机械设计课程设计二级减速器(详细版)

1、机械设计课程设计计算说明书题目设计带式运输机传动装置两级圆锥- 圆柱齿轮减速器专业班级机械设计制造及其自动化学号xxxxx学生姓名xxx指导教师xxxxxxxxxxxxxxx 年 x 月 x 日西安文理学院机械设计课程设计任务书学生姓名xx专业班级机械设计制造及其自动化专业xx 级x 班学号08102080124指导教师xxxxxxxxx职称教 研 室机电系机电教研室题目设计带式运输机传动装置编号Z-1传动系统图：图一原始数据：运输带工作拉力 F / N运输带工作速度 v /( m s 1 )卷筒直径 D / mm25001.4250工作条件：连续单向运转，工作时有轻微振动，小批量生产，单班制

2、工作，使用期限 8 年，运输带速度允许误差为± 5%要求完成：1. 减速器装配图 1 张（ A2）。2. 零件工作图 2 张（齿轮和轴）。3. 设计说明书 1 份， 6000-8000 字。开始日期 2010 年 12 月 06日完成日期 20010 年 12月 31日目录1 选择电动机······ ······· ············

3、;·· ··············11.1 电动机类型和结构型式·······························&

4、#183;··································11.2 电动机容量·············

5、83;·················································

6、83;···········11.3 电动机的转速····································

7、3;······································21.4 电动机的技术数据和外形,安装尺寸········&

8、#183;···········································22 计算传动装置总传动比和分配各级传动比··

9、3;· ·····················32.1 传动装置总传动比·························&#

10、183;············································32.2 分配各级传动比···&#

11、183;·················································&#

12、183;··················33 计算传动装置的运动和动力参数··· ···················· ·····&

13、#183;··43.1 各轴转速 ·············································

14、83;································43.2 各轴输入功率···············

15、3;·················································

16、3;·········43.3 各轴转矩 ·······································

17、·······································44 传动件的设计计算·········&

18、#183;······· ·····················64.1圆锥直齿轮设计···················&

19、#183;·················································&

20、#183;··64.1.1选定齿轮齿轮类型、精度等级、材料及齿数···········································

21、····························64.1.2按齿面接触强度设计···················

22、83;·················································

23、83;································64.1.3校核齿根弯曲疲劳强度···············

24、;··················································

25、;··································84.1.4几何尺寸计算 ·············

26、3;·················································

27、3;···············································94.2圆柱直齿齿轮设计

28、3;·················································

29、3;·················104.2.1选定齿轮精度等级、材料及齿数·····························&

30、#183;·················································&

31、#183;······104.2.2按齿面接触强度设计由设计········································

32、··················································

33、··104.2.3按齿根弯曲疲劳强度设计·············································

34、··················································

35、105 轴的设计计算···················· ·····················155.1输入轴设计·····

36、83;·················································

37、83;·················155.2中间轴设计·······························

38、;··········································215.3输出轴设计······&

39、#183;·················································&

40、#183;················266 滚动轴承的选择及校核计算······························

41、83;···326.1输入轴滚动轴承计算············································&

42、#183;·····················327 键联接的选择及校核计算·························

43、3;········337.1输入轴键计算········································

44、;·································337.2中间轴键计算···············

45、··················································

46、········337.3 输出轴键计算········································

47、·································338.联轴器的选择及校核计算··············

48、83;···················348.1 各种联轴器的比较····························&

49、#183;·······································348.1.1 刚性联轴器········

50、··················································

51、··················································

52、···348.1.2 弹性元件的挠性联轴器············································

53、··················································

54、····348.2联轴器的选择 ············································

55、·····························348.3联轴器的校核计算 ··················

56、3;·················································359.

57、减速器附件的选择················· ····················369.1 视孔盖和窥视孔·········&#

58、183;·················································&#

59、183;··········369.2 放油孔与螺塞·····································&#

60、183;···································369.3 油标 ·············

61、;··················································

62、;···············369.4 通气孔 ·································&

63、#183;···········································369.5 起盖螺钉 ····&#

64、183;·················································&#

65、183;·····················369.6 定位销 ··························

66、3;·················································

67、3;369.7 吊环 ················································&

68、#183;·····························3710.润滑与密封······ ······· ·····&

69、#183;······················3811.铸铁直齿锥齿轮减速器箱体结构尺寸的确定·······················3

70、912.设计小结······· ······· ·············· ·············4013.参考文献·····

71、3;· ······· ·············· ·············41设计计算及说明结果1 选择电动机计算驱动卷筒的转速60 1000 v60 1000 1.4107.01r / minn D3.14 250n 107.01r / mi

72、n选用同步转速为 1000r/min 或 1500r/min 的电动机作为原动机，可拟定以下传动方案：1.1 电动机类型和结构型式按工作要求和工作条件，选用一般用途的 Y （IP44）系列三相异步电动机。它为卧式封闭结构。1.2 电动机容量(1)工作机的输出功率PwPwFv25001.4 kW1000 w10000.96(2)电动机输出功率 PdPwPda传动装置的总效率24 a123 4依次确定式中各效率：2 个联轴器 =0.99、 4 个滚动轴承1=0.98、圆柱齿轮传动 3 =0.97、圆锥齿轮传动4=0.96。2则0.9920.9840.970.960.84a =0.991 =0.98

73、2 =0.973 =0.9640.84a故PdPw125001.44.3kW1000 0.960.84a(3)电动机额定功率 PedPd4.3kW由文献【】中选取电动机额定功率Pe d5.5kW 。1.3 电动机的转速Ped5.5kW推算电动机转速可选范围，由文献【】表1 中查得圆锥 -圆柱齿轮传动比范围i a'8 15 ，则电动机转速可选范围为：n dia' n856.08 1605.15r / mi1.4 电动机的技术数据和外形, 安装尺寸根据容量和转速，查文献【】Y 系列三相异步电动机，选定电 机Y132M2 - 6， 额 定 功 率 P5.5kW，满载转速ednm960

74、r / min ，同步转速 n1000r / min 。由文献【】表 19-1 查得主要数据，并记录备用，如表1-1 所示：nm960r / min电机型号 Y132M2-6表额定功率5.5Kw1-1 电机技术数据电流满载转速12.6A960电机质量轻轴径 mm382 计算传动装置总传动比和分配各级传动比2.1 传动装置总传动比nm960ia8.97nw107.012.2 分配各级传动比所以减速器传动比i ia 8.97圆锥齿轮传动比（ i13 ） i1 2.4圆柱齿轮传动比 i 2i3.7i1i a8.97i 8.97i 1 2.4i 23.73 计算传动装置的运动和动力参数3.1 各轴转速

75、n m960r / minni 0n960n400r / mini 12.4n400n 108.1r / mini 23.73.2 各轴输入功率按电动机所需功率Pd 计算各轴输入功率，即P P4.3 0.99 4.26kW d 01PP4.260.960.984.01kW12P P4.01 0.97 0.98 3.81kW 23P工作机轴 P34 3.81 0.98 0.99 3.70kW p 输出 p输入 0.98(式中： ； ; ;)0111242233234213.3 各轴转矩Td9550Pd95504.342.78N .mn m960则T9550P195504.2642.38N .mn

76、1960n960r / minn400r/ minn 108.1r / minP4.26kWP4.01kWP3.81kWP工作机轴3.70kWTd42.78N .mT42.38 N.mT9550 P295504.0195.74N .mn 2400T9550P395503.81336.59 N .mn 3108.1T工作机轴 9550P工作机轴95503.70n 工作机轴326.87 N.m108.1表 3-1 运动和动力参数T95.74 N .mT336.59 N .mT工作机轴326.87N .m功率 P/kw转矩 T/ （n.m）轴号输入输出输入输出转速传动比 i效率 电动机轴4.342.

77、7896010.99轴4.264.1742.3841.539602.40.94轴4.013.9395.7493.834003.70.95轴3.813.73336.59329.86108.110.97工作机轴3.703.63326.87320.33108.14 传动件的设计计算4.1 圆锥直齿轮设计已知输入功率 4.26kw，小齿轮转速 960r/min，齿数比 u=2.4，由电动机驱动，工作寿命 8 年（设每年工作 300 天），单班制，工作时有轻微振动。4.1.1选定齿轮齿轮类型、精度等级、材料及齿数（1）按传动方案选用直齿锥齿轮传动。（2）圆锥圆柱齿轮减速器为通用减速器，速度不高，故选用7

78、级精度 (GB10095-88)（3）材料选择由文献【】表10-1 选择小齿轮材料为40Cr (调质 )，硬度为 280HBS，大齿轮材料为 45 钢（调质），硬度为 240HBS。（4） 选小齿轮齿数 z123 ，大齿轮齿数 z223 2.4 55.2 ，取整 z56。则z256u2.42z1234.1.2按齿面接触强度设计由文献【】式10-9a 由设计计算公式进行试算，即Z E2KT1d1t 2.923R1 0.5 R2 uH（ 1） 确定公式内的各计算数值 试选载荷系数 K t 1.3 计算小齿轮的转矩为输T 95504.261000 4.238 104 N.mm960R1 选齿宽系数3

79、u2.4z123z256K t1.3T4.238 104 N .mmR13由文献 【】图 10-21d 按齿面硬度查得小齿轮的接触疲劳强度极限H lim 1600MPa，大齿轮的接触疲劳强度极限H lim 2550MPa由文献【】表 10-6 查得材料的弹性影响系数11ZE189.8MPa 2ZE189.8MPa 2计算应力循环次数8) 1.106 109N11.106109N160n1 jL h 609601(8300N 24.608108N 21.1061094.6081082.4由文献【】图 10-19 取接触疲劳寿命系数K HN10.95, K HN 21.0。KHN10.95 计算接

80、触疲劳许用应力式10-12 取失效概率为 1%，安全KHN 21.0系数 S=1，得H 1K HN1H lim 10.95600570MPaH 1570MPaSH 2K HN1H lim 11.0550550MPaH 2550MPaS（ 2）计算 试算小齿 轮 分度 圆直 径 d1t ，代入 H 中较 小的值d1 t2.933 ( ZE )23KT 1 H R (1 0.5 R ) 2 u2.923 (189.8 )211.3 4238066.49 mm55031)22.43(1 0.53平均分度圆直径d 1t66 .49 mmd md1t（10.5R） 55.41计算圆周速度 vvdm n1

81、55.41 960v2.78m / s1000602.78m / s601000计算载荷系数根据 v 2.78m/ s ，7 级精度，由文献【】图10-8 查得动载系数 K v1.1表 10-3 直齿轮 KHKF1由文献【】表10-2 查得使用系数 KA1.25根据小齿轮一端悬臂布置，查文献【】表10-9 得轴承系数 K H be 1.25 ，则 K HK F1.5K H be1.88接触强度载荷系数K KAKVKH KH1.25 1.11 1.882.59K2.59按实际的载荷系数校正所算得的分度圆直径，得d1d1t 3K66.49 32.5983.66mmK t1.3计算模数d183.66

82、3.64mmm 3.75mmm23z1取标准值，文献【】表 10-6 模数圆整为 m3.75mm计算齿轮相关参数d1mz13.75 2386.25mmd186.25mmd 23.7556210mmd 2210mmz123。'43"1arctanarc tan22 19z 2561。 '"。'17"22 19 43290167 4056267。40'17"（21d1 2d2 2u 2123）R（d186.25113 .51mm2） （）22113.51mmR2计算齿宽b RR1113.5137.84mmb1 b2 37 mm

83、3文献【】表10-7 圆整为 b1 b237mm （ BR取整）34.1.3校核齿根弯曲疲劳强度（ 1）确定计算参数K2.59载荷系数KKAKVKF KF2.59计算当量齿数ZZd v1z12324.9v1cos。'43"m m1cos22 19Zv124.9d v2z256v2coscos67。40 '17"147.4147.4m m2Zv 2由文献【】表10-5 查得齿形系数Y Fa12.623Y Fa 2 2.142应力校正系 数Y Sa 1 1.589Y Sa2 1.828安全系数 S 1.4K FN10.9由文献【】图 10-18 取弯曲疲劳寿命系

84、数KFN20.95K FN10.9KFN20.95FE 1500MPa由文献【】图 10-20c 查得FE 2380MPa小齿轮的弯曲疲劳强度极限FE 1500MPa ，大齿轮的弯曲疲劳强度极限FE 2380MPa许用应力F 1321.43MPaK FN1FE 10.9500321.43MPaF 2257.86MPaF 11.4SKFN2FE 20.95 380257.86 MPaF 21.4S（ 2）校核强度由式 10-23FKF t YFa YSa2KTY Fa YSaF22bm（1 0.5 R） bm（1 0.5 R）计算得F1110.099F195.968F 2F286.25mm可知弯

85、曲强度满足，参数合理。d14.1.4 几何尺寸计算d 2 =210mmR113.51mm。（1）锥齿轮大端分度圆直径d1122 19' 43"86.25mm,d 2 =210mm（2）计算锥距 RR 113.51mm267。40'17"（3）节圆锥角：。 '43"。 '"1 22192 67 4017（4）大端齿顶圆直径 :da1d12ha cos 1d12m cos 193.19 mmd a193.19mmd a 2d22mcos 2212.85mmd a 2212.85mm（5）计算齿宽b R R1113.5137.84mm3b1 b2 37 mm文献【】表10-7 圆整为 b1b237mm （ BR3 取整）4.2 圆柱直齿齿轮设计 （软齿面）u=3.7已知输入功率4.01 kw ，小齿轮转速400r/min ，齿数比u=3.7，由电动机驱动，工作寿命 8 年（设每年工作 300 天），单班制，工作有轻微震动。4.2.1选定齿轮精度等级、材料及齿数（ 1）圆