第三章轴承寿命计算

1、第三章轴、轴承和键的计算§3-1液压部§3-1 I轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩Ti = 295.74N m(1)Zi齿轮对轴的作用力2000T1Pt1 飞L2000 295.74127.424641.97NPr1Pt1tg4641.97tg 22 48 101951.57N渐开线花键因制造安装误差所产生的径向力c2000T1Fq0.22000 295.740.22628.8Nmz3 15求支座反力:(1)水平面的反力:RaxPr1cb c33 361018.21NRbxPr1 Rax1951.57 1018.21 933.36N垂直面的

2、反力:RayPt1cb c46412421.90N33 36RbyPt1Ray4641.972421.902220.07NPo产生的支座反力:DPo(b cRaoa)2628.8(33 36 6.5)2381.16N33 36RboPoRao 2628.82381.16247.64NRaV RaxRayRao合成反力:J1018.2122421.9022381.16 5008.39NRbJrBxrByRboJ933.362 2220.072 247.64 2655.93N二、轴承寿命计算:A点选用:42216ECr = 130000 Nn = 1453 r/minRaf P5008.39 1.

3、57512.59NLh竺（H）60n PCr10（13000060 14537512.59106153731hB点选用:42217ECr = 155000 Nn =1453 r/minRb fP 2655.93 1.53983.90NLhCr106（工）60n P 60 145310155000 3983.90-2289079h三、渐开线花键强度验算:挤压强度 P2Tz h l Dmp式中：T转矩，N mm各齿载荷不均匀系数，一般取屮=0.7 0.8齿数齿的工作高度，mm齿的工作（配合）长度，mmDm平均直径，mm许用比压，MpaT= 295.74N mW= 0.75z = 15h = m =

4、 3mml = 55mmDm = m z =3 X15 = 45mmp =100 140MpaP 2 295.74 10007.08M Pa0.75 15 3 55 45§3-1 n轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩 T2 = 382.56N mPt22000T2d22000 382.564551.85N168.09Pr2Pt2tg4551.85tg22 48 101913.68N不考虑效率损失:P't2 R2Pr2Pt2tg4551.85tg22 43 161906.05NP2X(1) Pt2、Pr2在X、Y方向的力P2YR2YPr2Y445

5、7.11388.404068.71N P2、Pr2 在 X、Pr2XPr2 cos1906.05 cos27.261694.36 NPt2XPt2 sin4551.85sin 27.262084.88 NPr2Y1Pr2 sin1906.05sin 27.26873.03NPt2YR2 cos4551.85cos27.264046.31n丫方向的力XYPt2YP r2YPr2XPt2X1694.36 2084.88 3779.24NP2XP2Y4046.31873.033173.28NPr2XPr2 COS1913.68cos11.711873.85NR2XPt2 sin4551.85si n

6、11.71923.84NPr2YPr2 sin1913.68si n11.71388.40NR2YPt2 cos4551.85cos11.714457.11NXY1873.85 923.842797.69NPt2XPr2X在X、丫方向的合力P XP2XP2X3779.24 2797.69981.55NPyP2YP2Y4068.713173.287241.99N2、求支座反力:PV'PxV'981.552 7241.9927308.21NRaRb7308.213654.11N二、轴承寿命计算:A、B两点均选用：53511Cr = 92200 Nn = 1100.76 r/minL

7、hRa fp 3654.111.51065481.17N60 1100.7610(92200 p 5481.17184650h§3-1 3 m轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩 T2 = 306.74Nc2000T3Pt3'ds2000 306.744460.70N137.53Pr3Pt3tg4460.70tg22 43 161867.88N不考虑效率损失:Pt3Pt3Pr3XPr3 COS1867.88cos27.261660.43NXP3XPt3 sin4460.70sin 27.262043.13NPr3YPr3 sin1867.88si

8、n 27.26855.54NYPt3YPt3 cos4460.70cos27.263965.28NP3XP r3XP3X1660.432043.133703.56NP3YPt3YPr3Y3965.28 855.543109.74NPr3Pt3tgPt3、Pr3在X、Y方向的力R3、Pr3 在 X、丫方向的力(1)4460.70tg22 43 161867.88NPr3XPr3 COS1867.88cos15.171802.79 N1xPt3XPt3 Sin4460.70si n 15.171167.29NPr3YPr'3 sin1867.88s in 15.17488.79N1YPt3

9、YPt3 cos4460.70cos15.174305.26 NP3XPr3XR3x 1802.791167.292970.08NP3YPt3YPr3Y 4305.26488.793816.47NPxP3XP3X3703.56 2970.08733.48NPYP3YP3Y3109.743816.476926.21N在X、丫方向的合力渐开线花键因制造安装误差所产生的径向力P02000T30.22000 306.74 0.22921.33Nmz2 21求支座反力:(1)水平面的反力:PxcRax733.48 35.5295.89N52.5 35.5RBXP XRax733.48 295.89437

10、.59N垂直面的反力:RPy cRay6926.21 35.52794.10N52.5 35.5RbyPyRay6926.212794.104132.11NPo产生的支座反力:DPo(a bRaoc)2921.33(552.535.5)3087.31N52.535.5RboRao Po 3087.31 2921.33 165.98N(4)合成反力:Ra JrAx RAy Rao J295.8922794.1023087.315897.03NRbJrBxrByRboJ437.592 4132.112165.98 4321.20N二、轴承寿命计算:A点选用:42514ECr = 145000 N=

11、1345.37 r/minRaf P5897.03 1.58845.55NLh竺（H）60n PCr10（145000 P60 1345.378845.55106138617hB点选用:53511Cr = 92200 Nn =1345.37 r/minRb fP 4321.20 1.56481.8NLhCr106（工）60n P 60 1345.371092200 -T （）386389h6481.8三、渐开线花键强度验算:挤压强度 P2Th l DmpT= 306.74N mW= 0.75z =21h = m = 2mml = 27mm=m z =2X21 = 42mmp =100140Mp

12、a2 306.7410000.75 212 27 4217.17M Pa§3-1 4 W轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩T4 = 367.41N mPt42000T4d42000 367.41168.094371.59NPr4Pt4tg4371.59tg22 43 161830.57N不考虑效率损失:Pt4Pt4P r4Pt4tg4371.59tg22 47 511837.42NPt4、Pr4在X、丫方向的力Pr4XPr4 COS1830.57 cos15.171766.78 NXPt4XPt4 sin4371.59si n 15.171143.97

13、 NPr4YPr4si n1830.57 si n15.17479.03NYPt4YR4 cos4371.59 cos15.174219.26NP4XPr4XPt4X1766.78 1143.972910.75NP4YR4YPr4Y 4219.26479.033740.23NPr'4 在 X、丫方向的力P r4X1Pr4 cosi1837.42 cos4.721831.89N1XPt4XPt4 sin4371.59si n4.72359.72Pr4Y1Pr4 sin1837.42si n4.72151.19N1YPt4YR4 cos4371.59cos4.724356.76 NP4XP

14、r4XPt4X1831.89 359.722191.61N151.194205.57NP4YZ7作用在轴上的力：输入扭矩Ft4YPr4Y4356.76Pt'4、T7 =272.77N mPt72OOOT72000 272.77d7127.424281.43NPr7Pt7tg4281.43tg22 48 101799.99N1050.89NPt7、Pr7在X、丫方向的力R7XPt7 sin4281.43sin 54.283476.01NPr7YPr7Si n1799.99sin 54.281461.38NPt7YR7 cos4281.43cos54.282499.6 NP7XPt7XPr

15、7X3476.011050.892425.12NP7YR7YPr7Y2499.6 1461.383960.98 NPr7 COS1799.99cos54.28Y(4)在X、丫方向的合力Pr7XPXP7XP4XP4X2425.12 2191.612910.751705.98NRyP7YP4YP4Y 3960.984205.573740.2311906.78N2、求支座反力:P2J1705.982 11906.78212028.37NRaRb12028.376014.19N二、轴承寿命计算:A、B两点均选用：53511Cr = 92200 Nn = 1100.76 r/minRa fP 6014.

16、191.59021.29NLh10660 1100.7692200J 9021.2910W 35078h§3-1 5 V轴键联接的强度验算1、键的挤压强度2Tp E p式中：T转矩，N mm轴的直径，mm键与轮毂的接触高度，mm，平键k=h/2键的工作长度，对于 A型键l=L-bp键联接的许用比压，MpaT = 316.42 N mD = 40mmk = h/2 = 8/2 = 4mml = 70-12 = 58mmp = 100 120 Mpa2 316.42 P1000404 5868.19 MPa2、键的剪切强度2TD b l 式中：T转矩,N mm轴的直径，mm键的宽度，mm

17、键的工作长度，对于 A型键l=L-b键联接的许用剪应力,MpaT=316.42 N mD =40mmb = 12mml = 58mmT = 90 MPa2 316.42 100022.73MPa40 12 58§3-1 6 TO轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩T7 = 6.87N mPt72000T72000 6.87d7127.42107.83NPr7Pt7tg107.83tg 22 48 1045.33N求支座反力:(1)水平面的反力:Pr7Raxa45428.01N3455RBXP r 7Rax 45.33 28.0117.32N垂直面的反力:

18、RAY严 b107.83 5566.64N34 55RbyPt7 Ray 107.83 66.64 41.19N合成反力:Ra J Rax Ray Rb 丿 Rbx RbyP28.01266.64272.29NJ17.32241.19244.68N、轴承寿命计算:A点选用:110Cr = 16800 Nn = 1453 r/min106Ra fp 72.29 1.5108.44NLh垃 Z)一(型00)342652300h60n P 60 1453108.44B点选用:110Cr = 16800 Nn = 1453 r/minRB fp 44.68 1.567.02NLh10660n P 60

19、 145316800 )3 180674853h67.02§3-2牵引部§3-2 I轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩T1 = 220.15N m(1)Z1齿轮对轴的作用力Pt1 2000Td12000 220.1578.695595.37NPr1Ptdg5595.37tg21 20 462186.73N渐开线花键因制造安装误差所产生的径向力Po12000T10.22000220.150.22446.11Nmz2 18P 02= P01求支座反力:(1)水平面的反力:RaxPr1 cb c沁口 385.89N23851RbxPr1Rax218

20、6.73 385.89 1800.84N垂直面的反力:Ray5595987.42N23851rbyPtiRay5595.37 987.42 4607.95NPoi产生的支座反力:RAO1Poi(a b c)如6.11 (9238 51)2522.29N238 51Rbo1Raoi Poi 2522.292446.1176.18NPO2产生的支座反力:RBO2Po2(b c d) 2446.11(238 515)2543.45N238 51Rao 2RbO2 PO2 2543.452446.1197.34N(5)合成反力：RaJrAxRayRao1Rao2 寸 385.892987.422252

21、2.29 97.343679.78NRBVRBXRBYRBO1RBO2山800.8424607.95276.18 2543.457566.98、轴承寿命计算:A点选用:42212ECr = 88800 N=565.24 r/minRa fP 3679.78 1.55519.67NLhCr10660 565.24(88800'5519.67103309943hB点选用:53512Cr = 110000 N=565.24 r/minRb fp 7566.98 1.511350.47NLhCr10660 565.24(8880011350.4710328029h三、渐开线花键强度验算:挤压强

22、度 P2Tz h l DmpT= 220.15N mW= 0.75z =18h = m = 2mml = 45mmDm = m z =2 X18 =36mm106p =100 140Mpa2 220.15 1000P 0.75 18 2 45 3607"Pa§3-2 2 n轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩 T2 = 506.18N mPt22000T2d22000 506.185483.18N184.63P r2Pt2tg5483.18tg21 20 462142.89N不考虑效率损失:P't2 R2Pr2Pt2tg5483.18t

23、g20 14012021.07N水平方向:PxPr2Pr22142.892021.07121.82N垂直方向:PyP2Pt25483.185483.1810966.36N由一只轴承在轴上P AXPX121.82NP AYPY 10966.36 N10967.04NPA JpAX pAY 121.82210966.362、轴承寿命计算:A点选用:53609Cr = 128000 N=240.92 r/minRA fp 10967.04 1.516450.56NLh比(刍一10 ( 12800060n P 60 240.9216450.5610364576.35h§3-2 3 m轴的轴承

24、寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩 T3 =585.51N mZ3齿轮对轴的作用力Pt32000T32000585.515413.37Nd3216.32Pr3Pt3tg5413.37tg20 14011995.34N渐开线花键因制造安装误差所产生的径向力Po2000T30.22000 585.510.21672.89Nmz4 35求支座反力:(1)水平面的反力:RaxPr 3cb1995.34 1411 141117.39NRbXPr3Rax 1995.341117.39877.95N垂直面的反力:RayPt35413.37 1411143031.49NRbypt3Ra

25、y5413.373031.492381.88NPo产生的支座反力:rboPo(a braopoc)曲89(34 1114)3948.02N11143948.02 1672.892275.13NRaJ RaxRay(4)合成反力：Rao J1117.3923031.4923948.027178.89 NRbJrBxrByRboJ877.952 2381.882 2275.13 4813.66N二、轴承寿命计算:A点选用:61924Cr = 55300 Nn = 204.11 r/minRaf P7178.89 1.510768.34NLh10660n（H）106（且乞）3 11059hP 60

26、204.1110768.34CrB点选用:61924Cr = 55300 Nn = 204.11 r/minRbP 4813.66 1.57220.49NLh10660 *）60n P 10660204.11（旨也）336683h7220.49§3-2 双行星机构、轴承寿命计算: 一级行星轮心轴 1、轴的受力分析:(1)传动件作用在轴上的力:输入扭矩 Ta Ta Kfp 585.511.15673.34N m太阳轮对行星轮的切向力Rac2000Ta2000Cs dA 3 67.678673.346632.78N内齿圈对行星轮的切向力PBC P C(2)求支座反力:由两轴承支承在轴上A

27、、B两点P PaPb-6632.78NcPA（b c） Pb c 6632.78（37 23.5） 6632.78 23.5R1223723.56753.38NR2PAPBR16632.78 6632.78 6753.386512.18NI2、轴承寿命计算:选用两只22208ECr = 89700 Nncx =98.83 r/minnA nxZcncxZancx(nAZc4.1136.857)1398.83r/min22动载系数Fk =1.5旋转系数Fn =1.1PPaFkFn6632.78 1.5 1.110944.09N60ncx(即60 98.83 ( 10944.0910沁 P 187

28、213.二级行星轮心轴1、轴的受力分析:(1)传动件作用在轴上的力:输入扭矩 Ta Ta Kfp 3145.28 1.15 3617.07N m太阳轮对行星轮的切向力Rac皿 20003617.0735630.19Ncs dA 3 67.678内齿圈对行星轮的切向力PtbcP c(2)求支座反力:由两轴承支承在轴上B两点PaRbRacRbc35630.19NRiPA(b c) Pb c 35630.19(3723.5)35630.19 23.5223723.536278NR2PaPbRi 35630.1935630.19 3627834982.38N2、轴承寿命计算:选用两只22208ECr

29、= 89700 Nn cx =17.847 r/minnAnxncxZcZ7ncx(nA咖576.655)1317.847r/minZc22动载系数Fk =1.5旋转系数Fn =1.1PPaFkFn35630.191.5 1.158789.8N106Lh60nCX10660 17.84710 (89700 尸 58789.8)3819h三、渐开线花键强度验算:挤压强度 P2Th l Dm P1、对一级太阳轮轴T= 585.51N mW= 0.75z =35h = m = 4mml = 20mmDm=m z =4 X35 =140mmp =100 140Mpa2 585.51P 0.75 35

30、4 20 1403.98 MPa2、对二级太阳轮轴T= 3145.28N mW= 0.75z =13h = m = 5mm1000l = 30mmDm = m z =5 X13 =65mmp =100140Mpa2 3145.28 10000.75 13 5 30 6566.17M Pa§3-2 5 V轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩T5 =16896N m(1)Z10齿轮对轴的作用力2000T5Pt102000 16896d1039.79 6141543.1NPr10Rgtg141543.1tg2051517.48N渐开线花键因制造安装误差所产生的

31、径向力P0沁0.22000 16896 0.264365.7Nmz5 21求支座反力:(1)水平面的反力:DPr10cRax51517.48 8722188.22N115 87RbxPr10 Rax 51517.48 22188.22 29329.26N垂直面的反力:DPt10cRay141543.1 8760961.63N115 87RbyPt10 Ray 141543.1 60961.63 80581.47NPo产生的支座反力:PO(a b c)Rao64365.7(55115 87)81891N115 87RboRao Po8189164365.717525.3N合成反力：RaJ Rax

32、RayRaoJ22188.22260961.63281891 146765NRbJ RbxRbyRboJ29329.262 80581.4721 7525.3 1 03278.3N二、轴承寿命计算:A点选用:42224ECr = 315000 Nn = 6.655 r/minRa fP 146765 1.5220147.5NLh岸）60n P10631500060 6.655 J 220147.51038267hB点选用:3053124Cr = 262000 Nn = 6.655 r/minRb fp 103278.3 1.5154917.45NLh（6）60n P10660 6.655（26

33、2000154947.4510"314424h三、渐开线花键强度验算:挤压强度2Th l DmpT= 16896NW= 0.75z =21h = m =5mml = 55mm=m z =5X21 =105mmp =100 140Mpa2 16896 1000P 0.75 21 5 55 10574.3MPa§3-3截割部§3-3 I轴的轴承寿命计算、轴的受力分析: 1、传动件作用在轴上的力：输入扭矩 T1 =857.46N m(1)Zi齿轮对轴的作用力Pt1沁 2000 857.41 13887.12Nd1123.49Pr1Rjtg13887.12tg 24 03

34、 296199.81N(2)渐开线花键因制造安装误差所产生的径向力c2000 T10.22000857.460.27145.5Nmz3 162、求支座反力:(1)水平面的反力:RaxPr1cb c整竺空3029.13N5653.5RbxPr1Rax6199.81 3029.13 3170.68N(2)垂直面的反力:Ray2 輕竺空 6785.03N5653.5RbyPt1 Ray 13887.12 6785.03 7102.09N(3) Po产生的支座反力:RaoPO(b c a)7145.5(56 53.5 2) 7014.99N5653.5RboPo Rao7145.5 7014.99 1

35、30.51N(4)合成反力:Ra JrAx RAy Rao J3029.1326785.0327014.99 14445.49NRbJ RbxRbyRboJ3170.6827102.092130.517908.23N二、轴承寿命计算:A点选用:NJ2217ECCr = 187000 Nn = 1470 r/minRa fP 14445.491.521668.24NLhCr106P)60n P 60 147010187000 p21668.24)14948hB点选用:53515Cr = 145000 Nn = 1470 r/minRb fp 7908.23 1.511862.35NLh10660

36、35三、渐开线花键强度验算:挤压强度 P2Th l DmPT= 857.46N mW= 0.75z =16h = m =3mml = 70mm=m z =3X16 =48mmp =100140Mpa2 857.46 10000.75 16 3 70 4814.18M Pa§3-3 2 n轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩T2 =1260.74N mPt2 2000T22000 1260.74185.24d213609.05NPr2P 2tg13609.05tg 24 03 296075.67N不考虑效

37、率损失:P't2Pt2Pr2Pt2tg13609.05tg21 11 475277.62N水平方向:PxPr2 Pr'2 6075.67 5277.62 798.05N垂直方向:& R2R213609.05 13609.0527218.1N求支座反力由两只轴承支承在轴上A、B两点(1)PaxPbxPayPbyPx2Py798.0527218.1399.025N13609.05NpP AX(bC)P BXc 399.025(3450)399.025 50R1Xab c393450P2XP AXPBXR1X798.05434.71363.34N(2)垂直面的反力:pPAY(

38、bC)PBYc 13609.05(3450)13609.05 50R1Yab c393450水平面的反力:434.71N14826.12NP2YR1y27218.1 14826.1212391.98N(3)合成反力:RiJR1xR1YJ434.71214826.12214832.49NR2Q R2 XR2YJ363.342 12391.98212397.31N、轴承寿命计算:A、B两点均选用53514Cr = 140000 Nn = 980 r/minPAPBJ PaxPayJ399.O252 13609.052 13614.89NP Ra fp 13614.891.520422.34NLh

39、需(P)60 980Cr106(丄空吗善10408h20422.34§3-3 3 m轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩T3 =1811.71N mZ3齿轮对轴的作用力2000T3Pt3d32000 1811.71266.0813617.78NPr3Pt3tg13617.78tg21 11475281NZ4齿轮对轴的作用力Pt42000T3d42000 1811.71148.1924451.18NPr424451.18tg24 03 2910916.07N求支座反力(1)水平面的反力:RaxPr3 (bc) Pr4 c 5281(83.569)10916

40、.07 69b c58 83.5 69247.71NPbxPaxPr4Rr3 247.7110916.0752815882.78N垂直面的反力:RayPt3(ba b cc) Pr4 c 13617.78 (83.5 69)24451.1858 83.5 696917880.49NPbYPt3Pt4 Ray13617.78 24451.18 17880.49 20188.47N合成反力:Ra JrAx RAy J247.712 17880.49217882.21NRb JrBx RBy V5882.78220188.47221028.11N二、轴承寿命计算:A点选用:53520Cr = 275

41、000 Nn = 668.182 r/minRA fp 17882.21 1.526823.32NLh106B点选用:106 g)106( 27500060n (P) 60 668.182 ( 26823.3242318ECr = 295000 N10358392h=668.182 r/minRB fp 21028.11 1.531542.17NLh106已60n (10660 668.182295000(31542.171042992h三、键的强度验算:1、键的挤压强度2TpT=1811.71 ND =120mmk = h / 2 = 18/2 = 9mm54mmp =100 120 MPa

42、2 1811.71 1000120 9 5462.13 MPa2、键的剪切强度2TD b l T=1811.71 ND =120mmb = 32mml = 54mmT = 90 MPa1811.711000 仃.47MPa120 32 54§3-3 W轴的轴承寿命计算、轴的受力分析: 1、传动件作用在轴上的力：输入扭矩 T4 =3156.4N mPt52000T42000 3156.4d5263.45Pr5Rstg'23962.04tg 24 03 2910697.69N不考虑效率损失：P 't5Pt5Pr5Pt5tg23962.04tg22 34 169960.26

43、 N(1)R5、Pr5 在 X、丫方向的力Pr5XPr5 cos9960.26cos40.737547.81N1XPt5XR5Si n23962.04 si n40.7315635.12NPr5YPr5Sin9960.26sin 40.736499.02N1YPt5YPt5 cos23962.04cos40.7318158.26NP5X1Pr5XPt5X7547.81 15635.12 23182.93NP5YPt5YPr'5Y 18158.26 6499.0211659.24 N在X、Y方向的合力PxP5XPr5 23182.93 10697.69 12485.24 NPyFt5PsY23962.04 11659.24 35621.28 N2、求支座反力由两只轴承支承在轴上A、B两点Px12485.246242.62N PaxPbxPAYPBYPy35621.2817810.64N(1)水平面的反力:R1XP AXc)PBXc6242.62 (46 126.5)6242.