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增速器设计过程

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1、设计结论设计要求：功率645KW输入速度27rpm传动比80使用年限10年经过初步计算和虚拟仿真，本设计方案经静力学和动力学分析符合设计要求。初步计算（EXCEL计算）选择一级行星轮和二级平行轴齿轮机构。条件=645KW，=26.8rpm，总传动比=56.6，按三级传动取=5，=4. =4行星齿轮系的设计i5555za31312328zb12512591110zc47473441np3333j=(zb-zc)/(za+zc)1111压力角202020200.3490660.3490660.3490660.349066啮合角ac23.523.523.523.50.4101520.4101520.4101520.410152ha*1111c*0.250.250.250.25P645645645645n272727270.9750.9750.9750.975n1T1=Ta/np*Kc17.0533817051.617051.617051.6na=n/il135135135135Kc1.151.151.151.15Ta=9549P/na44.4870844482.4344482.4344482

2、.431111u1.5161291.5161291.4782611.464286K1.41.41.41.4d0.50.50.50.5a0.3974360.3974360.4035090.405797H1170117011701170ac中心矩a0373.006373.1236368.751367.1417a0取整375375370368a390390456414m9.6153859.61538512.9824610.6666710101612中心矩变动系数y=0.5*（za+zc)(cosa/cosa-1)0.9624990.9624990.7033650.851441ac中心矩a=a+y*m399.625399.625467.2538424.2173取值400400470425实际中心距变动系数Y110.8750.916667实际捏合角ac0.4123030.4123030.4233890.41436723.6232323.6232324.2584123.74151总变位系数x1.089161.089160.967061.001128xa0.50.50.50.5xc0.589160.

3、589160.467060.501128齿高变动系数y0.089160.089160.092060.084462太阳轮尺寸da310310368336ha14.108414.108422.5270416.98646hf7.57.5129b159159190172行星轮尺寸dc470470544492ha15152217hf11.608411.608418.5270413.98646b164164195177bc中心矩a=0.5*m*(zb-zc)390390456414bc中心距变位系数Y110.8750.916667bc0.4123030.4123030.4233890.41436723.6232323.6232324.2584123.74151x1.089161.089160.967061.001128y0.089160.089160.092060.084462xb1.6783191.6783191.4341191.502256内齿圈尺寸db1250125014561320ha25.891625.891637.4729629.01354hf-4.28319-4.28319-2.94

4、591-3.02708b159159190172二级平行轴齿轮系设计P=645KW，n1=135rpm，i=4m12121212z1z125252525z2z2100100100100角度20202020弧度0.3490660.3490660.3490660.349066ha*1111c*0.250.250.250.25标准高度变位角度变位d=mzd1300300300300d21200120012001200db=mzcosdb1281.9259281.9259281.9259281.9259db21127.7041127.7041127.7041127.704a750750750750a750750771.9002771角度202024.0722523.92206弧度0.3490660.3490660.420140.417519inv()0.0266inv()=inv()+2(x1+x2)*tan/(z1+z2)0.026435y=(a-a)/m01.8250161.75y=x-y00.1549840.16922x100.40.680.67x20-0.41.31.24922x1.9

5、81.91922ha1=m(ha*+x1-y)ha11216.818.00936ha2=m(ha*+x2-y)ha2127.224.96hf1=m(ha*+c*-x1)hf11510.26.96hf2=m(ha*+c*-x2)hf21519.80.009359h=ha+hfh1272724.96936h2272724.96936da=d+2hada1324333.6336.0187da212241214.41249.92a=arccos(db/da)a1角度29.5248832.3171632.96337a1弧度0.5153060.5640410.575319a2角度22.879221.7808625.54847a2弧度0.3993170.3801480.4459051.7286231.6356281.36299512.1994090.803870.56243920.807241.1312740.652754选择角度变位轴的设计太阳轮轴行星轮轴行星轮支架轴carriersunplanetarypravell1pravell2P645645645645645n26.81355762160C112112112112112d323.365188.6369#DIV/0!116.304774.86061romax分析建模输入功率645KW，速度26.8rpm，太阳轮速度135rpm,平行轴输出速度576rpm，功率-645KW。静力学分析齿轮分析轴分析行星支架太阳轴平行轴1平行轴2轴承分析动力学分析（平行轴1为例）振型1.933e4rpm和2.899e4rpm阻尼固有频率临界速度图当工作转速一阶临界转速时，0.75当在第r阶及第r+1阶之间是，1.40.7模态柔度振型谐响应总装图

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