O形密封圈-吊环螺栓快开法兰计算

快开法兰强度计算CALCULATIONFORUTYPEGROOVEFLANGE按照Swedrsh压力容器规范1987版AccordingtoSwedrshPressureVcesselCode1987设计条件DesignConditionT=160℃设计温度DesigntemperatureP=0.8Mpa设计内压力DesignpressureD1=1139mm垫片内径GasketIDD2=1155mm垫片外径GasketODk1=3200垫片常数Gasketconstantk2=40垫片常数Gasketconstant304螺栓材料Boltmaterialn=24螺栓数量Boltnumberd=23.752mm螺栓根径Boltrootdiameter[σ]b=101.6Mpa螺栓的许用应力Boltallowablestress304法兰材料FlangematerialDi=1120mm法兰内径FlangeIDS1=8mm连接筒体厚度ConnectionshellthicknessDh=1330mm螺栓中心圆直径BCDDy=1300mmU形槽底直径Utypegroovebottomdiameterh=110mm法兰厚度Flangethickness[σ]=101.6Mpa法兰许用应力Flangeallowablestress1.螺栓载荷Boltload1.1内压引起的螺栓载荷BoltloadcausedbyinternalpressPi=P*πDm2/4=826621.5NDm=(D1+D2)/2=1147mm1.2计算垫片系数Calculategasketfactorm1=k1k3/(10αP)预紧状态Boltup=0.31177k3=0.894温度修正系数Temperaturefactorα=Dm/beff系数Factor=1147m2=1+k2/α=1.034874操作状态Operationb=(D2-D1)/2mm垫片宽度Gasketwidth=8mmm=max(m2,1.6,0.2m1+0.8*(m1*m2)0.5=1.2对于O形圈ForOring1.3确定垫片有效宽度beffGasketeffictivewidthbeff=1.8*b0.5(b13mm)beff=0.5b(b=13mm)beff=1(O形圈)ForOring=1mm1.4总的螺栓力TotalboltforcePs=mPi=991945.8N每个螺栓的力EachboltforcePs'=Ps/n=41331.07N1.5计算螺栓尺寸Calculateboltsize螺栓的设计根径Boltdesignrootdiameterd'=(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Flangecalculation2.1法兰外力矩计算Calculateflangemoment2.1.1确定力作用圆直径ForceeffectcirclediameterPa作用圆直径PaeffectcirclediameterDpa=Di+S1=1128mmPp作用圆直径为PpeffectcirclediameterDpp=(Di+(Dm-b))/2=1129.5mmPt作用圆直径为DmPteffectcirclediameter=1147mm2.1.2外力矩MomentM=0.5(Pa*e1+Pp*e2)=41153993NmmPa=πDi2*P/4=788162.8NPp=π[(Dm-b)2-Di2]P/4=26968.06Ne1=(Dh-Dpa)/2=101mme2=(Dh-Dpp)/2=100.25mm2.2法兰应力计算Flangestresscalculation2.2.1截面I-I处应力StressonsectionI-I圆周上单位周长的弯矩MomentonunitperimeterM1=M*A'/(πDm1)=1297.682NmmDm1=Di+S1=1128mmA'=f/(f2+(f-1)2+g)=0.111742f=1+β1h/2=2.053743g=0.91Z(h/S1)3ln(Dy/Di)/(β1Dm1)=13.05114β1=1.82/(S1Dm1)0.5=0.019159法兰在截面I-I处总的最大应力MaxstressonflangeI-Isectionσ1=σb1+σa=149.6577Mpa弯曲应力Bendingstressσb1=6M1/S12=121.6577Mpa轴向应力Axialstressσa=PDi/(4S1)=28Mpa2.2.2截面II-II处应力StressonsectionII-II截面II-II处单位周长的弯矩MomentonunitperimeterM2=M2'/(πD3)=16616.22NmmM2'=0.75(Pa+Pp)e4=59300766Nmm截面II-II处应力StressonsectionII-IIσb2=6M2/h2=8.239446Mpa3.应力评定Stressassessmentσ1=1.5[σ]σ1=149.6581.5[σ]=152.4MPaσb2=[σ]σb2=8.23945[σ]=101.6MPa应力评定合格，法兰计算通过。Thisflangeisadequate.