减速器设计传动零件设计资料

1、课程内容,目录,机电工程系,金守宽,机械设计课程设计,课程内容,目录,一、传动整体方案设计,二、传动零件设计,已知各轴,P n T i,一,减速器外传动零件设计,1,普通,V,带传动,二、传动零件设计,2,链传动,二）减速器内传动零件设计,1,齿轮传动设计,4,键的选择及强度校核,5,联轴器的选择,3,滚动轴承的选择,2,轴的设计,由传动系统方案,带式输送机、工作,16,小时，查表得,Ks= 1.3,工况系数,计算功率,Pc=KsP kW,选用型号,B,型三角带,n=1440r/min,计算功率,P,s,kW,小,带,轮,转,速,n,r,p,m,Z,A,B,C,D,F,一,减速器外传动零件设计

2、,1,普通,V,带传动,1,选择三角带型号,课程内容,目录,取滑动率,e = 0.02,带实际传动比,i,d,D,2,D,1,1,e,2,确定带轮节圆直径,D,1,D,2,查表选推荐值,Dmin=140(125,选择,D,1,140mm,D,2,i,d,D,1,1-e)mm,注意圆整,3,验算带速,v,v,p,D,1,n,60,1000,v,525,m/s,合适,初定中心距,a,0,公式,0.7,D,1,D,2,a,0,2,D,1,D,2,4,确定带长度,Lp,中心距,a,计算所需带长,L,0,L,0,2a,0,D,1,D,2,p,2,D,2,D,1,2,4a,0,确定带的节线长度,L,p,和

3、内周长度,L,i,查表选取,确定实际中心距,a,aa,0,L,p,L,0,2,5,验算小带轮包角,a1,a,1,180,57.3,D,2,D,1,a,Z,P,s,P,0,D,P,0,K,q,K,a,K,L,查表：皮带单根功率,P,0,内插值计算,P,0,2.81,kW,查表：皮带弯曲影响系数,K,b,K,b,2.65,10,3,查表：皮带传动比系数,K,i,K,i,1.12,1,K,i,D,P,0,K,b,n,1,2.65,10,3,1440,1,1,1.12,6,确定三角带根数,Z,查表：化纤结构胶带材质系数,K,q,查表：皮带长度系数,K,L,K,L,0.95,故,K,q,0.9,查表：皮

4、带包角系数,K,a,内插值计算,K,a,0.939,Z,P,s,P,0,D,P,0,K,q,K,a,K,L,课程内容,目录,计算单根三角带的张力,F,0,查表：皮带单位长度质量,q,q =0.17,kg/m,F,0,1,qv,2,1000P,s,2Zv,2.5,K,a,作用在轴上的作用力,Q,Q = 2.Z.F,0,sin,a,2,7,计算带传动作用在轴上的力,Q,课程内容,目录,查表,f=5,mm,m=15,mm,e=20,0.4,mm,g=12.5,mm,d,7.5,mm,b=17.4,mm,e,g,b,j,d,f,D,e,D,m,B,B,Z-1,e+2g=65,mm,D= 355,mm,

5、D,e,D+2f =365,mm,采用孔板结构,ZG45,铸造，查表,轴孔径,d= 32,mm,孔毂径,d,1,2d=64,mm,缘毂径,D,0,D,e,2,m,d,320,mm,其他结构尺寸,查图册,孔毂长,L=64,mm,8,带轮结构设计,课程内容,目录,齿轮材料选择，确定许用应力,1,材料选择,小齿轮选用,45,钢调质,HB,1,220,大齿轮选用,45,钢正火,HB,2,190,查表,s,Hlim1,520,N/mm,2,s,Hlim2,500,N/mm,2,s,Flim1,190,N/mm,2,s,Flim2,175,N/mm,2,1,齿轮传动设计,二）减速器内传动零件设计,课程内容

6、,目录,2,许用应力计算,计算,472.73,N/mm,2,齿面接触安全因数,S,H,1.1,齿根弯曲安全因数,S,F,1.4,454.55,N/mm,2,135.71,N/mm,2,125,N/mm,2,s,H,1,s,Hlim1,S,H,520,1.1,s,H,2,s,Hlim2,S,H,500,1.1,s,F,1,s,Flim1,S,F,190,1.4,s,F,2,s,Flim2,S,F,175,1.4,课程内容,目录,二,按齿面接触强度进行设计计算,1,初选载荷系数,K,载荷不大，转速不高,K=1.2,2,选择齿宽系数,f,a,f,a,0.4,3,计算中心距,a,a,48.5,i,1,

7、KT,1,f,a,i,s,H,2,3,48.5,4.556,1,1.292230,0.4,4.556,454.55,2,3,179.165,mm,取,a=200,mm,课程内容,目录,4,选择齿数,Z,1,Z,2,模数,m,取,Z,1,18,Z,2,82,m= = =4mm,2a,Z,1,Z,2,2,200,18 +82,5,确定实际载荷系数,K,因选择电机时已计入过载系数，故取,K,1,1,齿轮圆周速度,v=,p,d,1,n,1,60,1000,p,mZ,1,n,1,60,1000,p,4,18,546.718,60,1000,=2.061,m/s,课程内容,目录,5,确定实际载荷系数,K,

8、K,1,1,按,8,级精度查动载系数,K,2,1.05,齿宽系数,F,d,F,d,0.5,i+1,F,a,0.5,4.556+1,0.4,1.111,查表得荷载集中系数,K,3,1.061,故,K=K,1,K,2,K,3,1.114,由于,KK,1.2,且二者比较接近，无须重新,计算中心距,6,计算齿轮宽度,b,b,f,a,a=0.4,200=80,mm,课程内容,目录,三,齿根弯曲疲劳强度校核,查表,y,F1,3.02,y,F2,2.23,s,F1,2KT,1,y,F1,bm,2,Z,1,26.935,N/mm,2,s,F,1,135.71,N/mm,2,2,1.114,92230,3.02

9、,80,4,2,18,s,F2,s,F1,y,F2,y,F1,26.935,2.23,3.02,19.889,N/mm,2,s,F,2,125,N/mm,2,弯曲强度足够,课程内容,目录,四,齿轮传动几何尺寸计算,模数,m=4,mm,齿数,Z,1,18,Z,2,82,压力角,a,20,分度圆直径,d,1,m.Z,1,72,mm,d,2,m.Z,2,328,mm,中心距,a=200,mm,齿宽,b,1,90,mm,b,2,80,mm,顶圆直径,d,a1,80,mm,d,a2,336,mm,根圆直径,d,f1,62,mm,d,f2,318,mm,课程内容,目录,五,齿轮结构设计,小齿轮设计采用齿轴

10、结构,在装配图中完成,大齿轮采用幅板式锻造齿轮，结构如下,代号,名称,结构尺寸计算公式及数据,结果,mm,d,轴孔径,取,d,60,60,D,1,毂径,D,1,1.6d,1.6,60,96,L,毂孔长,L=b,80,80,n,倒角,n=0.5m,0.5,4,2,D,0,轮缘径,D,0,d,f2,2,d,0,318,2,12,294,D,2,板孔距,D,2,0.5(D,0,D,1,0.5,294+96,195,d,1,板孔径,按结构需要取,d,1,50,50,c,板厚,c=0.3b,0.3,80,24,r,圆角,r=0.4c,0.5,24,12,课程内容,目录,4,f,50,f,3,3,6,f,

11、3,2,8,f,9,6,80,f,6,0,24,课程内容,目录,课程内容,目录,高速轴的设计,一,轴的材料选择,查表,选用,45,钢，调质处理,HB=220,s,b,650,N/mm,2,s,s,350,N/mm,2,s,1,300,N/mm,2,t,1,155,N/mm,2,二,轴径的初步估算,查表,C=110,及,P=5.28,kW,n=546.718,r/min,d,C,P,n,3,110,23.425,mm,5.28,546.718,3,三,轴径的结构设计,与装配草图同步,取轴与带轮孔径,d,1,32,mm,轴各段直径,d,2,38,mm,d,3,40,mm,d,4,49,mm,课程内

12、容,目录,d,1,32,d,2,38,d,3,40,d,4,49,d= 72,b,1,9,0,D,1,1,0,D,2,2,0,高速轴,径向祥图,d,1,带轮孔径为依据,d,2,定位轴肩,h,d,3,以选择轴承公径,d,4,轴承定位轴肩,h,d,小齿轮节圆,轴承,0308,D,2,2,0,d,3,40,d,4,49,课程内容,目录,d=72,D,2,2,0,b,1,9,0,D,1,1,0,D,1,1,0,D,2,2,0,l,1,5,1,8,l,1,6,4,l,2,5,3,B,2,3,l,c,3,0,H,l,0,1,9,6,5,9,7,l,1,带轮孔径长为依据,l,2,9,3,2,9,0,l,0,

13、2,7,6,5,l,0,3,7,6,5,l,2,绘图,计算,l,c,端盖长度,查表,B,轴承宽度,0308,D,1,箱内距离,b,齿轮宽度,D,1,箱内轴承端面,l,箱外距离,H,端盖螺头高,l,0,计算受力点距离,l,轴长度,高速轴,轴向祥图,课程内容,目录,D,B,C,A,四,按弯扭合成进行轴的强度校核,1,绘制轴的计算简图,M,e,Q,F,t1,F,r1,97,76.5,76.5,2,计算轴的作用力,圆周力,F,t1,F,t1,2T,1,d,1,2,92230,72,2561.944,N,径向力,F,r1,F,r1,F,t1,tan,20,932.47,N,带传动作用在轴上的力,Q,Q

14、= 1213.273,N,课程内容,目录,D,B,C,A,四,按弯扭合成进行轴的强度校核,3,求支座反力,M,e,Q,F,t1,F,r1,R,Bz,R,Bx,R,Az,R,Ax,97,76.5,76.5,z,y,x,水平面,R,Ax,R,Bx,R,Ax,R,Bx,F,t1,R,Bx,R,Ax,F,t1,2,1280.972,N,垂直面,R,Az,R,Bz,Q,F,r1,R,Bz,R,Az,R,Az,932.471,76.5+1213.273,97+153,153,2448.708,N,R,Bz,1213.273,97,932.472,76.5,153,302.964,N,验算,Q+F,r1,R

15、,Bx,R,Az,代入数值，无误,课程内容,目录,D,B,C,A,四,按弯扭合成进行轴的强度校核,4,作弯矩图,M,e,Q,F,t1,F,r1,R,Bz,R,Bx,R,Az,R,Ax,97,76.5,76.5,z,y,x,F,t1,R,Bx,R,Ax,Q,F,r1,R,Bz,R,Az,M,Cx,97994.358,N.mm,M,Cz,23176.704,N.mm,M,Az,117687.48,N.mm,M,Dx,M,Ax,M,Bx,0,M,Dz,M,Bz,0,课程内容,目录,D,B,C,A,四,按弯扭合成进行轴的强度校核,4,作弯矩图合成弯矩,M,e,Q,F,t1,F,r1,R,Bz,R,Bx

16、,R,Az,R,Ax,z,y,x,M,D,M,B,0,M,A,M,2,Ax,M,2,Az,117687.48,N.mm,M,C,M,2,Cx,M,2,Cz,100697.834,N.mm,5,作扭矩图,查表得,a,0.59,a,T,1,0.59,92230=54415.7,N.mm,97994.358,117687.48,117687.48,100697.834,23176.704,54415.7,课程内容,目录,D,B,C,A,四,按弯扭合成进行轴的强度校核,6,作当量弯矩图,M,e,Q,F,t1,F,r1,R,Bz,R,Bx,R,Az,R,Ax,z,y,x,117687.48,100697

17、.834,54415.7,M,d,M,c,2,a,T,1,2,由,M,dD,aT,1,54415.7,N.mm,得,M,dA,M,A,2,a,T,1,2,129658.83,N.mm,M,dC,左,M,C,2,a,T,1,2,114460.134,N.mm,M,dC,右,M,C,2,a,T,1,2,100697.843,N.mm,M,dB,0,129658.83,54415.7,114460.134,100697.843,课程内容,目录,D,B,C,A,四,按弯扭合成进行轴的强度校核,7,校核轴的强度,M,e,Q,F,t1,F,r1,R,Bz,R,Bx,R,Az,R,Ax,z,y,x,1176

18、87.48,100697.834,54415.7,129658.83,54415.7,114460.134,100697.843,查表得许用弯曲应力,s,1,b,60,N/mm,2,A,点处当量弯矩最大，应力为,20.259,N.mm,2,s,1,b,s,dA,M,dA,0.1d,3,1,129658.83,0.1,40,3,D,点处轴径最小，应力为,s,dA,M,dD,0.1d,3,D,54415.7,0.1,32,3,16.606,N.mm,2,s,1,b,高速轴强度足够,课程内容,目录,低速轴的设计,一,轴的材料选择,二,轴径的初步估算,三,轴径的结构设计,与装配草图同步,同高速轴,选用

19、,45,钢，调质处理,HB=220,s,b,650,N/mm,2,查表,C=110,及,P,2,5.07,kW,n,2,120,r/min,d,C,P,2,n,2,3,110,38.312,mm,5.07,120,3,取轴为联轴器孔径尺寸,d,1,40,mm,轴各段直径,d,2,47,mm,d,3,50,mm,d,4,60,mm,课程内容,目录,d,1,40,d,2,48,d,3,50,d,4,60,d,5,70,b,8,0,D,2,2,5,D,2,2,5,D,1,1,5,d,1,联轴器孔径为依据,d,2,非定位轴肩,h,1,d,3,以选择轴承公径,d,4,大齿轮孔径,预选,b,大齿轮宽度,轴

20、承,0310,d,5,定位轴肩,h,轴套尺寸,绘图确定,高低速轴,径向祥图,d,4,60,d,3,50,课程内容,目录,b,8,0,D,2,2,5,D,2,2,5,D,1,1,5,2,7,B,b,0,1,5,l,0,1,7,8,5,l,0,2,7,8,5,l,2,4,9,l,1,9,0,l,3,3,2,l,1,联轴器孔长为依据,l,2,绘图,计算,l,c,端盖长度,查表,26,D,1,兼顾高速轴,b,齿轮宽度,D,2,箱内轴承端面,H,端盖螺头高,l,0,计算受力点距离,l,轴长度,l,0,1,0,7,5,B,轴承宽度,0310,l,c,H,b,0,定位轴肩宽度,轴承,0310,套筒,绘图确定

21、,l,3,2,3,3,2,0,l,3,绘图,计算,低速轴,轴向祥图,课程内容,目录,四,按弯扭合成进行轴的强度校核,1,绘制轴的计算简图,107.5,78.5,78.5,B,C,A,D,T,2,F,t2,F,r2,2,计算轴的作用力,圆周力,F,t2,径向力,F,r2,F,r2,F,t2,932.47,N,F,t2,F,t1,2561.94,N,低速轴上的力偶矩,T,2,T,2,403488,N.mm,课程内容,目录,四,按弯扭合成进行轴的强度校核,3,求支座反力,107.5,78.5,78.5,B,C,A,D,T,2,F,t2,F,r2,z,y,x,R,Bz,R,Bx,R,Az,R,Ax,水

22、平面,R,Ax,R,Bx,R,Ax,R,Bx,F,t2,2,1280.972,N,垂直面,R,Az,R,Bz,R,Az,R,Bz,F,r2,2,466.236,N,F,t2,R,Bx,R,Ax,F,r2,R,Bz,R,Az,课程内容,目录,四,按弯扭合成进行轴的强度校核,4,作弯矩图,107.5,78.5,78.5,B,C,A,D,T,2,F,t2,F,r2,z,y,x,R,Bz,R,Bx,R,Az,R,Ax,M,Ax,M,Bx,0,F,t2,R,Bx,R,Ax,F,r2,R,Bz,R,Az,M,Cx,100556.3,N.mm,M,Az,M,Bz,0,M,Cz,36599.526,N.mm,

23、合成弯矩,M,A,M,B,0,M,C,M,2,Cx,M,2,Cz,107009.788,N.mm,课程内容,目录,四,按弯扭合成进行轴的强度校核,5,作扭矩图,107.5,78.5,78.5,B,C,A,D,T,2,F,t2,F,r2,z,y,x,R,Bz,R,Bx,R,Az,R,Ax,查表得,a,0.59,a,T,2,0.59,403488=238057.92,N.mm,100556.3,36599.526,107009.788,238057.92,6,作当量弯矩图,M,dA,0,M,dD,aT,2,2380577.92,N.mm,M,dC,左,M,C,2,a,T,2,2,M,C,10700

24、9.788,N.mm,M,dC,右,M,C,2,a,T,2,2,261003.195,N.mm,107009.788,261003.195,238057.92,课程内容,目录,四,按弯扭合成进行轴的强度校核,7,校核轴强度,107.5,78.5,78.5,B,C,A,D,T,2,F,t2,F,r2,z,y,x,R,Bz,R,Bx,R,Az,R,Ax,100556.3,36599.526,107009.788,238057.92,107009.788,261003.195,238057.92,s,1,b,60,N/mm,2,C,点处当量弯矩最大，应力为,12.083,N.mm,2,s,1,b,s

25、,dC,M,dA,右,0.1d,3,c,261003.195,0.1,60,3,D,点处轴径最小，应力为,s,dA,M,dD,0.1d,3,D,238057.92,0.1,40,3,37.197,N.mm,2,s,1,b,低速轴强度足够,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A,D,z,y,x,107009.788,238057.92,C,C,键槽尺寸,C,截面,18,11,t=7,mm,C,截面校核,抗弯截面系数,W,p,d,3,32,bt,d,t,2,2d,p,60,3,32,18,7,60,7,2,2,60,18650.55,mm,3,抗扭截

26、面系数,W,t,p,d,3,16,bt,d,t,2,2d,p,60,3,16,18,7,60,7,2,2,60,429050.55,mm,3,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A,D,z,y,x,107009.788,238057.92,C,C,C,截面校核,弯曲正应力,s,M,Cmax,W,107009.788,18650.55,5. 737,N/mm,2,扭转切应力,t,T,Cmax,W,t,238057.92,429050.55,0.55,N/mm,2,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A

27、,D,z,y,x,107009.788,238057.92,C,C,C,截面校核,计算应力幅,s,a,s,max,s,min,2,s,s,2,5. 737,N/mm,2,t,a,t,max,t,min,2,t,0,2,0.275,N/mm,2,计算平均应力,s,m,s,max,s,min,2,s,s,2,0,N/mm,2,t,m,t,max,t,min,2,t,0,2,0.275,N/mm,2,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A,D,z,y,x,107009.788,238057.92,C,C,C,截面校核,查表得：有效应力集中系数,按过盈配

28、合，内插值计算,K,s,2.65,K,t,1.89,查表得：尺寸系数,e,s,0.81,e,t,0.70,查表得：表面质量系数,按,R,a,1.6,b,0.93,查表得：应力折算系数,y,s,0.1,y,t,0.05,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A,D,z,y,x,C,C,C,截面校核,计算安全系数,n,n,s,K,s,be,s,s,1,s,a,y,s,s,m,300,5.737+0.1,0,2.65,0.93,0.81,14. 9,n,t,K,t,be,t,t,1,t,max,y,t,t,m,155,0.275+0.05,0.275,1

29、.89,0.93,0.7,191,n=,n,s,n,t,n,2,s,n,2,t,安全系数,14. 85,n,1.31.5,足够安全,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A,D,z,y,x,107009.788,238057.92,D,D,键槽尺寸,D,截面,12,8,t=5,mm,D,截面校核,抗弯截面系数,W,p,d,3,32,bt,d,t,2,2d,p,40,3,32,12,5,40,5,2,2,40,4481.25,mm,3,抗扭截面系数,W,t,p,d,3,16,bt,d,t,2,2d,p,40,3,16,12,5,40,5,2,2,40

30、,11218.25,mm,3,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A,D,z,y,x,107009.788,238057.92,C,C,D,截面校核,弯曲正应力,s,M,Dmax,W,0,扭转切应力,t,T,Dmax,W,t,238057.92,11281.25,21.22,N/mm,2,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A,D,z,y,x,107009.788,238057.92,C,C,D,截面校核,计算应力幅,t,a,t,max,t,min,2,t,0,2,10.61,N/mm,2,计算平均

31、应力,t,m,t,max,t,min,2,t,0,2,10.61,N/mm,2,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A,D,z,y,x,107009.788,238057.92,C,C,D,截面校核,查表得：有效应力集中系数,按过盈配合，内插值计算,K,t,1.89,查表得：尺寸系数,e,t,0.88,查表得：表面质量系数,按,R,a,1.6,b,0.93,查表得：应力折算系数,y,t,0.05,课程内容,目录,五,按疲劳强度进行精确校核,107.5,78.5,78.5,B,C,A,D,z,y,x,C,C,D,截面校核,计算安全系数,n,n,t,

32、K,t,be,t,t,1,t,max,y,t,t,m,155,10.61+0.05,10.61,1.89,0.93,0.88,6.19,安全系数,n = n,t,6.19,n,1.31.5,足够安全,课程内容,目录,课程内容,目录,高速轴滚动轴承的选择,一,轴承所承受的载荷,由于轴承仅受径向载荷作用,选用单列向心球轴承,0308,因,R,A,R,B,故取,R,A,2763.523,N,计算,R,A,R,2,AX,R,2,AZ,1280.972,2,2448.708,2,2763.523,N,R,B,R,2,BX,R,2,BZ,1280.972,2,302.964,2,1316.312,N,二,

33、轴承的当量载荷,查表：轴承的当量载荷为,P=R=2763.523,N,课程内容,目录,三,轴承型号确定,查表：取轴承的寿命为,L,h,10000,h,查表得,f,h,2.71,f,F,1.5,由轴转速,n,1,546.718,r/min,查表,f,n,0.394,内插值计算,f,t,1,工作温度,100,由此得,C,f,P,f,h,f,F,f,n,f,t,2.71,1.5,0.394,1,2763.523=28511.982,N,查表得,308,型号轴承的,C=32000,N,满足,C,j,C,的要求，故高速轴轴承选用合适,额定载荷,课程内容,目录,低速轴滚动轴承的选择,一,轴承所承受的载荷,

34、同高速轴，轴承仅受径向载荷作,用，选用单列向心球轴承,0310,因,R,A,R,B,取,R=2763.523,N,计算,R,A,R,2,AX,R,2,AZ,1280.972,2,466.236,2,1363.182,N,R,B,R,2,BX,R,2,BZ,1280.972,2,466.236,2,1363.182,N,二,轴承的当量载荷,查表：轴承的当量载荷为,P=R=R,A,R,B,1363.182,N,课程内容,目录,三,轴承型号确定,查表：取轴承的寿命为,L,h,10000,h,查表得,f,h,2.71,f,F,1.5,由轴转速,n,2,120,r/min,查表,f,n,0.652,f,

35、t,1,工作温度,100,由此得,C,f,P,f,h,f,F,f,n,f,t,2.71,1.5,0.652,1,1363.182=8498.98,N,所需,C,值甚小，但根据低速轴结构要求，必,须保证轴承内径,d=50,mm,因此改选,210,型轴承,C=27500,N,轴承,B=20,mm,D=90,mm,低速轴跨度改变为,l=150,mm,小于初,定的,l=157,mm,轴,强度足够,课程内容,目录,课程内容,目录,高速轴与带轮联结键,一,键的型号确定,带和轴配合选钩头楔型键,b,h,10,8,取键长,L,80,mm,键的工作长度,l,L,b+h,62,mm,二,键的强度计算,键的材料,45,号钢，带轮为铸钢,查表得键联结的许用比压为,p,100120,N/mm,2,钢对铸钢的摩擦系数取,f,0.15,工作比压,12T,6l,b+6fd,p =,12,92230,6,62,10+6,0.15,32,76.679,N/mm