O形密封圈,吊环螺栓快开法兰计算--蓝皮书

CALCULATION FOR \"U\" TYPE GROOVE FLANGE

按照Swedrsh压力容器规范1987版

According to Swedrsh Pressure Vcessel Code 1987设计条件

T=200℃设计温度P=1.2Mpa设计内压力D1=920mm垫片内径D2=940mm

垫片外径k1=3200垫片常数k2=40

垫片常数304螺栓材料n=24螺栓数量d=20.5mm螺栓根径

[σ]b=127

Mpa螺栓的许用应力316L法兰材料Di=900mm法兰内径S1=12mm连接筒体厚度Dh=990mm螺栓中心圆直径Dy=968mmU形槽底直径h=80mm法兰厚度[σ]=80

Mpa

法兰许用应力

1. 螺栓载荷Bolt load1.1 内压引起的螺栓载荷Pi=P*πDm2/4

=815149NDm=(D1+D2)/2

=930

mm

1.2 计算垫片系数m1=k1k3/(10αP)

预紧状态=0.249462k3=0.87温度修正系数

α=Dm/beff

系数

=930m2=1+k2/α

=1.043011操作状态b=(D2-D1)/2mm

垫片宽度=10mm

Design ConditionDesign temperatureDesign pressureGasket IDGasket OD

Gasket constantGasket constantBolt materialBolt number

Bolt root diameterBolt allowable stressFlange materialFlange ID

Connection shell thicknessBCD

U type groove bottom diameterFlange thickness

Flange allowable stress

Bolt load caused by internal press

Calculate gasket factorBolt up

Temperature factorFactor

OperationGasket width

m=max(m2,1.6,0.2m1+0.8*(m1*m2)0.5

=1.2对于O形圈1.3 确定垫片有效宽度beffbeff=1.8*b0.5 (b>13mm)beff=0.5b (b<=13mm)beff=1 (O形圈)

=1mm1.4 总的螺栓力Ps=mPi

=978178.8N每个螺栓的力Ps'=Ps/n

=40757.45N

For O ring

Gasket effictive width

For O ring

Total bolt force

Each bolt force

1.5 计算螺栓尺寸Calculate bolt size螺栓的设计根径Bolt design root diameterd'=(4Ps'/(π[σ]b))0.5

=20.21421mm

螺栓根径不小于需要的螺栓根径，螺栓合格。2. 法兰计算

2.1 法兰外力矩计算2.1.1 确定力作用圆直径Pa作用圆直径Dpa=Di+S1

=912mmPp作用圆直径为Dpp=(Di+(Dm-b))/2

=910mmPt作用圆直径为Dm

=930mm2.1.2 外力矩

M=0.5(Pa*e1+Pp*e2)

=15572560NmmPa=πDi2*P/4

=763407

N

Flange calculation

Calculate flange moment

Force effect circle diameterPa effect circle diameter

Pp effect circle diameter

Pt effect circle diameter

Moment

Pp=π[(Dm-b)2-Di2]P/4

=34306.19Ne1=(Dh-Dpa)/2

=39mm

e2=(Dh-Dpp)/2

=40

mm

Flange stress calculationStress on section I-IMoment on unit perimeter

2.2 法兰应力计算2.2.1 截面I-I处应力圆周上单位周长的弯矩M1=M*A'/(πDm1)

=2118.702NmmDm1=Di+S1

=912mmA'=f/(f2+(f-1)2+g)=0.389811f=1+β1h/2

=1.695894

g=0.91Z(h/S1)3ln(Dy/Di)/(β1Dm1)

=0.990224β1=1.82/(S1Dm1)0.5

=0.017397

法兰在截面I-I处总的最大应力σ1=σb1+σa

=110.7793Mpa弯曲应力σb1=6M1/S12

=88.27925Mpa轴向应力

σa=PDi/(4S1)

=22.5Mpa2.2.2 截面II-II处应力截面II-II处单位周长的弯矩M2=M2'/(πD3)

=6801.429NmmM2'=0.75(Pa+Pp)e4

=19743402Nmm截面II-II处应力σb2=6M2/h2

=6.376339Mpa

Max stress on flange I-I section

Bending stress

Axial stress

Stress on section II-IIMoment on unit perimeter

Stress on section II-II

3. 应力评定Stress assessmentσ1<=1.5[σ]σ1=110.7791.5[σ]=120MPaσb2<=[σ]σb2=6.37634[σ]=80MPa应力评定合格，法兰计算通过。This flange is adequate.