湖北工业大学商贸学院毕业论文————机电一体化专科三班
目 录
一、设计任务书···········································································2
二、传动方案的拟定·····································································3 三、电动机的选择·········································································3
1.选择电动机的类型······································································3
2.选择电动机功率·········································································3 3.确定电动机转速··········································································4
四、传动比的计算及分配······························································4
1.总传动比···················································································4 2.分配传动比················································································4
五、传动装置运动、动力参数的计算············································4
1.各轴转速···················································································4
2.各轴功率··················································································4 3.各轴转矩··················································································4
六、传动件的设计计算···································································5
1.高速级锥齿轮传动的设计计算·····················································5 2.低速级斜齿圆柱齿轮的设计计算···················································8
七、 齿轮上作用力的计算································································12 八、减速器转配草图的设计····························································14
九、轴的设计计算·············································································14
1.高速轴的设计与计算································································14 2.中间轴的设计与计算································································19
3.低速轴的设计计算···································································25
十、减速器箱体的结构尺寸·····························································29 十一、润滑油的选择与计算·····························································30 十二、装配图和零件图······································································31 十三、Pro/E虚拟装配及造型·····························································32 十四、参考文献·················································································40
机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器第 1 页 共 40 页
湖北工业大学商贸学院毕业论文————机电一体化专科三班
一、设计任务书 班级 10机电专三班 学号1025112344 姓名 潘东 一、设计题目：设计圆锥—圆柱齿轮减速器 设计铸工车间的型砂运输设备。该传送设备的传动系统由电动机—减速器—运输带组成。每日二班工作。 （图1） 1—电动机；2联轴器；3—减速器；4—鼓轮；5—传送带 二、原始数据： 传送带拉力传送带速度鼓轮直径D使用年限F(KN) V(m/s) （mm） （年） 4.0 0.85 280 10 三、设计内容和要求： 1.编写设计计算说明书一份，其内容通常包括下列几个方面：（1）传动系统方案的分析和拟定以及减速器类型的选择；（2）电动机的选择与传动装置运动和动力参数的计算；（3）传动零件的设计计算（如除了传动，蜗杆传动，带传动等）；（4）轴的设计计算；（5）轴承及其组合部件设计；（6）键联接和联轴器的选择及校核；（7）减速器箱体，润滑及附件的设计；（8）装配图和零件图的设计；（9）校核；（10）轴承寿命校核；（11）设计小结；（12）参考文献；（13）致谢。 机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器第 2 页 共 40 页
湖北工业大学商贸学院毕业论文————机电一体化专科三班
二、传动方案的拟定
运动简图如下：
（图2）
由图可知，该设备原动机为电动机，传动装置为减速器，工作机为型砂运输设备。 减速器为两级展开式圆锥—圆柱齿轮的二级传动，轴承初步选用深沟球轴承。 联轴器2选用凸缘联轴器，8选用齿形联轴器。
三、电动机的选择
电动机的选择见表1 计算项目 1.选择电动机的类型 计算及说明 根据用途选用Y系列三相异步电动机 计算结果 Pw=3.4Kw ?总=0.88 P0=3.86Kw Ped=4Kw 运输带功率为 Pw=Fv/1000=4000*0.85/1000 Kw=3.4Kw 查表2-1，取一对轴承效率?轴承=0.99，锥齿轮传动效率?锥 齿轮=0.96，斜齿圆柱齿轮传动效率?齿轮=0.97，联轴器效率?联 2.选择电动机功率 =0.99，得电动机到工作机间的总效率为 ?总=?4轴承?锥齿轮?齿轮?2联=0.994*0.96*0.97*0.992=0.88 电动机所需工作效率为 P0= Pw/?总=3.4/0.88 Kw=3.86Kw 根据表8-2选取电动机的额定工作功率为Ped=4Kw 机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器第 3 页 共 40 页
湖北工业大学商贸学院毕业论文————机电一体化专科三班
输送带带轮的工作转速为 3.确定电动 nw=(1000*60V)/πd=1000*60*0.85/π机转速 *280r/min=58.01r/min 由表2-2可知锥齿轮传动传动比i锥=2～3，圆柱齿轮传动传动比i齿=3～6，则总传动比范围为 i总=i锥i齿=2～3*(3～6)=6～18 电动机的转速范围为 n0=nwi总≤58.01*(6～18)r/min=348.06～1044.18r/min 由表8-2知，符合这一要求的电动机同步转速有750r/min、1000r/min考虑到1000r/min接近上限，所以本例选用750r/min的电动机，其满载转速为720r/min,其型号为Y160M1-8 nw=58.01r/min nm=720r/min 四、传动比的计算及分配
传动比的计算及分配见表2 计算项目 1.总传动比 2.分配传动比 计算及说明 i=nm/nw=720/58.01=12.41 高速级传动比为 i1=0.25i=0.25*12.41=3.10 为使大锥齿轮不致过大，锥齿轮传动比尽量小于3，取i1=2.95 低速级传动比为 i2=i/i1=12.41/2.95=4.21 计算结果 i=12.41 i1=2.95 i2=4.21 五、传动装置运动、动力参数的计算
传动装置运动、动力参数的计算见表3 计算项目 1.各轴转速 计算及说明 n0=720r/min n1=n0=720r/min n2=n1/i1=720/2.95r/min=244.07r/min n3=n2/i2=244.07/4.21r/min=57.97r/min nw=n3=57.97r/min 计算结果 n1=n0=720r/min n2=244.07r/min nw=n3=57.97r/min p1=p0?联=3.86*0.99kw=3.82kw 2.各轴功率 3.各轴转
p1=3.82kw P2=3.63kw P3=3.49kw Pw=3.42kw T0=51.20N·m P2=p1?1-2=p1?轴承?锥齿=3.82*0.99*0.96kw=3.63kw P3=p2?2-3=p2?轴承?直齿=3.63*0.99*0.97kw=3.49kw Pw=p3?3-w=p3?轴承?联=3.49*0.99*0.99kw=3.42kw T0=9550p0/n0=9550*3.86/720N·mm=51.20N·m 机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器第 4 页 共 40 页
湖北工业大学商贸学院毕业论文————机电一体化专科三班
矩 T1=9550p1/n1=9550*3.82/720N·mm=50.67N·m T2=9550p2/n2=9550*3.63/244.07N·mm=142.04N·m T3=9550p3/n3=9550*3.49/57.97N·mm=574.94N·m Tw=9550pw/nw=9550*3.42/57.97N·mm=563.41N·m T1=50.67N·m T2=142.04N·m T3=574.94N·m Tw=563.41N·m
六、 传动件的设计计算
一、高速级锥齿轮传动的设计计算
锥齿轮传动的设计计算见表4 计算项目 1.选择材料、热处理方式和公差等级 2.初步计算传动的主要尺寸 计算及说明 考虑到带式运输机为一般机械，大、小锥齿轮均选用45钢，小齿轮调质处理，大齿轮正火处理，由表8-17得齿面硬度HBW1=217～255，HBW2=162～217.平均硬度HBW1=236，HBW2=190.HBW1-HBW2=46.在30～50HBW之间。选用8级精度。 计算结果 45钢 小齿轮调质处理 大齿轮正火处理 8级精度 因为是软齿面闭式传动，故按齿面接触疲劳强度进行设计。 其设计公式为 2??4kT(ZZ/?)H1EH d1≥3 0.85?R?(1?0.5?R)2 1)小齿轮传递转矩为T1=50670Ｎ·ｍｍ 2)因v值未知，Kv值不能确定，可初步选载荷系数Kt=1.3 3)由表8-19，查得弹性系数ZE=189.8Mpa 4)直齿轮，由图9-2查得节点区域系数ZH=2.5 5)齿数比?=i1=2.95 6)取齿宽系数?R=0.3 7)许用接触应力可用下式公式 ???H?ZN?Hlim/SH 由图8-4e、a查得接触疲劳极限应力为 ?Hlim1?580pa,?Hlim2?390pa 小齿轮与大齿轮的应力循环次数分别为 9 N1=60n1aLh=60*720*1*2*8*250*10=1.728*10 98N2=N1/i1=1.728*10/2.95=5.858*10 由图8-5查得寿命系数ZN1=1，ZN2=1.05；由表8-20取安全系 数SH=1，则有 机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器第 5 页 共 40 页