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RF、RJ法兰计算GB150和ASME-V2.0

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平面密封法兰计算书 项目号 ITEM NO.
Flange calculation 文件号 DOC. NO.
遵循规范： GB/T 150-2011 法兰编号 N1
设计条件 简              图
主体 计算压力 Pc -0.065 Mpa 1
设计温度 t 670 °C
筒体 材料 S30409
设计温度许用应力
 [σ]nt 34 Mpa
法兰 材料 S30409II
常温许用应力 [σ]f 137 Mpa
设计温度许用应力
 [σ]ft 34 mm
常温弹性模量 E0 195000 Mpa
设计温度弹性模量
 Et 143000 Mpa
螺栓 材料 S30409
常温许用应力 [σ]b 137 Mpa
设计温度许用应力
 [σ]bt 36 Mpa
公称直径 dB 27 mm
根径 d根 23.751 mm
数量 n 16 个 分程隔板槽面积Ar= 0 mm2
垫片 垫片系数 m 3 结
构
尺
寸
（mm）		 法兰假定厚度 δf 46.1
比压力 y        69 Mpa Di 194.0  δ0 11.0 
垫片宽度 N  15.10  mm D0 445.0  δ1 31.5 
基本密封宽度 b0  7.55  mm Db 387.4  h 70.0 
有效密封宽度 b 6.95  mm D外 317.5  Le 28.8 
压紧力作用中心圆DG 303.60  mm D内 287.3  LA 65.2 
b0≤6.4mm     b= b0 b0≤6.4mm   DG= ( D外+D内 )/2
b0 > 6.4mm     b=2.53√b0 b0 > 6.4mm   DG= D外 - 2b
1. 螺栓受力计算
流体压力引起的总轴向力 F=πDG2Pc/4 = 4.705E+03 N
操作状态下需要的最小垫片压紧力 Fp=2Pc（πbDGm+0.5Arm） = 2.586E+03 N
操作状态下需要的最小螺栓载荷 Wp=F+Fp = 7.291E+03 N
预紧状态下需要的最小螺栓载荷 Wa=πbDGy+0.5Ary = 457498.5561 N
操作状态下需要的最小螺栓总截面积 Ap=Wp/[σ]bt = 0.0  mm2
预紧状态下需要的最小螺栓总截面积 Aa=Wa/[σ]b = 3339.4  mm2
所需螺栓总截面积 Am取Ap和Aa中大者， Am = 3339.4  mm2
实际螺栓总截面积 Ab=nπd根2/4 = 7088.81534 mm2
判断依据：Ab≥Am, 螺栓面积 合格
操作状态螺栓设计载荷W1 W1=Wp = 7291.3  N
预紧状态螺栓设计载荷W2 W2=0.5(Am+Ab)[σ]b = 714333.1  N
2. 法兰力矩计算
操作 FD=πDi2Pc/4= 1.921E+03 N LD=LA+0.5δ1= 80.95 mm
FG=FP= 2.586E+03 N LG=0.5(Db-DG)= 41.9  mm
FT=F-FD= 2.784E+03 N LT=0.5(LA+δ1+LG)= 69.3  mm
MD=FDLD= 1.555E+05 Nmm 外压:Mp=FD(LD-LG)+FT(LT-LG )
MG=FGLG= 1.084E+05 Nmm 外压: = 1.513E+05 Nmm
MT=FTLT= 1.929E+05 Nmm 内压:Mp=MD+MG+MT = 4.568E+05 Nmm
Mp (注：按照外压的值计算） = 1.513E+05 Nmm
预紧 Ma=W2LG = 29931806.48 Nmm
Ma[σ]tf/[σ]f = 7428331.536 Nmm
计算力矩 Mo= Mp 与Ma[σ]ft/[σ]f中大者，Mo = 7.428E+06 Nmm
3. 螺栓间距校核
实际间距 L=πDb/n = 76.1  mm
最小间距(查GB/T150.3表7-3) Lmin = 62.0  mm
最大间距 Lmax = 133.0  mm
判断依据： 当Lmin<=L<=Lmax，螺栓间距合格。 合格
4. 形状常数确定
h0=(Diδ0)0.5= 46.20  h/h0= = 1.52 
K=D0/Di= 2.29  δ1/δ0= = 2.86 
由K查表7-9 T= 1.40  查图7-3 F1 = 0.63 
Z= 1.47  查图7-4 V1 = 0.06 
Y= 2.48  查图7-7 f = 1.00 
U= 2.73  e=F1/H0 = 0.01 
d1=Uh0δ02/VI= 2.36E+05 ψ=δf e+1= = 1.63 
β=4δf e/3+1= 1.83  γ=ψ/T= = 1.16 
η=δf3/d1= 0.41  λ=γ+η= = 1.57 
5. 法兰应力校核
当Di<20δ1,且f≤1,Dil=Di+δ1 = 225.5  mm
应力 计算值(MPa)      许用值(MPa) 结论
轴向应力 σH=fM0/(λδ12Dil)= 21.11  1.5[σ]ft= 51 合格
2.5[σ]nt= 85 合格
径向应力 σR=βM0/(λδf2Di)= 21.02  [σ]ft= 34 合格
切向应力 σT=YM0/(δf2Di)-ZσR= 13.86  [σ]ft= 34 合格
组合应力 （σH+σR）/2= 21.06  [σ]ft= 34 合格
（σH+σT）/2= 17.49  [σ]ft= 34 合格
6. 刚度校核
刚度系数 K1= 0.3 Mo由预紧控制时，E用E0代替 E=E0= 195000.0  Mpa
刚度指数   J=52.14V1Mo/λEδ02K1Ho= = 0.049  合格
注：
1. 所有尺寸均不含腐蚀裕量。

环槽密封法兰计算书 项目号 ITEM NO.
Flange calculation 文件号 DOC. NO.
遵循规范： GB/T 150-2011 法兰编号 N1
设计条件 简              图
主体 计算压力 Pc 18.17 Mpa 1
设计温度 t 85 °C
筒体 材料 20IV
设计温度许用应力
 [σ]nt 123 Mpa
法兰 材料 10IV
常温许用应力 [σ]f 123 Mpa
设计温度许用应力
 [σ]ft 119.8 mm
常温弹性模量 E0 195000 Mpa
设计温度弹性模量
 Et 143000 Mpa
螺栓 材料 35CrMoA ω
常温许用应力 [σ]b 254 Mpa
设计温度许用应力
 [σ]bt 233.7 Mpa
公称直径 dB 48 mm
根径 d根 45 mm
数量 n 16 个 分程隔板槽面积Ar= 0 mm2
垫片 垫片系数 m 6.5 结
构
尺
寸
（mm）		 法兰假定厚度 δf 140
比压力 y        179.3 Mpa Di 306.0  δ0 24.0 
垫片宽度 ω 22.20  mm D0 675.0  δ1 72.5 
基本密封宽度 b0  2.78  mm Db 571.5  h 120.0 
有效密封宽度 b 2.78  mm D外 403.2  Le 51.8 
压紧力作用中心圆DG 381.00  mm D内 358.8  LA 60.3 
b0≤6.4mm     b= b0 b0≤6.4mm   DG= ( D外+D内 )/2
b0 > 6.4mm     b=2.53√b0 b0 > 6.4mm   DG= D外 - 2b
1. 螺栓受力计算
流体压力引起的总轴向力 F=πDG2Pc/4 = 2.072E+06 N
操作状态下需要的最小垫片压紧力 Fp=2Pc（πbDGm+0.5Arm） = 7.846E+05 N
操作状态下需要的最小螺栓载荷 Wp=F+Fp = 2.856E+06 N
预紧状态下需要的最小螺栓载荷 Wa=πbDGy+0.5Ary = 595549.8579 N
操作状态下需要的最小螺栓总截面积 Ap=Wp/[σ]bt = 12221.3  mm2
预紧状态下需要的最小螺栓总截面积 Aa=Wa/[σ]b = 2344.7  mm2
所需螺栓总截面积 Am取Ap和Aa中大者， Am = 12221.3  mm2
实际螺栓总截面积 Ab=nπd根2/4 = 25446.90049 mm2
判断依据：Ab≥Am, 螺栓面积 合格
操作状态螺栓设计载荷W1 W1=Wp = 2856124.8  N
预紧状态螺栓设计载荷W2 W2=0.5(Am+Ab)[σ]b = 4783865.3  N
2. 法兰力矩计算
操作 FD=πDi2Pc/4= 1.336E+06 N LD=LA+0.5δ1= 96.5 mm
FG=FP= 7.846E+05 N LG=0.5(Db-DG)= 95.3  mm
FT=F-FD= 7.353E+05 N LT=0.5(LA+δ1+LG)= 114.0  mm
MD=FDLD= 1.289E+08 Nmm 外压:Mp=FD(LD-LG)+FT(LT-LG )
MG=FGLG= 7.473E+07 Nmm 外压: = 1.546E+07 Nmm
MT=FTLT= 8.382E+07 Nmm 内压:Mp=MD+MG+MT = 2.875E+08 Nmm
Mp （注：按照内压的值计算) = 2.875E+08 Nmm
预紧 Ma=W2LG = 455663167.8 Nmm
Ma[σ]tf/[σ]f = 443808516.3 Nmm
计算力矩 Mo= Mp 与Ma[σ]ft/[σ]f中大者，Mo = 4.438E+08 Nmm
3. 螺栓间距校核
实际间距 L=πDb/n = 112.2  mm
最小间距(查GB/T150.3表7-3) Lmin = 102.0  mm
最大间距 Lmax = 216.0  mm
判断依据： 当Lmin<=L<=Lmax，螺栓间距合格。 合格
4. 形状常数确定
h0=(Diδ0)0.5= 85.70  h/h0= = 1.40 
K=D0/Di= 2.21  δ1/δ0= = 3.02 
由K查表7-9 T= 1.43  查图7-3 F1 = 0.63 
Z= 1.52  查图7-4 V1 = 0.06 
Y= 2.60  查图7-7 f = 1.00 
U= 2.86  e=F1/H0 = 0.01 
d1=Uh0δ02/VI= 2.30E+06 ψ=δf e+1= = 2.03 
β=4δf e/3+1= 2.37  γ=ψ/T= = 1.42 
η=δf3/d1= 1.20  λ=γ+η= = 2.61 
5. 法兰应力校核
当Di<20δ1,且f≤1,Dil=Di+δ1 = 378.5  mm
应力 计算值(MPa)      许用值(MPa) 结论
轴向应力 σH=fM0/(λδ12Dil)= 85.42  1.5[σ]ft= 179.7 合格
2.5[σ]nt= 307.5 合格
径向应力 σR=βM0/(λδf2Di)= 67.22  [σ]ft= 119.8 合格
切向应力 σT=YM0/(δf2Di)-ZσR= 90.71  [σ]ft= 119.8 合格
组合应力 （σH+σR）/2= 76.32  [σ]ft= 119.8 合格
（σH+σT）/2= 88.07  [σ]ft= 119.8 合格
6. 刚度校核
刚度系数 K1= 0.3 Mo由预紧控制时，E用E0代替 E=E0= 195000.0  Mpa
刚度指数   J=52.14V1Mo/λEδ02K1Ho= = 0.189  合格
注：
1. 所有尺寸均不含腐蚀裕量。

平面密封法兰计算书 项目号 ITEM NO.
Flange calculation 文件号 DOC. NO. 1
As Per ASME VIII I-2021 Mandatory Appendix 2 FLANGE NAME N1
DESIGN DATA FIG
MAIN Design pressure P 1.94 Mpa 1
Design Temperature t 250 °C
SHELL Material SA-516 70
Allowable stress @T0 Snatm 137.9 Mpa
Allowable stress @T1 Sno 137.9 Mpa 法兰几何尺寸协调性校核
FLANGE Material SA-105 限制值 实际值 判断
Allowable stress @T0 Sfatm 137.9 Mpa 螺栓直径 2 1/4
Allowable stress @T1 Sfo 135.64 mm 根径 53.03 
Elastictiy Modules @T0
 Eatm 202713 Mpa B应大于 120.65  153.0  合格
Elastictiy Modules @T1
 Eop 188980 Mpa Rh应大于 69.85  75 合格
BOLT Material SA-193 B7 E应大于 57.15  67 合格
Allowable stress @T0 Sa 172.38 Mpa h应大于 91.95  110.0  合格
Allowable stress @T1 Sb 172.38 Mpa h应大于1.5g0 30 110 合格
Nominal Bolt diameter a 2 1/4 inch
Root diameter dr 53.03  mm All dimensions are free of corrosion.
Number n 40 Partition Area Ar= 0 mm2
GASKET Gasket factor m 3 DIMENSIONS
（mm）		 B 1698.7  t 128
Seating load y 68.95 Mpa A 2084.0  go 20.0 
seating width N  60.00  mm C 1950.0  g1 50.7 
Basic seating width b0  30.00  mm Dout 1860.0  h 110.0 
Effective seating width b 13.86  mm Din 1740.0  R 75
Diameterof load reaction G 1832.29  mm
b0≤6.4mm     b= b0; b0 > 6.4mm     b=2.53√b0 b0≤6.4mm  G= ( Dout+Din )/2; b0 > 6.4mm   G= Dout- 2b
1. The bolt area check
Total hydrostatic end force H=πG2P/4 = 5.115E+06 N
Total joint‐contact surface compression load Hp=2P（πbGm+0.5Arm） = 9.285E+05 N
Min. required Operating Bolt Load Wm1=H+Hp = 6.044E+06 N
Min. required Gasket Seating Bolt Load Wm2=πbGy+0.5Ary = 5499945.355 N
Required Bolt Area at operating condition Ap=Wm1/Sb = 35061.3  mm2
Required Bolt Area at seating condition Aa=Wm2/Sa = 31905.9  mm2
Required Bolt Area Am=max(Ap,Aa) = 35061.3  mm2
Actual  bolt area Ab=nπdr2/4 = 88335.3072 mm2
Ab>=Am, the bolt area is OK!
Flange Design Bolt Load, Gasket Seating W W=0.5(Am+Ab)Sa = 10635554.2  N
2. The bolting spacing check
Actual  bolt distance Bs=Gsin(π/n) = 153.0  mm
Min. bolt spacing(According to TEMA) Bmin = 120.7  mm  
For vessels in lethal service, Max. bolt spacing Bsmax=2a+6t/(m+0.5) = 333.7  mm
Bolt pitch correction factor Bsc=max(sqrt(Bs/(2a+t)) , 1) = 1.0 
Bmin <=Bs   The space is OK! Bs  <= Bsmax The space is OK!
3. The flange load calculation
Operating  HD=πB2P/4= 4.397E+06 N hD=R+0.5g1= 100.325 mm
HG=HP=Wm1-H= 9.285E+05 N hG=0.5(C-G)= 58.9  mm
HT=H-HD= 7.187E+05 N hT=0.5(R+g1+hG)= 92.3  mm
MD=HDhDBSC= 4.411E+08 Nmm External pressure: Mop=HD(hD-hG)+HT(hT-hG )
MG=HGhGBSC= 5.465E+07 Nmm External pressure: = 2.063E+08 Nmm
MT=HThTBSC= 6.630E+07 Nmm Internal:Mop=MD+MG+MT = 5.620E+08 Nmm
Mop （Note：According to internal pressure) = 5.620E+08 Nmm
Total moment for gasket Seating,   Matm=WhGBSC = 625980864.9 Nmm
4. Factor calculation
h0=(Bgo)0.5= 184.32  h/h0= = 0.60 
K=A/B= 1.227  g1/g0= = 2.53 
Factor from Figure 2-7.1 T= 1.828  FIG 2-7.2 F = 0.791 
Z= 4.960  FIG 2-7.3 V = 0.159 
Y= 9.614  FIG 2-7.6 f = 1.567 
U= 10.566  e=F/h0 = 0.004 
d=Uh0g02/V= 4.915E+06 L=(t e+1)/T+t3/d= = 1.274 
5. Summary of stresses
When B≥20g1，B1=B = 1698.7  mm
Operating Actual (MPa) Operating allowed stress(MPa) Result
Longitudinal hub stress SH=fMop/(Lg12B1)= 158.63  1.5Sfo= 203.46 Safe
2.5Sno= 344.75 Safe
Radial fla-
nge stress		 SR=(1.33te+1)Mop/(Lt2B)= 27.46  Sfo= 135.64 Safe
Tangential f
lange stress		 ST=YMop/(t2B)-ZSR= 57.97  Sfo= 135.64 Safe
Combined stress （SH+SR）/2= 93.04  Sfo= 135.64 Safe
（SH+ST）/2= 108.30  Sfo= 135.64 Safe
Seating Actual (MPa) Gasket seating allowed stress(MPa) Result
Longitudinal hub stress SH=fMatm/(Lg12B1)= 176.67  1.5Sfatm= 206.85 Safe
2.5Snatm= 344.75 Safe
Radial fla-
nge stress		 SR=(1.33te+1)Matm/(Lt2B)= 30.58  Sfatm= 137.9 Safe
Tangential f
lange stress		 ST=YMatm/(t2B)-ZSR= 64.56  Sfatm= 137.9 Safe
Combined stress （SH+SR）/2= 103.63  Sfatm= 137.9 Safe
（SH+ST）/2= 120.62  Sfatm= 137.9 Safe
6. Rigidity calculation
Operating condition Rigidity index   J=52.14VMop/BscLEopgo2K1ho= = 0.872  Safe
Gasket seating condition Rigidity index   J=52.14VMatm/BscLEatmgo2K1ho= = 0.905  Safe
Note: 1. The regidity factor K1=0.3 for integral flange.
2. T0 means Atmospheric Temperature(gasket seating). T1 means Design Temperature(operating condition).

环槽密封法兰计算书 项目号 ITEM NO.
Flange calculation 文件号 DOC. NO. 1
As Per ASME VIII I-2021 Mandatory Appendix 2 FLANGE NAME N1
DESIGN DATA FIG
MAIN Design pressure P 1.94 Mpa 1
Design Temperature t 250 °C
SHELL Material SA-516 70
Allowable stress @T0 Snatm 137.9 Mpa
Allowable stress @T1 Sno 137.9 Mpa 法兰几何尺寸协调性校核 1
FLANGE Material SA-105 限制值 实际值 判断
Allowable stress @T0 Sfatm 137.9 Mpa 螺栓直径 2 1/4
Allowable stress @T1 Sfo 135.64 mm 根径 53.03 
Elastictiy Modules @T0
 Eatm 202713 Mpa B应大于 120.65  153.0  合格
Elastictiy Modules @T1
 Eop 188980 Mpa Rh应大于 69.85  75 合格
BOLT Material SA-193 B7 E应大于 57.15  67 合格
Allowable stress @T0 Sa 172.38 Mpa h应大于 91.95  110.0  合格
Allowable stress @T1 Sb 172.38 Mpa h应大于1.5g0 30 110 合格
Nominal Bolt diameter a 2 1/4 inch
Root diameter dr 53.03  mm All dimensions are free of corrosion. 《Pressure vessel design manual》一书对于椭圆垫，w值为
Number n 40 Partition Area Ar= 0 mm2
GASKET Gasket factor m 3 DIMENSIONS
（mm）		 B 1698.7  t 128
Seating load y 68.95 Mpa A 2084.0  go 20.0 
seating width w 60.00  mm C 1950.0  g1 50.7 
Basic seating width b0  7.50  mm Dout 1860.0  h 110.0 
Effective seating width b 6.93  mm Din 1740.0  R 75
Diameterof load reaction G 1846.14  mm
b0≤6.4mm     b= b0; b0 > 6.4mm     b=2.53√b0 b0≤6.4mm  G= ( Dout+Din )/2; b0 > 6.4mm   G= Dout- 2b
1. The bolt area check
Total hydrostatic end force H=πG2P/4 = 5.193E+06 N
Total joint‐contact surface compression load Hp=2P（πbGm+0.5Arm） = 4.678E+05 N
Min. required Operating Bolt Load Wm1=H+Hp = 5.661E+06 N
Min. required Gasket Seating Bolt Load Wm2=πbGy+0.5Ary = 2770770.432 N
Required Bolt Area at operating condition Ap=Wm1/Sb = 32839.1  mm2
Required Bolt Area at seating condition Aa=Wm2/Sa = 16073.6  mm2
Required Bolt Area Am=max(Ap,Aa) = 32839.1  mm2
Actual  bolt area Ab=nπdr2/4 = 88335.3072 mm2
Ab>=Am, the bolt area is OK!
Flange Design Bolt Load, Gasket Seating W W=0.5(Am+Ab)Sa = 10444020.7  N
2. The bolting spacing check
Actual  bolt distance Bs=Gsin(π/n) = 153.0  mm
Min. bolt spacing(According to TEMA) Bmin = 120.7  mm  
For vessels in lethal service, Max. bolt spacing Bsmax=2a+6t/(m+0.5) = 333.7  mm
Bolt pitch correction factor Bsc=max(sqrt(Bs/(2a+t)) , 1) = 1.0 
Bmin <=Bs   The space is OK! Bs  <= Bsmax The space is OK!
3. The flange load calculation
Operating  HD=πB2P/4= 4.397E+06 N hD=R+0.5g1= 100.325 mm
HG=HP=Wm1-H= 4.678E+05 N hG=0.5(C-G)= 51.9  mm
HT=H-HD= 7.964E+05 N hT=0.5(R+g1+hG)= 88.8  mm
MD=HDhDBSC= 4.411E+08 Nmm External pressure: Mop=HD(hD-hG)+HT(hT-hG )
MG=HGhGBSC= 2.429E+07 Nmm External pressure: = 2.421E+08 Nmm
MT=HThTBSC= 7.071E+07 Nmm Internal:Mop=MD+MG+MT = 5.361E+08 Nmm
Mop （Note：According to internal pressure) = 5.361E+08 Nmm
Total moment for gasket Seating,   Matm=WhGBSC = 542344316.9 Nmm
4. Factor calculation
h0=(Bgo)0.5= 184.32  h/h0= = 0.60 
K=A/B= 1.227  g1/g0= = 2.53 
Factor from Figure 2-7.1 T= 1.828  FIG 2-7.2 F = 0.791 
Z= 4.960  FIG 2-7.3 V = 0.159 
Y= 9.614  FIG 2-7.6 f = 1.567 
U= 10.566  e=F/h0 = 0.004 
d=Uh0g02/V= 4.915E+06 L=(t e+1)/T+t3/d= = 1.274 
5. Summary of stresses
When B≥20g1，B1=B = 1698.7  mm
Operating Actual (MPa) Operating allowed stress(MPa) Result
Longitudinal hub stress SH=fMop/(Lg12B1)= 151.30  1.5Sfo= 203.46 Safe
2.5Sno= 344.75 Safe
Radial fla-
nge stress		 SR=(1.33te+1)Mop/(Lt2B)= 26.19  Sfo= 135.64 Safe
Tangential f
lange stress		 ST=YMop/(t2B)-ZSR= 55.29  Sfo= 135.64 Safe
Combined stress （SH+SR）/2= 88.75  Sfo= 135.64 Safe
（SH+ST）/2= 103.30  Sfo= 135.64 Safe
Seating Actual (MPa) Gasket seating allowed stress(MPa) Result
Longitudinal hub stress SH=fMatm/(Lg12B1)= 153.07  1.5Sfatm= 206.85 Safe
2.5Snatm= 344.75 Safe
Radial fla-
nge stress		 SR=(1.33te+1)Matm/(Lt2B)= 26.50  Sfatm= 137.9 Safe
Tangential f
lange stress		 ST=YMatm/(t2B)-ZSR= 55.93  Sfatm= 137.9 Safe
Combined stress （SH+SR）/2= 89.78  Sfatm= 137.9 Safe
（SH+ST）/2= 104.50  Sfatm= 137.9 Safe
6. Rigidity calculation
Operating condition Rigidity index   J=52.14VMop/BscLEopgo2K1ho= = 0.832  Safe
Gasket seating condition Rigidity index   J=52.14VMatm/BscLEatmgo2K1ho= = 0.784  Safe
Note: 1. The regidity factor K1=0.3 for integral flange.
2. T0 means Atmospheric Temperature(gasket seating). T1 means Design Temperature(operating condition).
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