Hp Flare Raiser 90 Inch Wnrf Flange

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NATCO-AL-RUSHAID MIDDLE EAST LTD

Jubail Industrial City 31961

COMPRESS Pressure Vessel Design Calculations

Item: ADSORBER VESSEL

Vessel No: 4075-VE-02-V00

Customer: PETROFACContract:

Designer: VP JAGANNAATH

Date: Sunday, January 12, 2014

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



Table of Contents

Deficiencies Summary..............................................................................................................................................1/19

Pressure Summary...................................................................................................................................................2/19

Revision History........................................................................................................................................................3/19

Settings Summary.....................................................................................................................................................4/19

Radiography Summary.............................................................................................................................................6/19

Thickness Summary.................................................................................................................................................7/19

Weight Summary.......................................................................................................................................................8/19

Hydrostatic Test........................................................................................................................................................9/19

Corroded Hydrostatic Test.....................................................................................................................................10/19

Flange #1..................................................................................................................................................................11/19



Deficiencies Summary

No deficiencies found.

1/19



Pressure Summary

Identifier

P

Design

( kPa)

T

Design

( °C)

MAWP

( kPa)

MAP

( kPa)

MAEP

( kPa)

Te

external

( °C)

MDMT

( °C)

MDMT

Exemption

Impact

Tested

Flange #1 350 240 1,675.94 2,200.71 3,689.77 240 -48 Note 1 No

Flange #1 - Flange Hub 350 240 1,050.26 1,454.93 547.4 240 -49 Note 2 No

Chamber design MDMT is 0 °CChamber rated MDMT is -48 °C @ 1,050.26 kPa

Chamber MAWP hot & corroded is 1,050.26 kPa @ 240 °C

Chamber MAP cold & new is 1,454.93 kPa @ 40 °C

Chamber MAEP is 547.4 kPa @ 240 °CVacuum rings did not govern the external pressure rating.

Notes for MDMT Rating:

Note # Exemption Details

1.Flange is impact tested to -46 °C with an additional 3 °C reduction per UCS-66(g)

UCS-66 governing thickness = 12 mm

Bolts rated MDMT per Fig UCS-66 note (c) = -48 °C

2. Material is impact tested to -46 °C with an additional 3 °C reduction per UCS-66(g) UCS-66 governing thickness = 12 mm

Design notes are available on the Settings Summary page.

2/19



Revision History

No. Date Operator Notes

0 1/15/2014 vp.jagannaath New vessel created ASME Section VIII Division 1 [COMPRESS 2014 Build 7400]

3/19



Settings Summary

COMPRESS 2014 Build 7400

Units: SI

Datum Line Location: 0.00 mm from bottom seam

Design

ASME Section VIII Division 1, 2013 Edition Metric

Design or Rating: Get Thickness from Pressure

Minimum thickness: 1.5 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: 300 mmJuncture calculations for α > 30 only: Yes

Preheat P-No 1 Materials > 1.25" and <= 1.50" thick: No

UG-37(a) shell tr calculation considers longitudinal stress: No

Pipe under-tolerance is not applied to pipe cap thicknesses.Butt welds are tapered per Figure UCS-66.3(a).

Hydro/Pneumatic Test

Shop Hydrotest Pressure:1.3 times vesselMAWP

Test liquid specific gravity: 1.00

Field Hydrotest Pressure:1.3 times vessel

MAWP

Wind load present @ field: 33% of design

Maximum stress during test: 90% of yield

Required Marking - UG-116

UG-116(e) Radiography: None

UG-116(f) Postweld heat treatment: None

Code Cases\Interpretations

Use Code Case 2547: No

Use Code Case 2695: No

Apply interpretation VIII-1-83-66: Yes



No UCS-66.1 MDMT reduction: Yes

No UCS-68(c) MDMT reduction: Yes

Disallow UG-20(f) exemptions: Yes

4/19



UG-22 Loadings

UG-22(a) Internal or External Design Pressure : No

UG-22(b) Weight of the vessel and normal contents under operating or test conditions: No

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

UG-22(d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: No

UG-22(f) Wind reactions: No

UG-22(f) Seismic reactions: No

UG-22(j) Test pressure and coincident static head acting during the test: YesNote: UG-22(b),(c) and (f) loads only considered when supports are present.

5/19



Radiography Summary

Radiography for Chamber bounded by Top of vessel and Top of vessel

ComponentLongitudinal Seam Top Circumferential Seam Bottom Circumferential Seam

MarkCategory

(Fig UW-3)Radiography / Joint Type

Category


Category


Chamber bounded by Top of vessel and Top of vessel - UG-116(e) Radiography: None

6/19



Thickness Summary

Component

IdentifierMaterial Diameter

(mm)

Length

(mm)

Nominal t

(mm)

Design t

(mm)

Total Corrosion

(mm)

Joint

ELoad

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

7/19



Weight Summary

Component

Weight ( kg) Contributed by Vessel Elements

Surface Aream2

Metal

New*

Metal

Corroded*Insulation

InsulationSupports

LiningPiping

+ Liquid

Operating

LiquidTest Liquid

New Corroded New Corroded

TOTAL: 0 0 0 0 0 0 0 0 0 0 0

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

Component

Weight ( kg) Contributed by Attachments SurfaceArea

m2Body FlangesNozzles &Flanges

PackedBeds

Ladders &Platforms

TraysTray

SupportsRings &

ClipsVerticalLoads

New Corroded New Corroded

TOTAL: 2,749.7 2,699.8 0 0 0 0 0 0 0 0 2.33

Vessel operating weight, Corroded: 2,700 kg

Vessel operating weight, New: 2,750 kg

Vessel empty weight, Corroded: 2,700 kg

Vessel empty weight, New: 2,750 kg

Vessel test weight, New: 2,750 kg

Vessel test weight, Corroded: 2,700 kgVessel surface area: 2.33 m2

Vessel center of gravity location - from datum - lift condition

Vessel Lift Weight, New: 2,750 kg

Center of Gravity: 140 mm

Vessel Capacity

Vessel Capacity** (New): 0 liters

Vessel Capacity** (Corroded): 0 liters

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

8/19



Hydrostatic Test

Shop test pressure determination for Chamber bounded by Top of vessel and Top of vessel based on MAWPper UG-99(b)

Shop hydrostatic test gauge pressure is 1,385.4 kPa at 40 °C (the chamber MAWP = 1,050.26 kPa)

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

IdentifierLocal testpressure

kPa

Test liquidstatic head

kPa

UG-99(b)stressratio

UG-99(b)pressure

factor

Stressduring test

MPa

Allowabletest stress

MPa

Stressexcessive?

Flange #1 - Flange Hub (1) 1,407.57 22.16 1.0147 1.30 133.366 223.2 No

Flange #1 1,407.57 22.16 1.0147 1.30 176.528 334.8 No

Notes:

(1) Flange #1 - Flange Hub limits the UG-99(b) stress ratio.(2) 1.5*0.9*Sy used as the basis for the maximum local primary membrane stress at the nozzle intersection PL.

(3) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-most

flange.

The test temperature of 40 °C is warmer than the minimum recommended temperature of -31 °C so the brittlefracture provision of UG-99(h) has been met.

Field test pressure determination for Chamber bounded by Top of vessel and Top of vessel based on MAWPper UG-99(b)

Field hydrostatic test gauge pressure is 1,385.4 kPa at 40 °C (the chamber MAWP = 1,050.26 kPa)

The field test is performed with the vessel in the vertical position.

Identifier Local testpressurekPa

Test liquidstatic headkPa

UG-99(b)stressratio

UG-99(b)pressurefactor

Stressduring testMPa

Allowabletest stressMPa

Stressexcessive?

Flange #1 - Flange Hub (1) 1,388.15 2.74 1.0147 1.30 131.526 223.2 No

Flange #1 1,388.15 2.74 1.0147 1.30 174.092 334.8 No

Notes:(1) Flange #1 - Flange Hub limits the UG-99(b) stress ratio.

(2) 1.5*0.9*Sy used as the basis for the maximum local primary membrane stress at the nozzle intersection PL.

The test temperature of 40 °C is warmer than the minimum recommended temperature of -31 °C so the brittlefracture provision of UG-99(h) has been met.

9/19



Corroded Hydrostatic Test

The shop test condition has not been investigated for the Chamber bounded by Top of vessel and Top of vessel.

Field test pressure determination for Chamber bounded by Top of vessel and Top of vessel based on designP per UG-99(b)

Field hydrostatic test gauge pressure is 461.69 kPa at 40 °C (the chamber design P = 350 kPa)

The field test is performed with the vessel in the vertical position.

IdentifierLocal testpressure

kPa

Test liquidstatic head

kPa

UG-99(b)stressratio

UG-99(b)pressure

factor

Stressduring test

MPa

Allowabletest stress

MPa

Stressexcessive?

Flange #1 - Flange Hub (1) 464.43 2.74 1.0147 1.30 60.094 223.2 No

Flange #1 464.43 2.74 1.0147 1.30 57.235 334.8 No

Notes:(1) Flange #1 - Flange Hub limits the UG-99(b) stress ratio.

(2) 1.5*0.9*Sy used as the basis for the maximum local primary membrane stress at the nozzle intersection PL.

10/19



Flange #1

ASME VIII-1, 2013 Edition Metric, Appendix 2 Flange Calculations

Flange type: Weld neck integralFlange material specification: SA-350 LF2 Cl 1 (II-D Metric p. 18, ln. 37)

Bolt material specification:SA-193 B7 Bolt <= 64 (II-D Metric p. 352, ln.31)

Bolt Description: 48 mm Metric boltInternal design pressure, P: 350 kPa @ 240 °CRequired flange thickness, tr: 219.46 mm

Maximum allowable working pressure,MAWP:

1,675.94 kPa @ 240 °C

Maximum allowable pressure, MAP: 2,200.71 kPa @ 40 °CExternal design pressure, Pe 101.33 kPa @ 240 °C

Maximum allowable external pressure,MAEP:

3,689.77 kPa @ 240 °C

Corrosion allowance: Bore = 3.2 mm Flange = 0 mm

Bolt corrosion (root), Cbolt: 0 mmDesign MDMT: 0 °C No impact test performed

Rated MDMT: -48 °C Flange material is normalized

Material is not produced tofine grain practicePWHT is not performed

Estimated weight: New = 2,749.72 kg corroded = 2,699.74 kg

Flange dimensions, new

flange OD A = 2,650 mm

bolt circle C = 2,536 mm

raised face OD Rf = 2,446 mm

gasket OD = 2,488 mm

gasket ID = 2,262 mm

flange ID B = 2,262 mm

facing height trf = 1.52 mm

thickness t = 230 mm

bolting = 88- 48 mm dia

hub thickness g1 = 20 mm

hub thickness g0 = 12 mm

hub length h = 50 mm

length e = 280 mm

gasket factor m = 3

seating stress y = 68.948 MPaGasket thickness T = 4.45 mm

gasket descriptionFlexitallic Spiral

Wound CG 316 S.S.Note: this flange is calculated as an integral type.

Determination of Flange MDMT

11/19



Flange is impact tested to -46 °C with an additional 3 °C reduction per UCS-66(g)UCS-66 governing thickness = 12 mm

Bolts rated MDMT per Fig UCS-66 note (c) = -48 °C

The rated flange MDMT is -48 °C

Flange calculations for Internal Pressure + Weight Only

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

Gasket width N = 92 mm

b0 = N/2 = 46 mm

Effective gasket seating width, b = 2.5*b01/2 = 16.96 mm

G = OD of contact face - 2*b = 2,446 - 2*16.96 = 2,412.09 mm

hG = (C - G)/2 = (2,536 - 2,412.09)/2 = 61.96 mm

hD = R + g1 /2 = 117 + 16.8/2 = 125.4 mm

hT = (R + g1 + hG)/2 = (117 + 16.8 + 61.96)/2 = 97.88 mm

Hp = 2*b*3.14*G*m*P= 2*16.96*3.14*2,412.09*3*0.35

= 269,706.74 N

H = 0.785*G2*P= 0.785*2,412.092*0.35= 1,598,539.15 N

HD = 0.785*B2*P

= 0.785*2,268.42*0.35

= 1,413,765.37 N

HT = H - HD

= 1,598,539.15 - 1,413,765.37

= 184,773.78 N

Wm1 = H + Hp

= 1,598,539.15 + 269,706.74

= 1,868,245.89 N

Wm2 = 3.14*b*G*y

= 3.14*16.96*2,412.09*68.9476= 8,855,059.28 N

Required bolt area, Am = greater of Am1, Am2 = 514.829 cm2

Am1 = Wm1 /Sb = 1,868,245.89/(100*172) = 108.6189 cm2

Am2 = Wm2 /Sa = 8,855,059.28/(100*172) = 514.829 cm2

Total area for 88- 48 mm dia bolts, corroded, Ab = 1,253.4581 cm2

W = (Am + Ab)*Sa /2

12/19



= (51,482.9 + 125,345.8)*172/2= 15,207,270.59 N

MD = HD*hD = 1,413,765.37*0.1254 = 177,285.8 N-mMT = HT*hT = 184,773.78*0.0979 = 18,085.3 N-m

HG = Wm1 - H = 1,868,245.89 - 1,598,539.15 = 269,706.74 N

MG = HG*hG = 269,706.74*0.062 = 16,710.2 N-m

Mo = MD + MT + MG = 177,285.8 + 18,085.3 + 16,710.2 = 212,081.4 N-m

Mg = W*hG = 152.07E+05*0.062 = 942,197.7 N-m

13/19



Hub and Flange Factors

g0 = min(g0, tn) = min(8.8, 8.8) = 8.8

h0 = (B*g0)1/2 = (2,268.4*8.8)1/2 = 141.28 mm

From FIG. 2-7.1, where K = A/B = 2,650/2,268.4 = 1.1682

T = 1.8516 Z = 6.4833 Y = 12.5598 U = 13.802

h/h0 = 0.3539 g1 /g0 = 1.9091

F = 0.8597 V = 0.2872 e = F/h0 = 0.0609

d = (U/V)*h0*g02= (13.802/0.2872)*14.1283*0.882

= 525.7725 cm3

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

f = 1.6481

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

= (23*0.0609 + 1)/1.8516 + 233

/525.7725= 24.4371

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

= 1e3*1.6481*212,081.4/(24.4371*16.82*2,268.4)

= 22.342 MPa

SR = (1.33*t*e + 1)*Mo /(L*t2*B)= (1.33*230*0.0061 + 1)*1e3*212,081.4/(24.4371*2302*2,268.4)

= 0.207 MPa

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

= 1e3*12.5598*212,081.4/(2302*2,268.4) - 6.4833*0.207

= 20.856 MPa

Allowable stress Sfo = 136 MPa

Allowable stress Sno = 136 MPa

ST does not exceed Sfo

SH does not exceed Min[ 1.5*Sfo, 2.5*Sno ] = 204 MPaSR does not exceed Sfo

0.5(SH + SR) = 11.274 MPa does not exceed Sfo

0.5(SH + ST) = 21.599 MPa does not exceed Sfo

Flange rigidity at operating per VIII-1 Appendix 2-14

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

= 1e3*52.14*0.2872*212,081.4/(24.4371*189.6E+03*8.82*0.3*141.28)

= 0.2088

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

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

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

= 1e3*1.6481*942,197.7/(24.4371*16.82*2,268.4)

14/19



= 99.255 MPa

SR = (1.33*t*e + 1)*Mg /(L*t2*B)= (1.33*230*0.0061 + 1)*1e3*942,197.7/(24.4371*2302*2,268.4)= 0.919 MPa

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

= 12.5598*1e3*942,197.7/(2302*2,268.4) - 6.4833*0.919= 92.656 MPa

Allowable stress Sfa = 138 MPaAllowable stress Sna = 138 MPa

ST does not exceed Sfa

SH does not exceed Min[ 1.5*Sfa, 2.5*Sna ] = 207 MPaSR does not exceed Sfa

0.5(SH + SR) = 50.087 MPa does not exceed Sfa

0.5(SH + ST) = 95.956 MPa does not exceed Sfa

Flange rigidity at gasket seating per VIII-1 Appendix 2-14

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

= 1e3*52.14*0.2872*942,197.7/(24.4371*201.2E+03*8.82*0.3*141.28)= 0.8743


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

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

Gasket width N = 92 mm

b0 = N/2 = 46 mm

Effective gasket seating width, b = 2.5*b01/2 = 16.96 mm

G = OD of contact face - 2*b = 2,446 - 2*16.96 = 2,412.09 mm

hG = (C - G)/2 = (2,536 - 2,412.09)/2 = 61.96 mm

hD = R + g1 /2 = 117 + 16.8/2 = 125.4 mm

hT = (R + g1 + hG)/2 = (117 + 16.8 + 61.96)/2 = 97.88 mm

Hp = 2*b*3.14*G*m*P= 2*16.96*3.14*2,412.09*3*0.1013

= 78,080.24 N

H = 0.785*G2*P= 0.785*2,412.092*0.1013= 462,777.89 N

HD = 0.785*B2*P

= 0.785*2,268.42*0.1013= 409,285.79 N

15/19



HT = H - HD

= 462,777.89 - 409,285.79

= 53,492.1 N

Wm1 = H + Hp

= 462,777.89 + 78,080.24= 540,858.13 N

Wm2 = 3.14*b*G*y

= 3.14*16.96*2,412.09*68.9476= 8,855,059.28 N

Required bolt area, Am = greater of Am1, Am2 = 514.829 cm2

Am1 = 0.785*G2*(Pm - Pr)/Sb = 0/(100*172) = 0 cm2

Am2 = Wm2 /Sa = 8,855,059.28/(100*172) = 514.829 cm2

Total area for 88- 48 mm dia bolts, corroded, Ab = 1,253.4581 cm2

W = (Am2 + Ab)*Sa /2

= (51,482.9 + 125,345.8)*172/2

= 15,207,270.59 N

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

= 409,285.79*(0.1254 - 0.062) + 53,492.1*(0.0979 - 0.062)= 27,887.7 N-m

Mg = W*hG = 152.07E+05*0.062 = 942,197.7 N-m

16/19



Hub and Flange Factors

g0 = min(g0, tn) = min(8.8, 8.8) = 8.8

h0 = (B*g0)1/2 = (2,268.4*8.8)1/2 = 141.28 mm

From FIG. 2-7.1, where K = A/B = 2,650/2,268.4 = 1.1682

T = 1.8516 Z = 6.4833 Y = 12.5598 U = 13.802

h/h0 = 0.3539 g1 /g0 = 1.9091

F = 0.8597 V = 0.2872 e = F/h0 = 0.0609

d = (U/V)*h0*g02= (13.802/0.2872)*14.1283*0.882

= 525.7725 cm3

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

f = 1.6481

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

= (23*0.0609 + 1)/1.8516 + 233

/525.7725= 24.4371

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

= 1e3*1.6481*27,887.7/(24.4371*16.82*2,268.4)

= 2.938 MPa

SR = (1.33*t*e + 1)*Mo /(L*t2*B)= (1.33*230*0.0061 + 1)*1e3*27,887.7/(24.4371*2302*2,268.4)

= 0.027 MPa

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

= 1e3*12.5598*27,887.7/(2302*2,268.4) - 6.4833*0.027

= 2.742 MPa

Allowable stress Sfo = 136 MPa

Allowable stress Sno = 136 MPa

ST does not exceed Sfo

SH does not exceed Min[ 1.5*Sfo, 2.5*Sno ] = 204 MPaSR does not exceed Sfo

0.5(SH + SR) = 1.483 MPa does not exceed Sfo

0.5(SH + ST) = 2.84 MPa does not exceed Sfo

Flange rigidity at operating per VIII-1 Appendix 2-14

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

= 1e3*52.14*0.2872*27,887.7/(24.4371*189.6E+03*8.82*0.3*141.28)

= 0.0275


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

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

= 1e3*1.6481*942,197.7/(24.4371*16.82*2,268.4)

17/19



= 99.255 MPa

SR = (1.33*t*e + 1)*Mg /(L*t2*B)= (1.33*230*0.0061 + 1)*1e3*942,197.7/(24.4371*2302*2,268.4)= 0.919 MPa

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

= 12.5598*1e3*942,197.7/(2302*2,268.4) - 6.4833*0.919= 92.656 MPa

Allowable stress Sfa = 138 MPaAllowable stress Sna = 138 MPa

ST does not exceed Sfa

SH does not exceed Min[ 1.5*Sfa, 2.5*Sna ] = 207 MPaSR does not exceed Sfa

0.5(SH + SR) = 50.087 MPa does not exceed Sfa

0.5(SH + ST) = 95.956 MPa does not exceed Sfa

Flange rigidity at gasket seating per VIII-1 Appendix 2-14

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

= 1e3*52.14*0.2872*942,197.7/(24.4371*201.2E+03*8.82*0.3*141.28)= 0.8743


Flange #1 - Flange hub

ASME Section VIII Division 1, 2013 Edition Metric

Component: Flange hub

Material specification: SA-350 LF2 Cl 1 (II-D Metric p. 18, ln. 37)Material is impact tested to -46 °C with an additional 3 °C reduction per UCS-66(g)UCS-66 governing thickness = 12 mm

Internal design pressure: P = 350 kPa @ 240 °C

External design pressure: Pe = 101.33 kPa @ 240 °C

Static liquid head:

Not Considered

Corrosion allowance Inner C = 3.2 mm Outer C = 0 mm

Design MDMT = 0 °C No impact test performed

Rated MDMT = -49 °C Material is normalized

Material is not produced to Fine Grain PracticePWHT is not performed

Radiography: Longitudinal joint - Seamless No RT

Top circumferential joint - Full UW-11(a) Type 1Bottom circumferential joint - N/A

Estimated weight New = 33.4 kg corr = 24.6 kg

Capacity New = 200.93 liters corr = 202.07 liters

18/19



ID = 2,262 mmLength

Lc

= 50 mm

t = 12 mm

Design thickness, (at 240 °C) UG-27(c)(1)

t = P*R / (S*E - 0.60*P) + Corrosion= 350*1,134.2 / (136,000*1.00 - 0.60*350) + 3.2

= 6.12 mm

Maximum allowable working pressure, (at 240 °C) UG-27(c)(1)

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

= 136,000*1.00*8.8 / (1,134.2 + 0.60*8.8) - 0= 1,050.26 kPa

Maximum allowable pressure, (at 40 °C) UG-27(c)(1)

P = S*E*t / (R + 0.60*t)= 138,000*1.00*12 / (1,131 + 0.60*12)

= 1,454.93 kPa

External Pressure, (Corroded & at 240 °C) UG-28(c)

L / Do = 50 / 2,286 = 0.0500Do / t = 2,286 / 1.25 = 1824.1468

Experimental basin formula

Pa = [2.42*E / (1 - µ2)0.75]*[(t / Do)2.50 / (L / Do - 0.45*(t / Do)

0.50)] / 3

= [2.42*188545445.24 / (1 - 0.302)0.75]*[(1.25 / 2,286)2.50 / (50 / 2,286 - 0.45*(1.25 / 2,286)0.50)] / 3= 101.32 kPa

Design thickness for external pressure Pa = 101.32 kPa

ta = t + Corrosion = 1.25 + 3.2 = 4.45mm

Maximum Allowable External Pressure, (Corroded & at 240 °C) UG-28(c)

L / Do = 50 / 2,286 = 0.0500Do / t = 2,286 / 8.8 = 259.7845From table G: A = 0.012182

From table CS-2Metric:

B = 106.6549 MPa

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

= 4*106,654.88 / (3*(2,286 / 8.8))

= 547.4 kPa

Hp Flare Raiser 90 Inch Wnrf Flange

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