多级压气机一维气动设计

多级压气机一维气动设计设计指标：压比10质量流量8kg/s进口条件：大气压P=101325pa温度T=288.15k密度p=1.225kg/m3结构形式：参考发动机-透博梅卡公司TM333公司2级轴流加1级离心压比10.5-11转速45000r/min空气流量3kg/s输出功率800kw选择结构为2级轴流（1级压比1.4二级压比1.35总压比1.89）加一级离心（压比5.5）轴流级设计：第一级（等环量设计）设计转速30000r/min转子设计1：全压p=101325义0.4=40530pain：体积流量q=8/p=6.5306m3/sv：压升Ap=p=40530pain4：比转速n=5.54八孝葭=5.54x30000x"5306=148.687s（Ap）4（40530）45：由下图由比转速选择R+S级，选择全压效率和全压系数为V=0.4n=85.59%ttF

6：I即20D26：I即20D2犯30D芋如44。4M出叶轮直径D=-上==0.261549549mn\w30000\0.4t7：叶轮外缘圆周速度LD/60二410.8410705m/s8：流量系数中=，_兀C一D2u4t6.5306x4兀x0.265872x417.63=0.2958572499：全压系数W年=建篝短=0.3920331632t10：轮毂比选为d=d/D=0.55所以d=0.143852252所以轴向速度c2aq=174.2656758c2a兀一D2（1一d2）42/图4.20日与鼻间的关系V=\|//r|=0.44326t.thtF图最隹干算蠡数码酬，»图最隹干算蠡数码酬，»与单皴理论全压杀薮曲必问的关系11叶片数目选择10-20由上表叶片选择在8-16又有公式10-20由上表叶片选择在8-16又有公式表44叶片数月与轮鞍同关系选择16个叶片12：将叶片截面分为6个截面，其中相对平均半径为截面123456相对半径;0.650.710.770.8430.921.0半径2r=2~rrt0.17280.1887680.20470.224120.24460.26587rm■1+d2，=0.8432

厂为叶轮半径t1552841圆周速度u=四60271.46296.516321.57352.06384.216417.63Ac=_^p_n=0.8586upu“tFtFc=01u141.95129.957119.83109.45100.29392.27ca203.69203.69203.69203.69203.69203.69uuUp=cot-1—1ca36.88334.48732.35130.0527.9326uu-U-cp=cot-12u2ca57.55150.72645.2740.01635.65632.048Ap=p-P2120.66816.23912.9199.9667.7266.0481T=/1.55、_21.5(cotp-cotp)312或者查看图4-301.2251.0490.91710.7960.69830.6193攻角i32.41.81.070.3-0.5(2a、2m=0.23——-0.002p+Ib)20.18a=a/b=0.450.2511980.2648480.275760.2862680.2949880.302204g_Ap-icm1-五22.85518.66515.6113.111.47710.63k_0.50ic11.4279.337.8056.555.7385.315安装角0_p+i+ki1i51.2646.21741.95637.6733.96830.815轮缘功L_uAcu39533.7

出口温度T*=L+T*2c1p327.5图第30扩任式叶栅中颊宓气流

转折角ar号叶栅稠度「及

颖定出口气流角踮间的关春静子设计：理论全压系数为W=w/n=0.44326t.thtF查得n2=0,18截面123456相对半径；0.650.710.770.8430.921.0半径2r=2~rrtr为叶轮半径t0.17281550.1887680.204720.224128410.24460.26587

ca203.69203.69203.69203.69203.69203.69c2u141.95129.957119.83109.45100.29392.27c=nc3u22u25.55123.39221.56919.718.0516.6进气角8=cot-icu2ca55.1357.46159.53161.74963.78565.63一二—一c出气角8=cot-i-^u3ca82.8583.44883.95584.475784.9385.34AS=8-83227.7225.98724.42422.7221.14519.71T=1.5521.5(cot8-cot8)323或者查看图4-300.8760.7640.67780.59580.52820.4728_।(c+c、2c1c2+~^2u3u-mslla/Vk7220.235217.64215.61213.68212.1210.84tc=|2(c-c)/csycI3u2ums1.0570.9790.9115c=2(sin8/sin8)2.75yc23/\1.18571.3496叶片数Z="从m(sc),rc1-d，tyc入为1-1.6ms21第二级设计（等环量设计）设计转速30000r/minV2总压P*=141855pa总温T*=327.4k静温丁=T*———=306.52kK=1KK=1K=103130.72pa密度「=RT=1.1723kg/m3设计压比1.35转子设计1：全压p=141855义0.35=49649.5pain2：体积流量q=8/p=6.8242m3/sv3：压升Ap=p-49649.5pain4：比转速n=5.54n*-=5.54x30000xv6.8242=130.533s(Ap)3(49649.5,5：由下图由比转速选择R+S级，选择全压效率和全压系数为V=0.4609n=V=0.4609n=85.25%ttFTw150前一7一切。¥扬而.通f湫6：等外径设计，叶轮直径D=0.26587m7：叶轮外缘圆周速度u-冗Dn/60=417.63m/st8：8：:0.2943流量系数中二上兀C一D2u4t

6.8242x4兀x0.265872x417.639：全压系数w=

tAp49649.5x2=0.4856*2L1723x417.6322t10：轮毂比选为d=d/D=0.7所以d=0.1861m无因次轴向速度C=*=0.57701-d2所以c=cu=241m/s00t为避免在叶片根部产生气流分离，验算最小轮毂比理论全压系数为W=w/n=0.5696t.thtF由下图查得n=0,14由下表，对于R+S级2

2x0.577VG-n)—0.5696G-0.14)t.2x0.577VG-n)—0.5696G-0.14)t.th2:2.3558所以叶轮最小允许轮毂比为d=1/中-0,42448符合要求minr对于后导叶①=22c="々JfnV2t.th后导叶最小轮毂比为dI1dInd+—==0.026符合要求中\21-d2fmin表44叶片数月与轮辍同关系10-20由上表叶片选择在10-20又有公式ZZ=兀入T1^-d=Kx

mm1-d(0.9-1.5)x1xil07=16-261-0.7tt为叶珊稠度，取1.0-1.5m当d=0.5—0.7时当d=0.3—0.4时入为0.9—1.5m入为2.0或者更多m选择22个叶片12：将叶片截面分为6个截面，其中相对平均半径为m截面123456相对半径;0.70.750.80.8630.931半径2r=2~rrtr为叶轮半径t0.1861090.19940250.2126960.229445810.24725910.26587圆周速度u=四60292.33313.2114769334.092242360.4020061388.3822313417.6153025Ac=-p^—n=0.8525upuntFtFc=c查上表1u3u169.944158.6149283148.7014953137.8461138127.9152648118.9611962ca241241241241241241C=Ac+c2uu1u195.495566182.0069283170.2704953157.5461138145.9652648135.5611962uu-u-cB=cot-11u1ca42.0936184839.7452884837.6373488635.2741761133.0547506531.00479689uu-cB=cot-12u2ca68.1094630361.4353666855.7937691549.9118191944.8320580840.51210013Ap=p-B2126.0158445521.690078218.1564202914.6376430811.777307439.507303243

1T=1.5521.5(cotp-cotp)312或者查看图4-301.2520139771.1069500690.9920112350.8772412460.7811309620.700901971攻角i32.41.810.3-0.5(2a、2m=0.23———0.002p+Ib)20.184=a/b=0.450.2300810740.2434292670.2547124620.2664763620.2766358840.2852758g=Ap-ic1m1一后28.9735325625.0967322421.9766382319.0605926916.7064549115.17983818k=0.50ic14.4867662812.5483661210.988319119.5302963468.3532274557.589919091安装角0=p+i+ki1i59.5803847654.6936546150.4256679745.8044724641.7079781138.09471598轮缘功L=uAcu49680.01595出口温度T*=L+T*2c1p376.83

图第30#压式叶栅中额定气流

揩折角&Tm叶栅凋度r及

颖定出口气流角尾;间的关於静子设计：理论全压系数为W=甲/n=0.44326t.thtF查得n20.18截面123456相对半径;0.70.750.80.8630.931半径2r=2~rrtr为叶轮半径t0.1861090.19940250.2126960.229445810.24725910.26587ca241241241241241241

c2u195.495566182.0069283170.2704953157.5461138145.9652648135.5611962c=nc3u22u27.3693792425.4809699623.8378693422.0564559320.4351370718.97856747进气角8=cot-icu2ca50.9515567152.93933354.7581606956.8266196958.7981776760.64248192一二—一c出气角8=cot-i-^u-3ca83.5209127683.9645309884.3511158884.7708253585.1533067685.49729318AS=8-83232.5693560631.0251979829.5929551927.9442056626.3551290924.854811251T=/1.55、_21.5(cot8-cot8)323或者查看图4-301.2276535821.081856810.9671164080.8537099670.759193970.680529758I(c+c'c=1c2+—2u3u-msAlaI2,2265.5149637262.381034259.8086109257.187229254.9573953253.0842442tc=|2(c-c)/csyc।3u2ums1.2664159071.1931194571.1272345861.0536266390.9847145450.921295035c=2(sin8/sin8)2.75yc23/\1.015654761.0918756721.1615842441.2403165041.3143184971.382176109叶片数Z=2兀rrm(1Tsc/rc1-d，tycr为1-1.6ms27个叶片离心机级设计设计压比5.5转速30000r/min进口流量8kg/s进口条件：V2总压P*=191504.25pa总温T*=376.83k静温丁=T*———=347.65kPK=1静压p2K=106908.525pa密度「=RT=1.07149kg/静压p2进口速度。=242.17m/s1,进口部分损失系数4=0.03ic2.2.进气多变指数mc+1=1.3833k/1、」K—11-^)ic3,定熵压缩功*三3,定熵压缩功*三RTEK-11k-1=237590.446J/kgJ4.选取定熵能量头系数选定B=50选出口流量系数①=0,248选轮阻及漏气损失2A2rP+P=0.03103叶片数Z=24多变效率「=0.81dftopt兀①=1—-sinP一①cotP=0.6916283082uZ2A2r2AW=”(1+P+P)=0.5776025s2uoptdft.叶轮圆周速度u=，,匕=641.35716992Ws.导风轮进口轴向速度c为242.17m/s1z.进口流量系数①=c/u=0.37758991611z2.叶轮外径D=60u/(即)=0.408312698221/2=0.177287904.D=0.26587D/D=0.6511431111/2=0.177287904d=D2-4qm10.导风轮进口内径L1邛1c1z_ii,导风轮进口平均直径Dm=《V+d2)2)/2=0.22596222912.导风轮顶部周速u=n兀D/60=417,615302511TOC\o"1-5"\h\z.导风轮进口平均直径周速u=n兀D/60=354.93017131mm.导风轮进口根部周速u=n兀d/60=278,47497580.导风轮顶部气流角B=tan一i(c/u)=30.1089205911z1.导风轮平均中径气流角B=tan_1(c/u)=34,305844161m1z1m.导风轮根部气流角B=tan-1(c/u)=41.0111777901z0.导风轮顶部气流冲角i选取为31.导风轮平均中径气流冲角i选取为41m.导风轮根部气流冲角i选取为50TOC\o"1-5"\h\z.导风轮顶部叶片安装角p=i+p=33.108920591A11.导风轮平均中径叶片安装角p=i+p=38.305844161Am1m1m.导风轮根部叶片安装角p=i+p=46.011177790A00.导风轮顶部相对速度W=(2+u2)/2=482,751333311z1.导风轮平均中径相对速度w=(c2+u2)/2=429,67631471m1z1m.导风轮根部相对速度w=(2+u2)/2=369,0455542101z0.导风轮叶尖进口马赫数MA=W/、.kT=1.2915225911.导风轮叶片数z=fl]2兀sin(/+以A)/2)=24J)inD/D7opt21.导风轮叶片前缘厚度8=1mm1.导风轮进口阻塞系数工=1--28=0.944806471兀DsinP1m1Am31.导风轮进口叶片内部速度c=c/T=256,317042411z132.导风轮进口叶片马赫数：三1=1.310917858kRT

33.滑移系数目=—133.滑移系数目=—1+:0.6981334382兀3Z1-m^Dj2TOC\o"1-5"\h\z34.叶轮出口气流周向速度c=日u=447.75288632u2.选取出口流量系数隼=0.248，则叶轮出口气流径向速度2rc=4u=159.05657812r2r2.叶轮出口绝对速度c=.Jc2+c2=475.1648582、2r2u.导风轮损失系数选为C=0.21.导风轮中气流能量损失h=cwm=18462.17354h112.叶轮中损失系数选为C=0.12.叶轮中气流能量损失h=c2=1264.949753h222.轮盘摩擦鼓风损失系数a=0.04.轮盘摩擦鼓风损失h=au2=16453.56078r2.叶轮气流总损失Zh=h+h+h=36180.68407h1h2r.叶轮出口前气流温度T=T+k-[uc+h-c2-c2]=566.673815921kRI22ur2j.叶轮气流指数系数a=&-也=2.924543166ik-1RT-T)21.叶轮气流多变指数m=-1-+1=1.51960383ia-1i….,mmi、一.叶轮出口气流压力p=p-m-1=446245.46921T.叶轮出口前气流密度p=p/rt=2.743266457222.叶轮出口叶片厚度5=2.5mm2.叶片出口堵塞系数工二1一Z2B二0.9382129682兀Dsinp22A.叶轮出口气流径向速度0.0:149.22894433r22r.叶轮出口气流绝对速度c=,：FT=471,966021c=03'3r3u3u2u.叶轮出口外气流出口角a=tan-1(c/0)=18.4324130733r3u.叶轮出口外气流温度t=t+J-0=565,1664939322010.叶轮出口外气流压力p氏p32.叶轮出口外气流密度p=p/rt=2.7505828633.叶轮宽度b=q/(兀D0p)=0.0151939062m23r3.叶轮出口相对宽度b/D=0.03721144622.叶轮出口马赫数Ma=0/■(k