二级圆锥-圆柱齿轮减速器.doc

XX学院
毕业设计说明书
课 题： 二级圆锥-圆柱齿轮减速器
子课题:
同课题学生姓名:

专 业
学生姓名
班 级
学 号
指导教师
完成日期

二级圆锥-圆柱齿轮减速器
摘要
减速器是各类机械设备中广泛应用的传动装置。减速器设计的优劣直接影响机械设备的传动性能。
减速器是原动机和工作机之间的独立的闭式传动装置，用来降低转速和增大转矩，以满足工作需要，在某些场合也用来增速，称为增速器。
　　选用减速器时应根据工作机的选用条件，技术参数，动力机的性能，经济性等因素，比较不同类型、品种减速器的外廓尺寸，传动效率，承载能力，质量，价格等，选择最适合的减速器。
减速器的类别、品种、型式很多，目前已制定为行（国）标的减速器有40余种。减速器的类别是根据所采用的齿轮齿形、齿廓曲线划分；减速器的品种是根据使用的需要而设计的不同结构的减速器；减速器的型式是在基本结构的基础上根据齿面硬度、传动级数、出轴型式、装配型式、安装型式、联接型式等因素而设计的不同特性的减速器。
齿轮传动是现代机械中应用最广的一种传动形式。它的主要优点是：
瞬时传动比恒定，工作平稳，传动准确可靠，可传递空间任意两轴间的运动和动力
适用的功率和速度范围广
传动效率高
工作可靠，使用寿命长
外轮廓尺寸小，结构紧凑。

  绪论
随着社会的发展和人民生活水平的提高，人们对产品的需求是多样化的，这就决定了未来的生产方式趋向多品种、小批量。在各行各业中十分广泛地使用着齿轮减速器，它是一种不可缺少的机械传动装置. 它是机械设备的重要组成部分和核心部件。目前，国内各类通用减速器的标准系列已达数百个，基本可满足各行业对通用减速器的需求。国内减速器行业重点骨干企业的产品品种、规格及参数覆盖范围近几年都在不断扩展，产品质量已达到国外先进工业国家同类产品水平，承担起为国民经济各行业提供传动装置配套的重任，部分产品还出口至欧美及东南亚地区，推动了中国装配制造业发展。
由于编者水平有限，设计中有错误与不当之处在所难免，希望老师批评指正。

关键字：减速器、齿轮、轴承、联接

目 录
摘要························································································2
绪论························································································4
一、设计任务书······································································8
一、设计题目········································································8
二、原始数据········································································8
三、设计内容和要求······························································8
二、传动方案的拟定·····························································9
三、电动机的选择··································································9
1.选择电动机的类型·······························································9
2.选择电动机功率···································································9
3.确定电动机转速···································································10
四、传动比的计算
1. 总传动比·········································································10
2. 分配传动比······································································10
五、传动装置运动、动力参数的计算
1.各轴的转速············································································10
2.各轴功率计············································································10
3.各轴转矩················································································11
六、 传动件的设计计算
一、高速级锥齿轮传动的设计计算················································11
1.选择材料、热处理方式和公差等级·············································11
2.初步计算传动的主要尺寸··························································11
3.确定传动尺寸·········································································12
4.校核齿根弯曲疲劳强度·····························································13
5.计算锥齿轮传动其他几何尺寸····················································14
二、低速级斜齿圆柱齿轮的设计计算
1.选择材料、热处理方式和公差等级··············································14
2.初步计算传动的主要尺寸···························································15
3.确定传动尺寸···········································································16
4.校核齿根弯曲疲劳强度······························································17
5.计算锥齿轮传动其他几何尺寸·····················································18
七、齿轮上作用力的计算·························································19
1.高速级齿轮传动的作用力····························································19
2.低速级齿轮传动的作用力····························································19
八、减速器装配草图的设计······················································19
九、轴的设计计算···································································20
一、高速轴的设计与计算····························································20
1.已知条件············································································21
2.选择轴的材料······································································21
3.初算轴径············································································22
4.结构设计············································································22
5.键连接················································································23
6.轴的受力分析·······································································23
7.校核轴的强度·······································································24
8.校核键连接的强度·································································24
二、中间轴的设计与计算································································25
1.已知条件···············································································25
2.选择轴的材料········································································25
3.初算轴径···············································································26
4.结构设计···············································································26
5.键连接··················································································28
6.轴的受力分析·········································································28
7.校核轴的强度·········································································29
8.校核键连接的强度···································································30
三、低速轴的设计与计算·································································30
1.已知条件·················································································30
2.选择轴的材料···········································································30
3.初算轴径·················································································30
4.结构设计·················································································31
5.键连接····················································································32
6.轴的受力分析···········································································32
7.校核轴的强度···········································································33
8.校核键连接的强度·····································································34
十、减速器箱体的结构尺寸··························································35
十一、润滑油的选择与计算························································36
十二、装配图和零件图································································37
致谢·······························································································38
参考文献························································································39

一、设计任务书
一、设计题目：设计圆锥—圆柱齿轮减速器
设计卷扬机传动装置中的两级圆锥-圆柱齿轮减速器。该传送设备的传动系统由电动机—减速器—运输带组成。轻微震动，单向运转，在室内常温下长期连续工作。

（图1）
1—电动机；2联轴器；3—减速器；4—卷筒；5—传送带
二、原始数据：
运输带拉力F(KN)
运输带速度V(m/s)
卷筒径D（mm）
使用年限（年）
4000
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。
2. 要求每个学生完成以下工作：
（1）减速器装配图一张（0号或一号图纸）
（2）零件工作图二张（输出轴及该轴上的大齿轮），图号自定，比例1︰1。
（3）设计计算说明书一份。
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
计算及说明
计算结果
1.选择电动机的类型
根据用途选用Y系列三相异步电动机

2.选择电动机功率

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=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

Pw=3.4Kw

总=0.88

P0=3.86Kw

Ped=4Kw

3.确定电动机转速
输送带带轮的工作转速为
nw=(1000*60V)/πd=1000*60*0.85/π*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
计算及说明
计算结果
1.总传动比
i=nm/nw=720/58.01=12.41
i=12.41

2.分配传动比

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

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
计算及说明
计算结果

1.各轴转速

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

n1=n0=720r/min

n2=244.07r/min

nw=n3=57.97r/min

2.各轴功率
p1=p0联=3.86*0.99kw=3.82kw
P2=p11-2=p1轴承锥齿=3.82*0.99*0.96kw=3.63kw
P3=p22-3=p2轴承直齿=3.63*0.99*0.97kw=3.49kw
Pw=p33-w=p3轴承联=3.49*0.99*0.99kw=3.42kw
p1=3.82kw

P2=3.63kw
P3=3.49kw
Pw=3.42kw
3.各轴转矩
T0=9550p0/n0=9550*3.86/720N·mm=51.20N·m

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
T0=51.20N·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
计算及说明
计算结果
1.选择材料、热处理方式和公差等级
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。
45钢
小齿轮调质处理
大齿轮正火处理
8级精度

2.初步计算传动的主要尺寸
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
d1≥
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=189.8
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=0.3
7) 许用接触应力可用下式公式

由图8-4e、a查得接触疲劳极限应力为
小齿轮与大齿轮的应力循环次数分别为
N1=60n1aLh=60*720*1*2*8*250*10=1.728*109
N2=N1/i1=1.728*109/2.95=5.858*108
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

取
初算小齿轮的分度圆直径d1t,有

d1t≥69.78mm

3.确定传动尺寸
（1）计算载荷系数 由表8-1查得使用系数KA=1.0，齿宽中点分度圆直径为
dm1t=d1t(1-0.5)=69.78*(1-0.5*0.3)mm=59.313mm
故vm1=πdm1tn1/60*1000=π*59.313*720/60*1000m/s=2.23m/s
由图8-6降低1级精度，按9级精度查得动载荷系Kv=1.19，由图8-7查得齿向载荷分配系数Kß=1.13，则载荷系数K=KAKvKß=1.0*1.19*1.13=1.34
(2） 对d1t进行修正 因K与Kt有较大的差异，故需对Kt计算出的d1t进行修正 ，即
d1=≥69.78=70.485mm
（3） 确定齿数 选齿数Z1=23，Z2=uZ1=2.95*23=67.85，取Z2=68，则，，在允许范围内
（4） 大端模数m ，查表8-23，取标准模数m=3.5mm
（5） 大端分度圆直径为
d1=mZ1=3.5*23mm=80.5mm>70.485
d2=mZ2=3.5*68mm=238mm
(6) 锥齿距为
R=
（7） 齿宽为 b==0.3*70.374mm=21.112mm
取b=25mm

d1=70.485mm

Z1=23
Z2=57

m=3.5mm

d1=80.5mm
d2=238mm

R=70.374mm

b=25mm

4.校核齿根弯曲疲劳强度

齿根弯曲疲劳强度条件为
≤
（1） K、b、m和同前
（2） 圆周力为
Ft=
（3） 齿形系数YF和应力修正系数YS

即当量齿数为

由图8-8查得YF1=2.65,YF2=2.13，由图8-9查得YS1=1.58，YS2=1.88
（4） 许用弯曲应力

由图8-4查得弯曲疲劳极限应力为
由图8-11查得寿命系数YN1=YN2=1,由表8-20查得安全系数SF=1.25，故

满足齿根弯曲强度

5.计算锥齿轮传动其他几何尺寸
ha=m=3.5mm
hf=1.2m=1.2*3.5mm=4.2mm
C=0.2m=0.2*3.5mm=0.7m
da1=d1+2mcos=80.5+2*3.5*0.9474mm=87.132mm
da2=d2+2mcos=238+2*3.5*0.3201mm=240.241mm
df1=d1-2.4mcos=80.5-2.4*3.5*0.9474mm=72.542mm
df2=d2-2.4mcos=238-2.4*3.5*0.3201mm=235.311mm

ha=3.5mm
hf=4.2mm
C=0.7m

da1=87.132mm

da2=240.241mm

df1=72.542mm

df2=235.311mm

二、低速级斜齿圆柱齿轮的设计计算
斜齿圆柱齿轮的设计计算见表5
计算项目
计算及说明
计算结果

1.选择材料、热处理方式和公差等

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。
45钢
小齿轮调质处理
大齿轮正火处理
8级精度

2.初步计算传动的主要尺寸
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

1) 小齿轮传递转矩为T2=146040Ｎ·ｍｍ
2) 因v值未知，Kv值不能确定，可初步选载荷系数Kt=1.4
3) 由表8-19，查得弹性系数ZE=189.8
4) 初选螺旋角，由图9-2查得节点区域系数ZH=2.46
5) 齿数比=i=4.21
6) 查表8-18，取齿宽系数=1.1
7) 初选Z3=23，则Z4=uZ3=4.21*23=96.83，取Z4=97
则端面重合度为

=
=1.67
轴向重合度为

由图8-13查得重合度系数
8） 由图11-2查得螺旋角系数Z=0.99
9） 许用接触应力可用下式计算

由图8-4e、a查得接触疲劳极限应力为
小齿轮与大齿轮的应力循环次数分别为
N3=60n2aLh=60*244.07*1*2*8*250*10=5.86*108
N4=N3/i2=5.86*108/4.21=1.39*108
由图8-5查得寿命系数ZN3=1.05，ZN4=1.13；由表8-20取安全系数SH=1.0，则有

取
初算小齿轮的分度圆直径d3t，得

=
=66.59mm

Z3=23
Z4=97

d3t≥66.59mm

3.确定传动尺寸
（1）计算载荷系数 由表8-21查得使用系数KA=1.0
因=0.85m/s，由图8-6查得动载荷系数Kv=1.08，由图8-7查得齿向载荷分配系数K=1.11，由表8-22查得齿向载荷分配系数K=1.2，则载荷系数为
K=KAKvKK=1.0*1.08*1.11*1.2=1.44
（2） 对d3t进行修正 因K与Kt有较大的差异，故需对Kt计算出的d3t进行修正，即
=67.22mm
(3) 确定模数mn
mn=
按表8-23，取mn=3mm
（4） 计算传动尺寸 中心距为
=184.03mm
取整，
螺旋角为

因值与初选值相差不大，故对与有关的参数无需进行修正
则可得，

b4=78mm
b3=85mm

K=1.44

mn=3mm

a=184mm

d3=70.531mm

d4=297.455mm

b4=78mm

b3=85mm

4.校核齿根弯曲疲劳强度
齿根弯曲疲劳强度条件为

1） K、T3、mn和d3同前
2） 齿宽b=b4=78mm
3） 齿形系数YF和应力修正系数YS。当量齿数为

由图8-8查得YF3=2.62，YF4=2.24；由图8-9查得YS3=1.59，
YS4=1.82
4） 由图8-10查得重合度系数
5） 由图11-23查得螺旋角系数
6） 许用弯曲应力为

由图8-4f、b查得弯曲疲劳极限应力
由图8-11查得寿命系数YN3=YN4=1，由表8-20查得安全系数SF=1.25，故

=
=63.93Mpa<

满足齿根弯曲疲劳强度

5.计算齿轮传动其他几何尺寸
端面模数
齿顶高 ha=ha*mn=1*3mm=3mm
齿根高 hf=(ha*+c*）mn=（1+0.25）*3mm=3.75mm
全齿高 h=ha+hf=3+3.75mm=6.75mm
顶隙 c=c*mn=0.25*3mm=0.75mm

齿顶圆直径为
da3=d3+2ha=70.531+2*3mm=76.531mm
da4=d4+2ha=297.455+2*3mm=303.455mm

齿根圆直径为
df3=d3-2hf=70.531-2*3.75mm=63.031mm
df4=d4-2hf=297.455-2*3.75mm=289.955mm
m1=2.56mm

ha=3mm
hf=3.75mm
h=6.75mm
c=0.75mm

da3=76.531mm
da4=303.455mm

df3=63.031mm
df4=289.955mm

七、 齿轮上作用力的计算
齿轮上作用力的计算为后续轴的设计和校核、键的选择和验算及轴承的选择和校核提供数据，其计算过程见表6
计算项目
计算及说明
计算结果

1.高速级齿轮传动的作用力
（1）已知条件 高速轴传递的转矩T1=50670Nmm，转速n1=720r/min，小齿轮大端分度圆直径d1=80.5mm，=0.9474，=0.3201，
（2）锥齿轮1的作用力 圆周力为

其方向与力作用点圆周速度方向相反
径向力为

其方向为由力的作用点指向轮1的转动中心
轴向力为

其方向沿轴向从小锥齿轮的小端指向大端
法向力为

Ft1=1481.0N

Fr1=510.7N

Fa1=172.5N

FN1=1576.1N

2.低速级齿轮传动的作用力
（1）已知条件 中间轴传递的转矩T2=142040Nmm，转速n2=244.07r/min，低速级斜齿圆柱齿轮的螺旋角。为使斜齿圆柱齿轮3的轴向力与锥齿轮2的轴向力互相抵消一部分，低速级的小齿轮右旋，大齿轮左旋，小齿轮分度圆直径为
d3=70.531mm
（2） 齿轮3的作用力
圆周力为
其方向与力作用点圆周速度方向相反
径向力为

其方向为由力的作用点指向轮3的转动中心
轴向力为

其方向可用右手法则来确定，即用右手握住轮3的轴线，并使四指的方向顺着轮的转动方向，此时拇指的指向即为该力的方向
法