离心式压缩机的热力计算(C++)

1、离心式压缩机的热力计算 #include #include void main()double p0=200000,T0=350,ps_=380000,n=60000,G=0.25,H=0.635,c2r,c1=c2r=90,o1=0.98,a=0.05,n2=1.55,n3=1.9,n5=1.8;/压头系数取H=0.635,叶轮进口空气速度c1=90m/s,总压恢复系数o1=0.98,/ D1h/D2=0.3 double sc=ps_/p0; /1.压缩机增压比 cout1.压缩机增压比sc=scendl;double lcs=1004.5*T0*(pow(sc,0.4/1.4)-1);

2、/2.等熵过程的压缩功 cout2.等熵过程的压缩功lcs=lcsendl; double u2=sqrt(lcs/H); /3,H=0.635叶轮外径圆周速度coutu2=u2endl;double T1=T0-c1*c1/2/1005; /4.c1=90,叶轮进口处温度 coutT1=T1endl;double p1=o1*p0*(pow(T1/T0,3.5); /5进气管总压恢复系数为0.98，叶轮进口空气压力coutp1=p1endl;double j1=p1/T1/287; /6.叶轮进口密度coutj1=j1endl; double D2=60*u2*1000/3.14159/n;

3、 /7.叶轮外径coutD2=D2endl;double D1h=0.3*D2; /8,D1h/D2=0.3叶轮进口叶根直径coutD1h=D1hendl;double D1t=sqrt(D1h*D1h+4*G*1000000/3.1415/j1/c1); /9.叶轮进口叶尖直径coutD1t=D1tendl; coutD1t/D2=D1t/D2 一般范围在0.500.65之间endl; double D1=sqrt(D1h*D1h/2+D1t*D1t/2) ; /10.叶轮进口平均直径coutD1=D1endl;double u1t=D1t/D2*u2; /11.叶轮进口叶尖圆周速度cout

4、u1t=u1tendl; double w1t=sqrt(c1*c1+u1t*u1t); /12. 叶轮进口叶尖处气流相对速度coutw1t=w1tendl; double Mw1t=w1t/20.1/sqrt(T1); /13.叶轮进口叶尖马赫数coutMw1t=Mw1t 一般希望Mw1t取值范围0.800.92endl;double u1=D1/D2*u2; /14.叶轮进口平均直径处的圆周速度coutu1=u1endl;double w1=sqrt(c1*c1+u1*u1); /15. .叶轮进口平均直径处的相对速度coutw1=w1endl;double zi=10+0.03*D2;

5、/叶轮叶片数coutzi=ziendl;double h=1/(1+2*3.1415/3/zi*(1/(1-D1*D1/D2/D2); /16.叶轮滑动系数couth=hendl; double T2=T1+(h+a-h*h/2)*u2*u2/1005; /17.叶轮出口温度coutT2=T2endl;double p2=p1*pow(T2/T1,n2/(n2-1); /18.叶轮出口压力 coutp2=p2endl;double j2=p2/287/T2; /19.叶轮出口空气密度coutj2=j2endl;double c2u=h*u2; /20.叶轮出口周向分速度coutc2u=c2ue

6、ndl;double c2=sqrt(c2u*c2u+c2r*c2r); /21.叶轮出口气流绝对速度coutc2=c2endl;double a2=atan(c2r/c2u); /22.叶轮出口气流角couta2=a2endl;double w2=sqrt(c2*c2+u2*u2-2*c2*u2*cos(a2); /23.叶轮出口相对速度coutw2=w2endl;coutw2/w1=w2/w1判断叶轮中的相对运动是否是减速的endl; double l2=G*1000000/3.1415/D2/j2/c2r; /24.叶轮出口轴向宽度coutl2=l2endl;double D3=1.08

7、*D2; /25.无叶扩压器出口直径coutD3=D3endl;double c3=D2/D3*c2; /26. 无叶扩压器出口出口气流速度coutc3=c3endl;double T3=T2+(c2*c2-c3*c3)/2/1005; /27. 无叶扩压器出口温度coutT3=T3endl; double p3=p2*pow(T3/T2,n3/(n3-1); /28.取n3=1.9, 无叶扩压器出口压力coutp3=p3endl;double Mc3=c3/sqrt(T3)/20.1; /29.验算coutMc3=Mc3 是否=0.800.95endl;double a3g=3.1415/1

8、80*25; double a3=a3g;double a4g=a3g+3.1415/180*20;double a4=a4g;double D4=D3*cos(a3)/cos(a4); /30.直叶片扩压器出口直径coutD4=D4endl;coutD4/D3=D4/D3 是否=1.21.4endl;double r4=D4/2;double r3=D3/2;double L=(r4-r3)/sin(a3g+a4g)/2); /31.扩压器流道直线长度coutL=Lendl;double aav=3.14159/18; /平均扩张角取10coutaav=aavendl;double zd=3

9、.1415*(r4*sin(a4g)-r3*sin(a3g)/tan(aav/2)/L; /32.扩压器叶片数coutzd=zdendl;double n4=1.6,c4=111.3; /叶片扩压器多变指数n4=1.6,叶片扩压器出口速度c4=111.3/33.直叶片扩压器出口温度double T4_=T3*pow(c3*D3*sin(a3)/c4/D4/sin(a4),(n4-1); coutT4_=T4_endl;double T4=T3+(c3*c3-c4*c4)/2/1005;coutT4=T4endl;coutT4-T4_的绝对值为fabs(T4-T4_)是否小于0.5endl; d

10、ouble p4=p3*pow(T4/T3,n4/(n4-1); /34. 叶片扩压器出口压力coutp4=p4endl;double j4=p4/287/T4; /35. 叶片扩压器出口空气密度coutj4=j4endl;double c4u=c4*cos(a4); /36. 叶片扩压器出口周向分速coutc4u=c4uendl;double K=c4u*r4/1000; /37.系数KcoutK=Kendl;double C=720*j4*K*3.1415/G; /38.系数CcoutC=Cendl;double jcmax=360*1000/C+sqrt(720*1000*r4/C);

11、/39.蜗壳出口圆截面直径coutjcmax=jcmaxendl;double c5=G*1000000/3.1415/jcmax/jcmax/j4; /40.蜗壳出口气流速度coutc5=c5endl;double T5=T4+(c4*c4-c5*c5)/2/1005; /41. 蜗壳出口空气温度coutT5=T5endl;double p5=p4*pow(T5/T4,n5/(n5-1); /42. 蜗壳出口压力coutp5=p5endl;double Ts=T5+c5*c5/2010; /43. 蜗壳出口气流总温coutTs=Tsendl;double ps=p5*pow(Ts/T5,3.

12、5);/44 /44. 蜗壳出口气流总压coutps=psendl;cout与所要求的出口总压的相对误差fabs(ps-ps_)/ps_小于1%，满足要求endl;double lc=1005*(Ts-T0); /45.压缩机的实际耗功coutlc=lcendl;double Nc=G*lc/1000; /46.压缩机消耗功率coutNc=Ncendl;double ncs=lcs/lc; /47.压缩机绝热效率cout压缩机绝热效率为ncsendl;结果：1.压缩机增压比sc=1.92.等熵过程的压缩功lcs=70764.73.叶轮外径圆周速度u2=333.8274.叶轮进口处温度T1=34

13、5.975.进气管总压恢复系数为0.98，叶轮进口空气压力p1=1882156.叶轮进口密度j1=1.895547.叶轮外径D2=106.2618.叶轮进口叶根直径D1h=31.87829.叶轮进口叶尖直径D1t=53.6853D1t/D2=0.505224 一般范围在0.500.65之间10.叶轮进口平均直径D1=44.149411.叶轮进口叶尖圆周速度u1t=168.65712. 叶轮进口叶尖处气流相对速度w1t=191.16813.叶轮进口叶尖马赫数Mw1t=0.511329 一般希望Mw1t取值范围0.800.9214.叶轮进口平均直径处的圆周速度u1=138.69915.叶轮进口平均

14、直径处的相对速度w1=165.34叶轮叶片数zi=13.187816.叶轮滑动系数h=0.83896717.叶轮出口温度T2=405.5218.叶轮出口压力p2=29446419.叶轮出口空气密度j2=2.5301120.叶轮出口周向分速度c2u=280.0721.叶轮出口气流绝对速度c2=294.17522.叶轮出口气流角a2=0.31092623.叶轮出口相对速度w2=104.832w2/w1=0.63404判断叶轮中的相对运动是否是减速的 /小于1为减速24.叶轮出口轴向宽度l2=3.2888925.无叶扩压器出口直径D3=116.88726. 无叶扩压器出口出口气流速度c3=267.4

15、3227. 无叶扩压器出口温度T3=412.99228.无叶扩压器出口压力p3=30603629.验算Mc3=0.654706 是否=0.800.9530.直叶片扩压器出口直径D4=149.812D4/D3=1.28169 是否=1.21.431.扩压器流道直线长度L=28.703平均扩张角取10aav=0.17453332.扩压器叶片数zd=35.362133.直叶片扩压器出口温度T4_=442.16T4=442.411T4-T4_的绝对值为0.251063是否小于0.534. 叶片扩压器出口压力p4=36767535. 叶片扩压器出口空气密度j4=2.8957236. 叶片扩压器出口周向分

16、速c4u=78.702837.系数K=5.8953338.系数C=15445239.蜗壳出口圆截面直径jcmax=21.017340.蜗壳出口气流速度c5=62.214541. 蜗壳出口空气温度T5=446.64842. 蜗壳出口压力p5=37564643.蜗壳出口气流总温Ts=448.57444. 蜗壳出口气流总压ps=381345与所要求的出口总压的相对误差0.00353975小于1%，满足要求45.压缩机的实际耗功lc=99066.846.压缩机消耗功率Nc=24.7667压缩机绝热效率为0.714312Press any key to continue向心涡轮级的热力计算#includ

17、e #include void main()double p0=360000, p3=110000 ,T0=360, G=0.25,D1=0.12,x=0.97, y=0.88, a1g=0.314159,B2=0.610865,u=0.4,zn=27;/预取D1=120mm,喷嘴环速度系数x=0.97,叶轮速度系数y=0.88/喷嘴环出口叶片几何角a1g=18，叶轮出口相对气流角B2=35,u=0.4 double a1=a1g; /double zi=0.03*(33-a1/3.14159*180)*(33-a1/3.14159*180)+12; /double modf(double z

18、i_,double *zi); double zi=18; cout 1.叶轮叶片数zi=ziendl; double M=1-2/zi;cout2.速度比M=Mendl;double i1=cos(a1)*u/M*cos(a1)*u/M; double i1_=cos(a1)*u/M*u/M; double i2=1/y/cos(B2)*1/y/cos(B2)-1; double i3=2*cos(a1)*cos(a1)/M-1; double pt=x*x*(i1*i2+i3)/(1+x*x*(i1_*i2+i3); cout3.反力度pt=ptendl;double x0=x*sqrt(

19、1-pt)*cos(a1)/M;cout4.涡轮速比X0=x0endl;double s=p0/p3;cout5.涡轮膨胀比s=sendl;double vhs=1005*T0*(1-1/(pow(s,0.286);cout6.涡轮总等焓降vhs=vhsendl;double Cs=sqrt(2*vhs);cout7.等熵速度Cs=Csendl;double C1=x*sqrt(1-pt)*Cs; cout8.喷嘴环出口气流速度c1=C1endl;double k1_=pow(1/s,0.286);double k2_=pt+(1-pt)*k1_;double k3_=pow(k2_,3.5)

20、;double p1=p0*k3_; cout9.喷嘴环出口气流压力p1=p1endl;double T1=T0-x*x/1005*(1-pt)*vhs;cout10.喷嘴环出口气流温度T1=T1endl;double j1=p1/287/T1;cout11.喷嘴环出口气流密度j1=j1endl;double n=1/(1-log10(T1/T0)/log10(p1/p0);cout12.气流在喷嘴环中的多变指数n=nendl;double pcrn1=pow(2/(n+1),n/(n-1);cout13.临界压力比pcrn=pcrn1endl;double p11=p1/p0;cout14.

21、喷嘴环出口压力与涡轮进口压力之比p11=p11endl;coutpcrn1是否小于p11endl;double u1=x0*Cs;cout15.叶轮进口圆周速度u1=u1endl;double N1=60*u1/3.1415/D1;cout16.涡轮转速N1=N1endl;double C1u=M*u1;cout17.叶轮进口绝对速度的周向分量C1u=C1uendl;double C1r=C1*sin(a1);cout18.叶轮进口绝对速度的径向分量C1r=C1rendl;double w1=sqrt(C1*C1+u1*u1-2*C1*u1*cos(a1);cout19.叶轮进口相对速度w1=

22、w1endl;double w1u=u1-C1u;cout20.叶轮进口相对速度的周向分量w1=w1uendl;double B1=1.5708+atan(w1u/C1r);cout21.叶轮进口气流角B1=B1endl;double u2=u*u1;cout22.叶轮出口周向速度u2=u2endl;double w2s=sqrt(pt*Cs*Cs+w1*w1-u1*u1+u2*u2);cout23.叶轮出口理论相对速度w2s=w2sendl;double w2=y*w2s;cout24.叶轮出口实际相对速度w2=w2endl;double o=w2/w1; cout25.气流在叶轮中的加速因

23、子o=oendl;double C2=sqrt(w2*w2+u2*u2-2*w2*u2*cos(B2);cout26.叶轮出口绝对速度c2=C2endl;double a2=w2*sin(B2/C2);cout27.叶轮出口气流角的sin值a2endl;double T2=T1-pt*vhs/1005+(1-y*y)*w2s*w2s/2/1005;cout28.叶轮出口温度T2=T2endl;double j2=p3/T2/287;cout29.叶轮出口空气密度j2=j2endl;double en=(1-pt)*(1-x*x);cout30.喷嘴环相对能量损失en=enendl;double

24、 ei=(1-y*y)*(w2s/Cs)*(w2s/Cs);cout31.叶轮相对能量损失ei=eiendl;double ec2=(C2/Cs)*(C2/Cs);cout32.余速相对能量损失ec2=ec2endl;double nu=1-(en+ei+ec2);cout33.轮周效率nu=nuendl;double Ndf=736*1.18*j1*D1*D1*(pow(u1/100,3);cout34.轮盘摩擦损失功率Ndf=Ndfendl;double edf=Ndf/G/vhs;cout35.轮盘摩擦相对能量损失edf=edfendl;double zb=0.023; double n

25、_d=1-1.3*zb;cout36.间隙漏气修正系数n_d=n_dendl;double nt=(nu-edf)*n_d;cout37.涡轮绝热效率nt=ntendl;double vT0=vhs/1005;cout38.涡轮理论温降vT0=vT0endl;double vT=vT0*nt;cout39.涡轮实际温降vT=vTendl;double T3=T0-vT;cout40.涡轮出口速度T3=T3endl;double Nt=G*vhs*nt;cout41.涡轮功率Nt=Ntendl;double Nte=Nt*0.97;cout42.涡轮有效功率Nte=Nteendl;double

26、j3=p3/T3/287;cout43.涡轮出口空气密度j3=j3endl;double Q=G/j3;cout44.涡轮出口空气体积流量Q=Qendl;double w=3.1415*N1/30;cout45.叶轮角速度w=wendl;double Ns=w*sqrt(Q)/(pow(vhs,0.75);cout46.涡轮比转速Ns=Nsendl;double Fmin=sqrt(287*T0)*G*1000000/p0/sqrt(7*(pow(p1/p0,2/n)-(pow(p1/p0,(n+1)/n);cout47.喷嘴环最小截面积Fmin=Fminendl;double D1n=D1*

27、1000+2;cout48.喷嘴环内径D1n=D1nendl;double F1n=G*1000000/C1/sin(a1)/0.81/j1;/第49步cout49.喷嘴环出口总面积F1n=F1nendl;double ln=F1n/3.1415/D1n;cout50.喷嘴环出口叶片高度ln=lnendl;double bn=Fmin/zn/ln;cout51.喷嘴喉部宽度bn=bnendl;double h1=1-1.5*zi/3.14/D1/1000;cout52.叶轮进口阻塞系数h1=h1endl;double l1=G*1000/3.1415/D1/C1r/j1/h1;coutl1=l

28、1endl;coutl1?ln l1=l1 ln=lnendl; l1=1.18*ln;cout53.叶轮进口叶片高度l1=l1endl;double D2=u*D1*1000;cout54.叶轮出口平均直径D2=D2endl;double D2h=0.25*D1*1000; /预取D2h/D1=0.25cout55.叶轮出口叶根直径D2h=D2hendl;double F2=3.1415/2*(D2*D2-D2h*D2h);cout56.叶轮出口总面积F2=F2endl;double D2t=sqrt(D2*D2+2*F2/3.1415);cout57.叶轮出口叶尖直径D2t=D2tendl

29、;double l2=(D2t-D2h)/2;cout58.叶轮出口叶片高度l2=l2endl;double F2e=G*1000000/C2/j2;/sina2=1cout59.叶轮出口有效面积F2e=F2eendl;double h2=F2e/F2;cout60.叶轮出口的阻塞系数h2=h2endl;double v2=(F2-F2e)*sin(B2-0.0349066)/l2/zi*2;cout61.叶轮出口叶片尾缘厚度v2=v2endl;double lav=(l1+l2)/2;cout62.叶轮叶片高度lav=lav 0.23/lav与第36步预取值比较endl;结果1.叶轮叶片数z

30、i=182.速度比M=0.8888893.反力度pt=0.5292054.涡轮速比X0=0.7121095.涡轮膨胀比s=3.272736.涡轮总等焓降vhs=1040477.等熵速度Cs=456.1728.喷嘴环出口气流速度c1=303.619.喷嘴环出口气流压力p1=21635710.喷嘴环出口气流温度T1=314.1411.喷嘴环出口气流密度j1=2.3997512.气流在喷嘴环中的多变指数n=1.3654213.临界压力比pcrn=0.53417714.喷嘴环出口压力与涡轮进口压力之比p11=0.6009920.534177是否小于0.600992 /小于15.叶轮进口圆周速度u1=324.84416.涡轮转速N1=51702.1 /小于9000017.叶轮进口绝对速度的周向分量C1u=288.75118.叶轮进口绝对速度的径向分量C1r=93.820719.叶轮进口相对速度w1=100