圆锥圆柱齿轮减速器设计说明书1解读.docx
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圆锥圆柱齿轮减速器设计说明书1解读
机械设计课程设计
计算说明书
圆锥圆柱齿轮减速器
班号
设计者:
指导教师:
年月
目录
一¸设计任务书························································································2
二¸电机的选择计算
1.择电机的转速·················································································2
2.工作机的有效功率···········································································2
3.选择电动机的型号···········································································3
三¸传动和动力参数的计算
1.分配传动比····················································································3
2.各轴的转速····················································································3
3.各轴的功率····················································································4
4.各轴的转矩·····················································································4
四¸传动零件的设计计算
1.闭式直齿轮圆锥齿轮传动的设计计算·················································4
2.闭式直齿轮圆柱齿轮传动的设计计算·················································6
五¸轴的设计计算
4.减速器高速轴I的设计·····································································9
5.减速器低速轴II的设计··································································11
3.减速器低速轴III的设计··································································14
六¸滚动轴承的选择与寿命计算
1.减速器高速I轴滚动轴承的选择与寿命计算·········································16
2.减速器低速II轴滚动轴承的选择与寿命计算········································17
3.减速器低速III轴滚动轴承的选择与寿命计算·····································18
七¸键联接的选择和验算
1.联轴器与高速轴轴伸的键联接··························································19
2.大圆锥齿轮与低速轴II的的键联接····················································19
3.大圆柱齿轮与低速轴III的的键联接··················································20
八¸润滑油的选择与热平衡计算
1.减速器的热平衡计算·········································································21
2.润滑油的选择·················································································22
九¸参考文献························································································23
1.
计算内容
计算结果
一.设计任务书
设计题目:
热处理车间零件清洗用传送设备
的传动装置
(一)方案设计要求:
具有过载保护性能(有带传动)
含有二级展开式圆柱齿轮减速器
传送带鼓轮方向与减速器输出轴方向平行
(二)工作机原始数据:
传送带鼓轮直径278mm,
传送带带速0.98m/s,
传送带主动轴所需扭距T为248N.m
使用年限9年,2班制
工作载荷微振
二.电机的选择计算
1.选择电机的转速:
a.计算传动滚筒的转速
nw=60V/πd=60×0.98/3.14×0.278=67.326r/min
b.计算工作机功率
pw=nw/9.55×10³=248×67.326/9.55×10³=1.748Kw
2.工作机的有效功率
a.传动装置的总效率
带传动的效率η1=0.96
弹性联轴器的效率η2=0.99
D=300㎜
F=2400N
V=1.0m/s
L=11年
nw=67.326r/min
pw=1.748Kw
计算内容
计算结果
一对圆锥滚子轴承的效率η3=0.98
一对球轴承的效率η4=0.99
闭式直齿圆锥齿传动效率η5=0.95
闭式直齿圆柱齿传动效率η6=0.97
b.总效率η=η1η22η33η4η5η6=0.96×0.992×0.983×0.99×0.95×0.97=0.808
c.所需电动机的输出功率Pr=Pw/η=2.4/0.808=3kw
3.选择电动机的型号
查参考文献[1]表4-12.2得表1.1
方案号
电机
类型
额定
功率
同步
转速
满载
转速
总传
动比
1
Y100L2-4
3
1500
1420
22.294
2
Y132S-6
3
1000
960
15.072
根据以上两种可行同步转速电机对比可见,方案2传动比小且质量价格也比较合理,所以选择Y132S-6型电动机。
三,动和动力参数的计算
6.分配传动比
(1)总传动比i=15.072
(2)各级传动比:
直齿轮圆锥齿轮传动比i12=3.762,
直齿轮圆柱齿轮传动比i23=4
(3)实际总传动比i实=i12i34=3.762×4=15.048,
∵Δi=0.021﹤0.05,故传动比满足要求满足要求。
7.各轴的转速(各轴的标号均已在图1.1中标出)
n0=960r/min,n1=n0=960r/min,n2=n1/i12=303.673r/min,n3=n2/i34=63.829r/min,n4=n3=63.829r/min
8.各轴的功率
η=0.808
Pr=3kw
选用三相异步电动机Y132S-6
p=3kw
n=960r/min
i=15.072
i12=3.762
i23=4
n0=960r/min
n1=960r/min
n2=303.67r/min
n3=63.829r/min
n4=63.829r/min
计算内容
计算结果
p0=pr=3kw,p1=p0η2=2.970kw,p2=p1η4η3=2.965kw,p3=p2η5η3=2.628kw,p4=p3η2η3=2.550kw
4.各轴的转矩,由式:
T=9.55Pi/ni可得:
T0=29.844N·m,T1=29.545N·m,T2=86.955N·m,
T3=393.197N·m,T4=381.527N·m
四,传动零件的设计计算
1.闭式直齿轮圆锥齿轮传动的设计计算
a.选材:
小齿轮材料选用45号钢,调质处理,HB=217~255,
σHP1=580Mpa,σFmin1=220Mpa
大齿轮材料选用45号钢,正火处理,HB=162~217,
σHP2=560Mpa,σFmin2=210Mpa
b.由参考文献[2](以下简称[2])式(5—33),计算应力循环次数N:
N1=60njL=60×960×1×8×11×250=1.267×10
N2=N1/i2=1.267×10/3=2.522×10
查图5—17得ZN1=1.0,ZN2=1.12,由式(5—29)得
ZX1=ZX2=1.0,取SHmin=1.0,ZW=1.0,ZLVR=0.92,
∴[σH]1=σHP1ZLVRZWZX1ZN1/SHmin=580×0.92=533.6Mpa,
[σH]2=σHP2ZN2ZX2ZWZLVR/SHmin=560×1.12×0.92=577Mpa
∵[σH]1>[σH]2,∴计算取[σH]=[σH]2=533.6Mpa
c.按齿面接触强度设计小齿轮大端模数(由于小齿轮更容易失效故按小齿轮设计):
取齿数Z1=21,则Z2=Z1i12=3.762×32=79,取Z2=79
∵实际传动比u=Z2/Z1=79/21=3.762,且u=tanδ2=cotδ1,
∴δ2=72.2965
=72
1635,δ1=17.7035
=17
4212,则小圆锥齿轮的当量齿数zm1=z1/cosδ1=21/cos17.7035
=23,zm2=z2/cosδ2=79/cos72.2965
=259.79
p0=3kw
p1=2.970kw
p2=2.965kw
p3=2.628kw
p4=2.550kw
T0=29.844N·m
T1=29.545N·m
T2=86.955N·m
T3=393.197N·m
T=381.527N·m
σHP1=580Mpa,
σFmin1=220Mpa
σHP2=560Mpa,
σFmin2=210Mpa
[σH]=533.6Mpa
圆锥齿轮参数
Z1=21
Z2=79
δ1=17
4212
δ2=72
1635
计算内容
计算结果
由[2]图5-14,5-15得
YFa=2.8,Ysa=1.55,YFa2=2.23,Ysa2=1.81
ZH=√2/cosα×sinα=√2/cos20
×sin20
=2.5
由[2]表11-5有ZE=189.8,取Kt·Z
=1.1,由[2]取K=1.4
又∵T1=28.381N·m,u=3.762,фR=0.3
由[2]式5-56计算小齿轮大端模数:
m≥√4KT1YFaYsa/{фRZ
[σF](1-0.5фR)2√u2+1}
将各值代得m≥1.498
由[2]表5-9取m=3㎜
d.齿轮参数计算:
大端分度圆直径d1=mz1=3×21=63㎜,d2=mz2=3×79=237㎜
齿顶圆直径da1=d1+2mcosδ1=63+6cos17.7035=68.715㎜,
da2=d2+2mcosδ2=237+6cos72.2965
=238.827㎜
齿根圆直径df1=d1-2.4mcosδ1=63-7.2cos17.7035
=56.142㎜
df2=d2-2.4mcosδ2=237-7.2×cos72.2965
=231.808㎜
齿轮锥距R=√d1+d2/2=122.615㎜,
大端圆周速度v=∏d1n1/60000=3.14×63×960/60000=3.165m/s,
齿宽b=RфR=0.3×122.615=36.78㎜
由[2]表5-6,选齿轮精度为8级
由[1]表4.10-2得Δ1=(0.1~0.2)R
=(0.1~0.2)305.500=30.05~60.1㎜
取Δ1=10㎜,Δ2=14㎜,c=10㎜
轮宽L1=(0.1~0.2)d1=(0.1~0.2)93=12.4㎜
L2=(0.1~0.2)d2=(0.1~0.2)×291=39㎜
e.验算齿面接触疲劳强度:
按[2]式5-53
σH=ZHZE√2KT1√u+1/[bd
u(1-0.5фR)2],代入各值得
圆锥齿轮参数
m=3㎜
d1=63㎜
d2=237㎜
da1=68.715㎜
da2=238.827㎜
df1=56.142㎜
df2=231.808㎜
R=122.615㎜
v=3.165m/s
b=36.78㎜
Δ1=10㎜
Δ2=14㎜
c=10㎜
L1=12.4㎜
L2=39㎜
计算内容
计算结果
σH=470.899﹤[σH]=533.6Mpa
∴小齿轮满足接触疲劳强度,且大齿轮比小齿轮接触强度高,故齿轮满足接触强度条件
f.齿轮弯曲疲劳强度校核:
按[2]式5-55
由[2]图5-19得YN1=YN2=1.0,
由[2]式5-32及m=2﹤5㎜,得YX1=YX2=1.0
取YST=2.0,SFmin=1.4,由[2]式5-31计算许用弯曲应力:
[σF1]=σFmin1YFa1Ysa1YST/SFmin=220×2.0/1.4=314.29Mpa
[σF2]=σFmin2YFa2Ysa2YST/SFmin=210×2.0/1.4=300Mpa
∵[σF1]﹥[σF2],∴[σF]=[σF2]=300Mpa
由[2]式5-24计算齿跟弯曲应力:
σF1=2KT1YFa1Ysa1/[b1md1(1-0.5фR)]=2×1.4×80070×2.8×1.55/0.85×2×28.935×62=181.59﹤300Mpa
σF2=σF1YFa2Ysa2/(YFa1Ysa1)=181.59×1.81×2.23/(2.8×1.55)=178.28﹤300Mpa
∴两齿轮满足齿跟弯曲疲劳强度
2.闭式直齿轮圆柱齿轮传动的设计计算
a.选材:
小齿轮材料选用45号钢,调质处理,HB=217~255,
σHP1=580Mpa,σFmin1=220Mpa
大齿轮材料选用45号钢,正火处理,HB=162~217,
σHP2=560Mpa,σFmin2=210Mpa
b.由参考文献[2](以下简称[2])式(5—33),计算应力循环次数N:
N1=60njL=60×960×1×8×11×250=1.267×10
,N2=N1/i23=1.267×10/3=2.522×10
查图5—17得ZN1=1.05,ZN2=1.16,由式(5—29)得
ZX1=ZX2=1.0,取SHmin=1.0,ZW=1.0,ZLVR=0.92,
[σH]1=σHP1ZLVRZWZX1ZN1/SHmin=580×1.05×0.92=560.28MPa
[σH]=533.6Mpa
[σF]=300Mpa
σHP1=580Mpa
σFmin1=220Mpa
σHP2=560Mpa
σFmin2=210Mpa
计算内容
计算结果
[σH]2=σHP2ZN2ZX2ZWZLVR/SHmin=560×1.16×0.92=597.63MPa
∵[σH]1>[σH]2,∴计算取[σH]=[σH]2=560.28Mpa
c.按齿面接触强度计算中心距(由于小齿轮更容易失效故按小齿轮设计):
∵u=i34=4,фa=0.4,
ZH=√2/cosα·sinα=√2/cos200·sin200=2.5
且由[2]表11-5有ZE=189.8,取Kt·Z
=1.1
∴[2]式5-18计算中心距:
a≥(1+u)√KT1(ZEZHZε/[σH])2/(2uφa)=5×√1.1×86955×2.5×189.8/(2×4×0.4×560.28)=147.61㎜
由[1]表4.2-10圆整取a=160㎜
d.齿轮参数设计:
m=(0.007~0.02)a=180(0.007~0.02)=1.26~3.6㎜
查[2]表5-7取m=2㎜
齿数Z1=2a/m(1+u)=2×160/2(1+4)=32
Z2=uZ1=4×32=128取Z2=128
则实际传动比i=149/31=4
分度圆直径d1=mz1=2×32=64㎜,d2=mz2=2×128=256㎜
齿顶圆直径da1=d1+2m=68㎜,da2=d2+2m=260㎜
齿基圆直径db1=d1cosα=64×cos20o=60.14㎜
db2=d2cosα=256×cos20o=240.56㎜
齿根圆直径df1=d1-2.5m=64-2.5×2=59㎜
df2=d2-2.5m=256-2.5×2=251㎜
圆周速度v=∏d1n2/60×103
=3.14×256×63.829/60×103=1.113m/s,
中心距a=(d1+d2)/2=160㎜
齿宽b=aΦa=0.4×160=64㎜
由[2]表5-6,选齿轮精度为8级
[σH]=560.28Mpa
圆柱齿轮参数
m=2㎜
Z1=32
Z2=128
d1=64㎜
d2=256㎜
da1=8㎜
da2=260㎜
db1=60.14㎜
db2=240.56㎜
df1=59㎜
df2=251㎜
v=1.113m/s
a=160㎜
b=64㎜
计算内容
计算结果
e.验算齿面接触疲劳强度
按电机驱动,载荷平稳,由[2]表5-3,取KA=1.0;由[2]图5-4(d),按8级精度和VZ/100=∏dn/60000/100=0.30144,得Kv=1.03;由[2]表5-3得Ka=1.2;由[2]图5-7和b/d1=72/60=1.2,得KB=1.13;
∴K=KvKaKAKB=1.03×1.2×1.0×1.13=1.397
又∵ɑa1=arccosdb1/da1=arccos(60.14/68)=28.0268
=28
136;
ɑa2=arccosdb2/da2=arccos(2240.56/260)=22.0061
=22
017
∴重合度εa=[z(tanɑa1-tanɑ)+z(tanɑa1-tanɑ)]/2∏=[32(tan28.0268
-tan20)+128(tan22.0061
-tan20)]=1.773
即Zε=√(4-εa)/3=0.862,且ZE=189.8,ZH=2.5
∴σH=ZHZEZε√2KT1(u+1)/bd21u=2.5×189.8×0.862√2×1.397×83510×5.8065/(72×622×5.024)=240.63﹤[σH]=560.28Mpa
∴小齿轮满足接触疲劳强度,且大齿轮比小齿轮接触强度高,故齿轮满足接触强度条件
f.齿轮弯曲疲劳强度校核:
按Z1=32,Z2=128,由[2]图5-14得YFa1=2.56,YFa2=2.18;由[2]图5-15得Ysa1=1.65,Ysa2=1.84
由[2]式5-23计算
Y=0.25+0.75/εa=02.5+0.75/1.773=0.673
由[2]图5-19得YN1=YN2=1.0,
由[2]式5-32切m=2﹤5㎜,得YX1=YX2=1.0
取YST=2.0,Sfmin=1.4,由[2]式5-31计算许用弯曲应力:
[σF1]=σFmin1YFa1Ysa1YST/Sfmin=220×2.0/1.4=314.29Mpa
[σF2]=σFmin2YFa2Ysa2YST/Sfmin=210×2.0/1.4=300Mpa
[σF1]=314.29Mpa
[σF2]=300Mpa
计算内容
计算结果
∵[σF1]﹥[σF2],∴[σF]=[σF2]=300Mpa
由[2]式5-24计算齿跟弯曲应力:
σF1=2KT1YFa1Ysa1Y/bd1m=2×1.397×83510×2.56×1.65×0.673/(2×64×64)=71.233﹤300Mpa
σF2=σF1YFa2Ysa2/YFa1Ysa1=71.233×1.84×2.18/(2.56×1.65)=67.644﹤300Mpa
∴两齿轮满足齿跟弯曲疲劳强度
五,轴的设计计算
9.减速器高速轴I的设计
a.选择材料:
由于传递中小功率,转速不太高,故选用45优质碳素结构钢,调质处理,
按[2]表8-3查得σB=637Mpa,[σb]-1=59Mpa
b.由扭矩初算轴伸直径:
按参考文献[2]有d≥A√p/n
∵n0=960r/min,p1=2.97kw,且A=0.11~0.16
∴d1≥16~23㎜取d1=20㎜
c.考虑I轴与电机伸轴用联轴器联接。
并考虑用柱销联轴器,因为电机的轴伸直径为dD=38㎜,查[1]表4.7-1选取联轴器规格HL3(Y38×82,Y30×60),根据轴上零件布置,装拆和定位需要该轴各段尺寸如图1.2a所示
d.该轴受力计算简图如图1.2b,齿轮1受力:
(1)圆周力Ft1=2T1/dm1=2×29.545/(64×10-3)=915.52N,
(2)径向力Fr1=Ft1·tanα·cosδ1
=915.52×tan200·cos17.70350=317.44N,
(3)轴向力Fa1=Ft1·tanα·sinδ1
=915.52×tan200·sin17.70350=101.33N,
e.求垂直面内的支撑反力:
∵ΣMB=0,∴Rcy=Ft1(L2+L3)/L2=915.52(74+55)/74=1595.97.97N
∵ΣY=0,∴RBY=Ft1-Rcy=915.52-1595.97=-680.45N,
[σF]=300Mpa
σB=637Mpa,
[σb]-1=59Mpa
d1=20㎜
选用柱销联轴器
HL3(Y38×82,Y30×60)
Ft1=915.52N
Fr1=317.44N
Fa1=101.33N
Rcy=1595.97N
RBY=-680.45N
计算内容
计算结果
∴垂直面内D点弯矩Mdy=0,M
=RcyL3+RBY(L2+L3)=1595.97×55-680.45×129=3662.14N·㎜=3.662N·m
f.水平面内的支撑反力:
∵ΣMB=0,∴RCz=[Fr1(L3+L2)-Fa1dm1/2]/L2=[317.44(74+55)-680.45×64]/74=419.07N,
∵ΣZ=0,∴RBz=Fr1-