目 录
一、 传动装配的总体设计
1.1 电机的选择················································1 1.2 求传动比··················································2 1.3 计算各轴的转速、功率、转矩 ·······························2
二、 齿轮的设计
2.1 2.2 2.3 2.4 2.5
原始数据··················································3 齿轮的主要参数············································3 确定中心距················································4 齿轮弯曲强度的校核 ·······································5 齿轮的结构设计············································7
三、 轴的设计计算
3.1 轴的材料的选择和最小直径的初定····························8 3.2 轴的结构设计··············································8 3.3 轴的强度校核··············································10
四、 滚动轴承的选择与计算
4.1 滚动轴承的选择············································14 4.2 滚动轴承的校核············································14
五、 键连接的选择与计算
5.1 键连接的选择··············································15 5.2 键的校核··················································15
六、 联轴器的选择
6.1 联轴器的选择··············································16 6.2 联轴器的校核··············································16
七、 润滑方式、润滑油型号及密封方式的选择
7.1 润滑方式的选择············································16 7.2 密封方式的选择············································17
八、 箱体及附件的结构设计和选择
8.1 箱体的结构尺寸············································17 8.2 附件的选择················································18
九、 设计小结···········································19 十、参考资料·············································20
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机械设计课程设计计算说明书
已知条件：
项 目 参 数 运输带拉力 F（N） 4800 运输带速 v（m/s） 2.5 卷筒直径 D(mm) 210 结 构 简 图
1 传动装配的总体设计
1.1 电机的选择
1.1.1 类型：Y系列三项异步电动机 1.1.2 电动机功率的选择
假设： pw—工作机所需功率, kw; pe—电动机的额定功率, kw； pd—电动机所需功率, kw；
?1、?2、?3、?4分别为弹性连轴器、电动机到工作机的总效率为?，
闭式齿轮传动（齿轮精度为8级）、滚动轴承和共同的效率。
1
则：pw?
FV1000?4800?2.51000?12Kw
pd?pe?pw/?
3 ???轴 ??2?承齿轮联轴器卷筒查表可得：?轴承?0.99、?齿轮?0.97、?联轴器?0.98、?卷筒?0.96
322所以：???轴????0.99*0.97*0.99*0.96?0.89 承齿轮联轴器卷筒 pd?pe?pw/??12/0.?891Kw3.4 81.1.3电动机转速的选择以及型号的确定
方案号 1 电动机型号 Y180L-6 额定功率 同步转速 满载转速 总传动比 （kw） （r/min） （r/min） 15 1000 970 4.26 辅助计算：
nw?i1?60?1000?v?D?970227.48?60?1000?2.53.14?210?227.48r/min
nmnw?4.26 因为本设计为单级斜齿圆柱齿轮减速器的设计，总传动比应在3-5左
右，所以应按方案二选择电动机。
查表可得：外伸轴长度80mm,直径38mm，额定功率和满载转速见上表。
1.2 求传动比
nw?60?1000?v?D?60?1000?2.53.14?210?227.48r/min
i?nmnw?i齿?970227.48?4.26
1.3 计算各轴的转速n、功率p、转矩T
1.3.1 各轴的转速
n1?nm?970r/minn2?nw?227.48r/min
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1.3.2 各轴的输入功率
p1?pd?1?13.48?0.99?13.35Kwp2?p1?2?3?13.35?0.98?0.99?12.95Kw
1.3.3 各轴的输入转矩
T1?9550p1n1?9550?13.35970?131.44N?m
T2?9550p2n2?9550?12.95227.48?543.66N?m
2 齿轮的设计
2.1 原始数据
强度极限 材料牌号 热处理方法 正 火 调 质 ?B/Mpa 屈服极限 ?C/Mpa 硬 度 HBS 169~217 229~286 45 560 580 200 220 其中小齿轮45号钢调质，大齿轮45号钢正火 2.2 齿轮的主要参数
由上述硬度可知，该齿轮传动为闭式软尺面传动，软尺面硬度<350HBS，所以齿轮的相关参数按接触强度设计，弯曲强度校核。
?HP?
?HlimSHlimZNZW
式中：?Hlim—试验齿轮的接触疲劳强度极限应力；
SHlim—接触强度的最小安全系数，取SHlim?1.5；
ZN—接触疲劳强度计算的寿命系数，取ZN?1.02；
ZW—工作硬化系数，取ZW?1。
由教材图5—29查得：小齿轮?Hlim1?580Mpa；
大齿轮?Hlim2?560Mpa。
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?HP1??Hlim1SHlimZNZW?ZNZW?3801.55751.5?1.02?1?258.4Mpa
所以：
?HP2??Hlim2SHlim2?1.02?1?391.0Mpa?z??KT1?u?1?3d1?754???? ??HP??d?u?式中：
z?—重合度系数，对于斜齿轮传动
z?=0.75~0.88，取
z?=0.80；
K—载荷系数，一般近视取k=1.3~1.7,因是斜齿轮传动，故
k取小
K=1.5；
?d—齿宽系数，对于软尺面（<350HBS），齿轮相对于轴承
对称布置时，
?d=0.8~1.4,取
?d=1；
u—齿数比，对于斜齿轮u?5~6，取u?5。
所以：d1?754?3?z??KT1?u?1????? ??u??HP1?d?22 ?754?3?0.85???258.4??1?.325?.8?6?5??
0.95??1 ?16.08m m2.3 确定中心距
a=d1?d22?mv?Z1?Z22??mn?Z1?Z2cos??2
式中：Z1—小齿轮的齿数；
Z2—大齿轮的齿数； ?—齿轮的螺旋角；
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