二级 减速器 说明书 斜齿轮 锥齿轮

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·················································································22.工作机的有效功率···········································································23.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····················································································32.各轴的转速····················································································33.各轴的功率····················································································44.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·················································42.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·····································································95.减速器低速轴II的设计··································································113.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·········································162.减速器低速II轴滚动轴承的选择与寿命计算········································173.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··························································192.大圆锥齿轮与低速轴II的的键联接····················································193.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·········································································212.润滑油的选择·················································································22九¸参考文献························································································231.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/minb.计算工作机功率pw=nw/9.55×10³=248×67.326/9.55×10³=1.748Kw2.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=0.99D=300㎜F=2400NV=1.0m/sL=11年nw=67.326r/minpw=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=0.97b.总效率η=η1η22η33η4η5η6=0.96×0.992×0.983×0.99×0.95×0.97=0.808c.所需电动机的输出功率Pr=Pw/η=2.4/0.808=3kw3.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1Y100L2-431500142022.2942Y132S-63100096015.072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/min8.各轴的功率η=0.808Pr=3kw选用三相异步电动机Y132S-6p=3kwn=960r/mini=15.072i12=3.762i23=4n0=960r/minn1=960r/minn2=303.67r/minn3=63.829r/minn4=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=2.550kw4.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=210Mpab.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=1.267×109N2=N1/i2=1.267×10/3=2.522×108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=533.6Mpac．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=72.2965o=72o1635，δ1=17.7035o=17o4212，则小圆锥齿轮的当量齿数zm1=z1/cosδ1=21/cos17.7035o=23，zm2=z2/cosδ2=79/cos72.2965o=259.79p0=3kwp1=2.970kwp2=2.965kwp3=2.628kwp4=2.550kwT0=29.844N·mT1=29.545N·mT2=86.955N·mT3=393.197N·mT=381.527N·mσHP1=580Mpa，σFmin1=220MpaσHP2=560Mpa，σFmin2=210Mpa[σH]=533.6Mpa圆锥齿轮参数Z1=21Z2=79δ1=17o4212δ2=72o1635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=1.81ZH=√2/cosα×sinα=√2/cos20o×sin20o=2.5由[2]表11-5有ZE=189.8，取Kt·Z2εt=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/{фRZ21[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+6cos72.2965o=238.827㎜齿根圆直径df1=d1-2.4mcosδ1=63-7.2cos17.7035o=56.142㎜df2=d2-2.4mcosδ2=237-7.2×cos72.2965o=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5-53σH=ZHZE√2KT1√u+1/[bd21u（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/sb=36.78㎜Δ1=10㎜Δ2=14㎜c=10㎜L1=12.4㎜L2=39㎜计算内容计算结果σH=470.