 6395.0000/971.0001 = 6.5860Do/t = 971.0001/6.954663 = 139.6185



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

= 4*10.8297/(3*(971.0001/6.954663))= 103.4216 kPa


= t + Corrosion = 6.954663 + 3.00 = 9.95 mm


L/Do = 6395.0000/971.00 = 6.5860Do/t = 971.00/45.0003 = 21.5777

From table G: A = 0.002583From table CS-2 Metric: B = 108.5882 MPa

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

= 4*108.5882/(3*(971.00/45.0003))

= 6709.9165 kPa


= (50 * t / Rf) * (1 - Rf / Ro)

= (50 * 48.00 / 461.5000) * (1 - 461.5000 /)= 5.2004 %


A = 0.125 / (Ro / t)

= 0.125 / (485.5000 / 45.0003)

= 0.011586

B = 120.0401 MPa

S = 128.0000 / 1.0000

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= 128.0000 MPa

ScHC = 120.0401 MPa


A = 0.125 / (Ro / t)

= 0.125 / (485.5000 / 48.0000)

= 0.012358

B = 120.1204 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScHN = 120.1204 MPa


A = 0.125 / (Ro / t)

= 0.125 / (485.5000 / 48.0000)

= 0.012358

B = 120.1204 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScCN = 120.1204 MPa


A = 0.125 / (Ro / t)

= 0.125 / (485.5000 / 45.0003)

= 0.011586

B = 120.0401 MPa

S = 128.0000 / 1.0000= 128.0000 MPa

ScCC = 120.0401 MPa


A = 0.125 / (Ro / t)

= 0.125 / (485.5000 / 45.0003)

= 0.011586

B = 120.0401 MPa

S = 128.0000 / 1.0000

= 128.0000 MPa

ScVC = 120.0401 MPa

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Saddle #1

Saddle material:A-516 Gr.

60

Saddle construction is:Centered

webSaddle allowable stress: Ss = 137.895 MPa

Saddle yield stress: Sy = 262.001 MPaSaddle distance to datum: 3,382.5 mmTangent to tangent length: L = 11,405 mm

Saddle separation: Ls = 7,000 mmVessel radius: R = 462 mm

Tangent distance left: Al = 1,022.5 mmTangent distance right: Ar = 3,382.5 mm

Saddle height: Hs = 850 mmSaddle contact angle: = 120 Wear plate thickness: tp = 10 mm

Wear plate width: Wp = 279.4 mmWear plate contact angle: w = 132

Web plate thickness: ts = 10 mm

Base plate length: E = 850 mmBase plate width: F = 200 mmBase plate thickness: tb = 11 mm

Number of stiffener ribs: n = 3Largest stiffener rib spacing: di = 407.3 mmStiffener rib thickness: tw = 10 mm

Saddle width: B = 200 mmAnchor bolt size & type: 20 mm

Anchor bolt material:Anchor bolt allowable shear: 103.421 MPa

Anchor bolt corrosion allowance: 0 mmAnchor bolts per saddle: 2Base coefficient of friction: = 0.45

Weight on left saddle: operating corr =3,859.16 kg, test new =6,077.23 kg

Weight on right saddle: operating corr =10,533.32 kg, test new =15,650.3 kgWeight of saddle pair =189.6 kg

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

LoadVessel

condition

Bending + pressure

between saddles(MPa)

Bending + pressure at

the saddle(MPa)

S1(+)

allow(+)

S1(-)

allow(-)

S2(+)

allow(+)

S2(-)

allow(-)

Weight Operat ing 55.002 128 2.375 0 54.951 128 2.347 0

Weight Test 67.421 216.9 3.54 0 67.205 216.9 3.354 0

Weight Vacuum 2.375 128 2.832 0 2.347 128 2.804 0

LoadVessel

condition

Tangentialshear (MPa) Circumferentialstress (MPa)

Stress

oversaddle(MPa)

Splitting(MPa)

S3 allowS4

(horns)allow(+/-)

S5 allow S6 allow

Weight Operat ing 3.243 102.4 -4.97 192 5.102 111.5 4.757 91.93

Weight Test 4.493 173.52 -6.601 216.9 7.026 216.9 7.068 235.801

Weight Vacuum 3.243 102.4 -4.97 192 5.102 111.5 4.757 91.93

Load Case 1: Weight ,Operating

Longitudinal stress between saddles (Weight ,Operating, left saddle loading and geometry govern)

S1 = +- 3*K1*Q*(L/12) / (*R2*t)

= 3*0.6254*37,845.47*(11,405/12) / (*438.672*47)= 2.375 MPa

Sp = P*R/(2*t)

= 11.92*415.17/(2*47)= 52.627 MPa

Maximum tensile stress S1t = S1 + Sp = 55.002 MPaMaximum compressive stress (shut down) S1c = S1 = 2.375 MPa

Tensile stress is acceptable ( 0 ###,###,###,##0.###)**

Longitudinal stress at the left saddle (Weight ,Operating)

Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3= 2*164/3 + 11,405 + 2*249.14/3

= 11,680.43 mm

w = Wt/Le = 141,142.09*10/11,680.43 = 120.84 N/cm

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Bending moment at the left saddle:

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

= 120.84/10000*(2*164*1,022.5/3 + 1,022.52/2 - (4622 - 1642)/4)

= 7,104.1 N-m

S2 = +- Mq*K1'/ (*R2*t)

= 7,104.1*1e3*9.3799/ (*438.52*47)

= 2.347 MPa

Sp = P*R/(2*t)

= 11.92*415/(2*47)= 52.604 MPa

Maximum tensile stress S2t = S2 + Sp = 54.951 MPa

Maximum compressive stress (shut down) S2c = S2 = 2.347 MPa

Tensile stress is acceptable ( 0 #)**

Tangential shear stress in the shell (right saddle, Weight ,Operating)

Qshear = Q - w*(a + 2*H/3)

= 103,296.62 - 12.08*(3,382.5 + 2*249.14/3)= 60,416.67 N

S3 = K2.2*Qshear/(R*t)= 1.1707*60,416.67/(464*47)

= 3.243 MPa

Tangential shear stress is acceptable (

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= 16.25*1 + 1*27.94= 44.19 cm2

S6 = K8*Q / Ae= 0.2035*103,296.62 / 4,418.9997

= 4.757 MPa

Stress in saddle is acceptable (

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Tangential shear stress in the shell (right saddle, Weight ,Test)

Qshear = Q - w*(a + 2*H/3)= 153,477.01 - 18.24*(3,382.5 + 2*249.14/3)= 88,743.56 N

S3 = K2.2*Qshear/(R*t)

= 1.1707*88,743.56/(462.5*50)= 4.493 MPa


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Maximum compressive stress S1c = S1 + Sp = 2.832 MPa

Tensile stress is acceptable ( 0 ###,###,###,##0.###)**

Longitudinal stress at the left saddle (Weight ,Vacuum)

Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3

= 2*164/3 + 11,405 + 2*249.14/3= 11,680.43 mm

w = Wt/Le = 141,142.09*10/11,680.43 = 120.84 N/cm

Bending moment at the left saddle:

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

= 120.84/10000*(2*164*1,022.5/3 + 1,022.52/2 - (4622 - 1642)/4)

= 7,104.1 N-m

S2 = +- Mq*K1'/ (*R2*t)

= 7,104.1*1e3*9.3799/ (*438.52*47)

= 2.347 MPa

Sp = P*R/(2*t)

= 0.1*415/(2*47)= 0.457 MPa

Maximum tensile stress (shut down) S2t = S2 = 2.347 MPaMaximum compressive stress S2c = S2 + Sp = 2.804 MPa

Tensile stress is acceptable ( 0 #)**

Tangential shear stress in the shell (right saddle, Weight ,Vacuum)

Qshear = Q - w*(a + 2*H/3)= 103,296.62 - 12.08*(3,382.5 + 2*249.14/3)

= 60,416.67 N

S3 = K2.2*Qshear/(R*t)

= 1.1707*60,416.67/(464*47)= 3.243 MPa


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Ring compression in shell over right saddle (Weight ,Vacuum)

S5 = K5*Q/((t + tp)*(ts + 1.56*Sqr(Ro*tc)))= 0.7603*103,296.62/((47 + 10)*(10 + 1.56*Sqr(487.5*57)))= 5.102 MPa

Ring compression in shell is acceptable (

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= 7.539 MPa

The primary bending + axial stress in the saddle

6201-v-01

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