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.
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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
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Deficiencies Summary
No deficiencies found.
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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.
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Revision History
No. Date Operator Notes
0 1/15/2014 vp.jagannaath New vessel created ASME Section VIII Division 1 [COMPRESS 2014 Build 7400]
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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
Apply interpretation VIII-1-86-175: Yes
Apply interpretation VIII-1-01-37: Yes
No UCS-66.1 MDMT reduction: Yes
No UCS-68(c) MDMT reduction: Yes
Disallow UG-20(f) exemptions: Yes
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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.
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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
(Fig UW-3)Radiography / Joint Type
Category
(Fig UW-3)Radiography / Joint Type
Chamber bounded by Top of vessel and Top of vessel - UG-116(e) Radiography: None
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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
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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.
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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.
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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.
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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
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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
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= (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
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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)
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= 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
The flange rigidity index J does not exceed 1; satisfactory.
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
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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
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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
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)
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= 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
The flange rigidity index J does not exceed 1; satisfactory.
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
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8/10/2019 Hp Flare Raiser 90 Inch Wnrf Flange
http://slidepdf.com/reader/full/hp-flare-raiser-90-inch-wnrf-flange 21/21
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