快开法兰强度计算
CALCULATION FOR "U" TYPE GROOVE FLANGE
按照Swedrsh压力容器规范1987版
According to Swedrsh Pressure Vcesl Code 1987
设计条件Design Condition
T=160℃设计温度Design temperature
举办英语P=0.8Mpa设计内压力Design pressure
D1=1139mm垫片内径Gasket ID
D2=1155mm垫片外径Gasket OD
k1=3200垫片常数Gasket constant
k2=40垫片常数Gasket constant
304螺栓材料Bolt material
n=24螺栓数量Bolt number
d=23.752mm螺栓根径Bolt root diameter
[σ]b=101.6Mpa螺栓的许用应力Bolt allowable stress
304法兰材料Flange material
Di=1120mm法兰内径Flange ID
S1=8mm连接筒体厚度Connection shell thickness
Dh=1330mm螺栓中心圆直径BCD
Dy=1300mm U形槽底直径U type groove bottom diametertimber
h=110mm法兰厚度Flange thickness
[σ]=101.6Mpa法兰许用应力Flange allowable stress
1. 螺栓载荷Bolt load
1.1 内压引起的螺栓载荷Bolt load caud by internal press Pi=P*πDm2/4
=826621.5N
Dm=(D1+D2)/2
=1147mm
1.2 计算垫片系数Calculate gasket factor
m1=k1k3/(10αP)预紧状态Bolt up
=0.31177
k3=0.894温度修正系数Temperature factor
α=Dm/beff系数Factor
=1147
m2=1+k2/α
=1.034874操作状态Operation
b=(D2-D1)/2mm垫片宽度Gasket width
=8mm
m=max(m2,1.6,0.2m1+0.8*(m1*m2)0.5
=1.2对于O形圈For O ring
1.3 确定垫片有效宽度beff Gasket effictive width
beff=1.8*b0.5 (b>13mm)
beff=0.5b (b<=13mm)
beff=1 (O形圈)For O ring
=1mm
1.4 总的螺栓力Total bolt force
Ps=mPi
=991945.8N
每个螺栓的力Each bolt force
Ps'=Ps/n
=41331.07N
1.5 计算螺栓尺寸Calculate bolt size
螺栓的设计根径Bolt design root diameter
d'=(4Ps'/(π[σ]b))0.5
=22.75865mm
螺栓根径不小于需要的螺栓根径，螺栓合格。
2. 法兰计算Flange calculation
2.1 法兰外力矩计算Calculate flange moment
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2.1.1 确定力作用圆直径Force effect circle diameter Pa作用圆直径Pa effect circle diameter Dpa=Di+S1
=1128mm
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Pp作用圆直径为Pp effect circle diameter Dpp=(Di+(Dm-b))/2
=1129.5mm
Pt作用圆直径为Dm Pt effect circle diameter =1147mm
2.1.2 外力矩Moment
M=0.5(Pa*e1+Pp*e2)
=41153993Nmm
Pa=πDi2*P/4
=788162.8Nabove the moon
Pp=π[(Dm-b)2-Di2]P/4
=26968.06N
e1=(Dh-Dpa)/2
=101mm
e2=(Dh-Dpp)/2
=100.25mm
2.2 法兰应力计算Flange stress calculation
2.2.1 截面I-I处应力Stress on ction I-I
口才练习圆周上单位周长的弯矩Moment on unit perimeter
M1=M*A'/(πDm1)
=1297.682Nmm
Dm1=Di+S1
=1128mm
A'=f/(f2+(f-1)2+g)
=0.111742
f=1+β1h/2
=2.053743
g=0.91Z(h/S1)3ln(Dy/Di)/(β1Dm1)
=13.05114
thunderbirdβ1=1.82/(S1Dm1)0.5
=0.019159
法兰在截面I-I处总的最大应力Max stress on flange I-I ction σ1=σb1+σa
=149.6577Mpa
弯曲应力Bending stress
σb1=6M1/S12
=121.6577Mpa
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轴向应力Axial stress
σa=PDi/(4S1)
=28Mpa
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2.2.2 截面II-II处应力Stress on ction II-II
截面II-II处单位周长的弯矩Moment on unit perimeter
M2=M2'/(πD3)
=16616.22Nmm
M2'=0.75(Pa+Pp)e4
=59300766Nmm
截面II-II处应力Stress on ction II-II六级成绩查询官网
σb2=6M2/h2
=8.239446Mpa
3. 应力评定Stress asssment
σ1<=1.5[σ]σ1=149.658 1.5[σ]=152.4MPa
σb2<=[σ]σb2=8.23945[σ]=101.6MPa
应力评定合格，法兰计算通过。This flange is adequate.
