二级减速器设计自动计算参数

1、,输入信息,运输机工作轴转矩T（N*m）,900,运输带工作拉力F（N）,5625,手动输入,运输带工作速度 v（m/s）,0.78,运输带工作速度v（m/s）,0.78,自动读取/计算,卷筒直径 D（mm）,320,卷筒直径 D（mm）,320,查表,电动机选择,运输机工作轴转矩T（N*m）,900,运输带工作拉力F（N）,5625,运输带工作速度 v（m/s）,0.78,运输带工作速度v（m/s）,0.78,卷筒直径 D（mm）,320,卷筒直径 D（mm）,320,查表12-4 机械传动和轴承效率概略值,滚筒效率w,0.96,工作机输入功率Pw (kw),4.5703125, V带传动效

2、率1,0.95,齿轮副效率2,0.97,滚动轴承效率3,0.98,弹性联轴器效率4,0.99,轴承效率前提圆锥滚子,传动装置总效率a,0.832876283,重复计算,电动机所需提供功率Pd (kw),5.48738461,工作机滚筒转速nw r/min,46.55282165,查表2-2 传动比常用值,总传动比Min,16,总传动比Max,160,电机转速n电机min r/min,744.8451464,电机转速n电机max r/min,7448.451464,确定电动机,电动机满载转速nmax r/min,1460,选取Y160M-411kw,传动比,传动装置总传动比ia,31.36222

3、356,总传动比=带传动比*减速器传动比,减速器传动比=i1*i2,指定V带传动比iD,2,减速器传动比i,15.68111178,根据公式确定两个齿轮副传动比,高速级齿轮传动比i1,4.68546225,低速级齿轮传动比i2,3.34675875,各轴转速与功率,高速轴转速n1 r/min,730,中间轴转速n2 r/min,155.8010632,低速轴转速n3 r/min,46.55282165,滚筒轴转速nw r/min,46.55282165,高速轴输入功率P1 (kw),5.21301538,中间轴输入功率P2 (kw),4.95549242,低速轴输入功率P3 (kw),4.71

4、0691095,滚筒轴输入功率Pw (kw),4.5703125,电动机轴输入转矩Td (N*m),35.89350892,高速轴输入转矩T1 (N*m),68.19766696,中间轴输入转矩T2 (N*m),303.7524369,低速轴输入转矩T3 (N*m),966.3667713,滚筒轴输入转矩Tw (N*m),937.5690416,V带传动设计,Pd,5.48738461,Ka,1.1,Pca,6.036123072,V带选型表8-8，8-7，8-9（机械设计）,电动机转速n电动机 (r/min),1460,初选小带轮直径dd1 (mm),120,大带轮直径dd2 (mm),24

5、0,查表大带轮直径dd2 (mm),250,带速v (m/s),9.1688,带中心距最小值 (mm),259,带中心距最大值 (mm),740,初定中心距 a0 (mm),500,计算带长Ld0 (mm),1589.35,查表确定带基准长度ld (mm),1640,带长修正系数kl,0.99,带的实际中心距a,525.325,包角计算1,165.8202065,包角修正系数k,0.96,单根普通V带额定功率的增量p0,0.17,带长修正系数kl,0.99,单根普通V带基本额定功率p0,2.2,带的根数 z,2.679805736,确定V带根数,3,带选型q,0.105,带的初拉力F0,184

6、.8396505,压轴力Fp,1100.557886,高速级斜齿圆柱齿轮,高速轴输入功率P1 (kw),5.21301538,小齿轮转速(r/min),730,传动比i1,4.68546225,输入转矩T1 (N*mm),68197.66696,预选小齿轮齿数z1,24,大齿轮齿数z2,113,初选螺旋角,14,压力角,20,试选载荷系数Kht,1.3,选取区域系数ZH,2.433,材料弹性影响系数zE,189.8,han,1,t,20.56170535,at1,29.97411909,at2,23.00267302,1.658936063,d,1,1.904725669,z,0.664946

7、696,螺旋角系数Z,0.985035901,小齿轮接触疲劳极限Hlim 小 (MPA),600,大齿轮接触疲劳极限Hlim 大 (MPA),550,计算应力循环次数,安全系数S,1,jlh,24000,N1,1051200000,N2,224353531,接触疲劳强度KHN1,0.93,接触疲劳强度KHN2,0.95,u,4.68546225,H小,558,H大,522.5,齿轮许用应力H (MPA),522.5,试算小齿轮分度圆直径dlt,41.62101596,调整小齿轮分度圆直径,圆周速度v0,1.590868022,齿宽b,41.62101596,计算实际载荷系数KH,查表使用系数K

8、A,1.25,查表动载系数KV,1.06,根据8级精度，齿轮线速度kv=,1.590868022齿轮圆周力Ft1 (N),3277.078437,KAFt1/b,98.42018392,KAFt1/b,= (mm),2.144675276,按齿根弯曲强度设计,试选载荷系数KFt,1.3,b,13.1400591,v,1.749341947,弯曲疲劳强度重合度系数Y,0.678732645,螺旋角系数Y,0.777782005,计算YfaYsa/F,当量齿数Zv1,26.27234788,当量齿数Zv2,123.6989713,查表齿形系数YFa1,2.65,查表齿形系数YFa2,2.16,查表

9、应力修正系数Ysa1,1.6,查表应力修正系数Ysa2,1.81,查表齿根弯曲疲劳极限F lim 1 (MPA),500,查表齿根弯曲疲劳极限F lim 2 (MPA),380,弯曲疲劳寿命系数KFN1,0.9,弯曲疲劳寿命系数KFN2,0.95,弯曲疲劳安全系数S,1.4,【F】1 MPA,321.4285714,【F】2 MPA,257.8571429,【YfaYsa/F】1,0.013191111,【YfaYsa/F】2,0.015161884,【YfaYsa/F】,0.015161884,试算齿轮模数mn= (mm),1.323770817,调整齿轮模数,d1 (mm),32.7431

10、0991,圆周速度v (m/s),1.251530393,齿宽b (mm),32.74310991,齿高h (mm),2.978484339,宽高比b/h,10.99321205,计算实际载荷系数KF,查表动载系数Kv,1.04,齿间载荷分配系数kF,1.4,查表使用系数KA,1.25,齿向载荷分布系数KF,1.44,载荷系数KF,2.6208,按实际载荷系数计算的齿轮模数mn (mm),1.672282501,确认模数取值,模数mn (mm),2,分度圆直径d1 (mm),53.04795768,小齿轮齿数z1,25.73610331,z1,26,大齿轮齿数z2,121.8220185,z2

11、,121,中心距a (mm),151.5002035,调整后中心距a (mm),155,根据调整后中心距修正螺旋角,修正后螺旋角,18.48854092,齿宽b,54.82993197,小齿轮分度圆直径d1,54.82993197,b1 (mm),60,大齿轮分度圆直径d2,255.170068,b2 (mm),55,齿轮校核,齿面接触强度校核,KA,1.25,KV,1.08,KH,1.4,KH,1.456,KH,2.75184,区域系数ZH,2.31,弹性影响系数zE,189.8,螺旋角系数z,0.9738,重合度系数z,0.5553,齿面接触疲劳强度,394.0915164,与之前强度上限

12、对比,552Mpa,齿根弯曲疲劳强度校核,KA,1.25,KV,1.08,KF,1.4,KF,1.456,KF,2.75184,齿形系数YFa1,2.64,齿形系数YFa2,2.17,应力修正系数Ysa1,1.63,应力修正系数Ysa2,1.81,重合度系数Y,0.673,螺旋角系数Y,0.5736,小齿轮齿根弯曲疲劳强度F1,103.6986305,大齿轮齿根弯曲疲劳强度F2,94.6498213,与之前强度上限对比,258Mpa,低速级直齿圆柱齿轮传动设计,中间轴输入功率p /KW,4.95549242,中间轴转速r/min,155.8010632,传动比,3.34675875,输入转矩N

13、*mm,303752.4369,小齿轮齿数预选（20-40）,28,参考大齿轮齿数,93.70924499,大齿轮齿数,93,齿轮压力角,20,按齿面接触强度设计,kHt,1.3,小齿轮转矩N*mm,303752.4369,弹性影响系数ZE,189.8,齿宽系数d,1,区域系数ZH,2.4, a1,28.71188439, a2,23.08711365, ,1.741131938,Z ,0.867730385,小齿轮接触疲劳极限Hlim 小 (MPA),600,大齿轮接触疲劳极限Hlim 大 (MPA),420,计算应力循环次数,安全系数S,1,jlh,24000,N1,224353531,N

14、2,67036063.17,接触疲劳强度KHN1,0.95,接触疲劳强度KHN2,0.98,u,3.34675875,H小,570,H大,411.6,齿轮许用应力H (MPA),411.6,试算小齿轮分度圆直径dlt,98.16485031,调整小齿轮分度圆直径,圆周速度v0,0.8008018,齿宽b,98.16485031,计算实际载荷系数KH,查表使用系数KA,1.25,查表动载系数KV,1.04,齿轮圆周力Ft1 (N),6188.619163,KAFt1/b,78.80390923,KAFt1/b,= (mm),4.234542714,按齿根弯曲强度设计,试选载荷系数KFt,1.3,

15、b, ,1.741131938,弯曲疲劳强度重合度系数Y,0.68075426,计算YfaYsa/F,查表齿形系数YFa1,2.64,查表齿形系数YFa2,2.18,查表应力修正系数Ysa1,1.62,查表应力修正系数Ysa2,1.8,查表齿根弯曲疲劳极限F lim 1 (MPA),420,查表齿根弯曲疲劳极限F lim 2 (MPA),320,弯曲疲劳寿命系数KFN1,0.91,弯曲疲劳寿命系数KFN2,0.93,弯曲疲劳安全系数S,1.4,【F】1 MPA,273,【F】2 MPA,212.5714286,【YfaYsa/F】1,0.015665934,【YfaYsa/F】2,0.0184

16、59677,【YfaYsa/F】,0.018459677,试算齿轮模数mn= (mm),2.33057908,调整齿轮模数,d1 (mm),65.25621425,圆周速度v (m/s),0.532342215,齿宽b (mm),65.25621425,齿高h (mm),5.243802931,宽高比b/h,12.44444444,计算实际载荷系数KF,查表动载系数Kv,1.03,齿间载荷分配系数kF,1.1,KA,1.25,齿向载荷分布系数KH,1.458,载荷系数KF,2.0648925,按实际载荷系数计算的齿轮模数mn (mm),2.719246273,确认模数取值,模数mn (mm),

17、3,分度圆直径d1 (mm),118.567196,小齿轮齿数z1,39.52239866,z1,41,大齿轮齿数z2,137.2171087,z2,137,调整后d1,123,调整后d2,411,中心距a (mm),267,齿轮宽度b1,130,齿轮宽度b2,123,齿轮宽度b1,127,齿轮宽度b2,120,d,1.056910569,齿轮校核,齿面接触强度校核,KA,1.25,KV,1.04,KH,1.2,KH,1.475,KH,2.301,区域系数ZH,2.5,弹性影响系数zE,189.8,重合度系数z,0.856,齿面接触疲劳强度,390.244644,与之前强度上限对比,411.6

18、,齿根弯曲疲劳强度校核,KA,1.25,KV,1.04,KF,1.2,KF,1.475,KF,2.301,齿形系数YFa1,2.45,齿形系数YFa2,2.18,应力修正系数Ysa1,1.65,应力修正系数Ysa2,1.8,重合度系数Y,0.68075426,螺旋角系数Y,小齿轮齿根弯曲疲劳强度F1,80.19311127,大齿轮齿根弯曲疲劳强度F2,77.84236701,与之前强度上限对比,273,212,运输带速度误差校核,高速级传动比i1,4.653846154,低速级传动比i2,3.341463415,V带传动比iD,2,总传动比ia,31.10131332,电动机转速,1460,传

19、输带转速n,46.94335525,传输带速度v,0.786543453,输送带速度误差 (%),-0.838904257,润滑选择,轴2大齿轮线速度,2.081607104,脂润滑,结果输出,高速级斜齿轮,模数,2,螺旋角,18.48854092,大齿轮齿数,121,小齿轮齿数,26,大齿轮分度圆,255.170068,小齿轮分度圆,54.82993197,大齿轮齿宽,55,小齿轮齿宽,60,低速级直齿轮,模数,3,压力角,20,大齿轮齿数,137,小齿轮齿数,41,大齿轮分度圆,411,小齿轮分度圆,123,大齿轮齿宽,120,小齿轮齿宽,127,高速轴转速n1 r/min,730,中间轴

20、转速n2 r/min,166.8093726,低速轴转速n3 r/min,53.36371712,滚筒轴转速nw r/min,53.36371712,高速轴输入功率P1 (kw),9.959506508,中间轴输入功率P2 (kw),9.467506886,低速轴输入功率P3 (kw),8.999812046,滚筒轴输入功率Pw (kw),8.731617647,电动机轴输入转矩Td (N*m),68.57482851,高速轴输入转矩T1 (N*m),130.2921742,中间轴输入转矩T2 (N*m),542.0240443,低速轴输入转矩T3 (N*m),1610.611286,滚筒轴输入转矩Tw (N*m),1562.615069,