第三章轴承寿命计算

《第三章轴承寿命计算》由会员分享，可在线阅读，更多相关《第三章轴承寿命计算（46页珍藏版）》请在装配图网上搜索。

1、第三章轴、轴承和键的计算 3-1液压部 3-1 1 I轴的轴承寿命计算一、轴的受力分析：1、传动件作用在轴上的力：输入扭矩 Ti = m(1) Z 1齿轮对轴的作用力m2OOOT12000 295.74Pt1 4641.97 Nd1127.42Pr1Pt1tg 4641.97tg22 48 101951.57N(2) 渐开线花键因制造安装误差所产生的径向力P。mz2000 295.743 150.22628.8N2、求支座反力:(1) 水平面的反力:Pr1cb c1951.57 3633 361018.21NRBXPr1 Rax 1951.57 1018.21 933.36N(2) 垂直面的反

2、力:Pt1cb c4641.97 3633 362421.90NRby P1Ray4641.972421.902220.07N(3) Po产生的支座反力:Po(b c a)Rao,b c2628.8 (33 366.5)Kl2381.16 N33 36Rbo Po Rao 2628.82381.16247.64N(4) 合成反力：5008.39N2655.93NRa. RAXRAyRao1018.212 2421.902 2381.16RbrBxRBy Rbo933.362 2220.072 247.64二、轴承寿命计算:A点选用：42216ECr = 130000 N n = 1453 r/

3、minP RafP 5008.39 1.5 7512.59NLh需岸）10660 145310/ 130000 、可 )37512.59153731hB点选用：42217ECr = 155000 N n =1453 r/minP Rb fp2655.93 1.5 3983.90N10155000 可)32289079h3983.90106Cr（） 60n P、渐开线花键强度验算:挤压强度 P式中：Lh10660 14532Tz h转矩，N mm各齿载荷不均匀系数，一般取W 齿数Dmph 齿的工作高度，mml 齿的工作（配合）长度，mmD m 平均直径，mmp 许用比压，MpaT= mW = z

4、 = 15 h = m = 3mml = 55mm D m = m - z = 3X 15 = 45mmp =100140Mpa2 295.74 10000.75 15 3 55 457.08MPaT2 = m4551.85N 3-1 2 H轴的轴承寿命计算一、轴的受力分析：1、传动件作用在轴上的力：输入扭矩Pt22T220 382.56t2d2168.9Pr2Pt2tg 4551.85tg22 48 101913.68N不考虑效率损失： Pt 2Pt2Pr2Pt2tg 4551.85tg22 43 161906.05N(1) Pt2、Pr2在X、Y方向的力Pr 2XPr 2 cos1913

5、.68 cos11.711873.85NXPt2XPt 2 sin4551.85sin11.71923.84NPr 2YPr 2 sin1913.68sin11.71388.40NYPt 2YPt 2 cos4551.85cos11.714457.11NP2XPr 2XPt 2 X1873.85 923.84 2797.69NP2YPt2YPr 2Y4457.11 388.40 4068.71NP2、Pr2在X、丫方向的力Pr2XPr2 cos1906.05 cos27.261694.36NXPt2XPt2 sin4551.85sin 27.262084.88NPt2YPt2 cos4551.

6、85 cos27.264046.31NPr2YPr2 sin1906.05sin 27.26873.03NP2XPr 2XPt 2 X1694.362084.883779.24NP2Yp2YPr 2Y4046.31873.033173.28N在X、丫方向的合力PXP2XP2X3779.242797.69981.55NYPYP2Y P2Y 4068.71 3173.28 7241.99N2、求支座反力：PPX PY981.552 7241.992P 7308.21Ra Rb3654.11N2 2二、轴承寿命计算：7308.21Nn = r/minA、B 两点均选用：53511 Cr = 9220

7、0 NLh 3-1 3(C1)60n P 60 1100.76皿轴的轴承寿命计算1092200)35481.17184650h、轴的受力分析:1、传动件作用在轴上的力：输入扭矩 T2 = mPt32000T32000 306744460.70Nd3137.53Pr3Pt3tg4460.70tg2243 161867.88NPr3 在 X、丫方向的力Pr3XfPr3 COS1867.88cos27.261660.43NP3XPt3 sin4460.70sin 27.262043.13NPr3YrPr3 sin1867.88sin 27.26855.54NPt3YPt3 cos4460.70cos

8、27.263965.28N1867.88N4460.70tg2243 16P3X1660.432043.133703.56NP3XPr3XPt3Pt3(1) P t3、Pr3Pt3tg不考虑效率损失:P3YPt3YPr3Y3965.28 855.543109.74N(2) P3、Pr3 在 X、丫方向的力1Pr 3XPr3 COs1867.88cos15.171802.79N1XPt3XP3 sin4460.70 si n 15.171167.29N!Pr3YPr3 sin1867.88s in 15.17488.79N1YPt3Y1Pt3 cos4460.70cos15.174305.26N

9、P3XP r3XP3X1802.791167.292970.08NP3YPt3YPr3Y4305.26488.793816.47N在X、丫方向的合力P XP3XP3X3703.562970.08733.48N(4)渐开线花键因制造安装误差所产生的径向力Po200匹 0.22000 306.74 0.22921.33Nmz2、求支座反力：2 21(1) 水平面的反力:PXcRaxX733.48 35.5295.89N52.535.5RbxPx Rax733.48 295.89 437.59N(2) 垂直面的反力:PY cRay6926.21 35.52794.10Nb c 52.5 35.5Rb

10、y R Ray 6926.212794.104132.11N(3) P。产生的支座反力:P(a b c)Rao29233 (5 52.535.5)3087.31N52.5 35.5合成反力：RaRaxRayRboRao Po 3087.31 2921.33 165.98NRao295.892 2794.102 3087.31 5897.03N165.98 4321.20NRB_rBxRByRbo437.592 4132.112、轴承寿命计算：A点选用：42514ECr = 145000 N n = r/minP Rafp 5897.03 1.5 8845.55N10660n6 1010/ 14

11、5000( )360 1345.378845.55138617hB点选用：53511Cr = 92200 N n = r/min86389h加）P RB fP 4321.20 1.5 6481.8N、渐开线花键强度验算:挤压强度T= mP2Tpz h l DmW =z =21h = m = 2mml = 27mmDm = m - z = 2X 21 = 42mmp =100140Mpa17.17MPap 2 306.74 10000.75 212 27 42 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 = m2000T4d42000 367.4116

12、8.094371.59NPr4Pt4tg 4371.59tg22 43 161830.57N不考虑效率损失：Pt4Pt4Pr4Pt4tg 4371.59tg22 47 511837.42N(1) P t4、Pr4 在 X、丫方向的力Pr4XPr4 cos1830.57COS15.171766.78NXPt4XPt4 sin4371.59sin15.171143.97NPr4YPr4s in1830.57si n15.17479.03NYR4YPt4 cos4371.59cos15.174219.26NP4XPr4XPt4X1766.78 1143.97 2910.75NP4YR 4YPr4Y

13、4219.26479.033740.23N P4、Pr4 在 X、丫方向的力1Pr 4XPr4 cos1837.42 cos4.721831.89NxPt4XPt4 sin4371.59sin 4.72359.721P r4YPr4 sin1837.42sin4.72151.19N1YPt4YP4cos4371.59cos4.724356.76N11P4XPr 4XPt4x1831.89 359.72 2191.61N11PP4Yt4YPr4Y 4356.76151.194205.57NZ 7作用在轴上的力：输入扭矩T7 = mPt72000T72000 272.77127.424281.43

14、NPr7Pt7tg4281.43tg 22 48 101799.99 NPt7、Pr7 在 X、丫方向的力Pr 7XPr7 cos1799.99cos54.281050.89NXP7XPt7 sin4281.43sin 54.283476.01NPr7YPr7 sin1799.99sin 54.281461.38NYP7YR7 cos4281.43cos54.282499.6Nd；P7XR7x Pr7X 3476.01 1050.89 2425.12NP7YR7Y Pr7Y2499.6 1461.38 3960.98N在X、Y方向的合力PxP7XP4XP4X2425.12 2191.61291

15、0.751705.98N&P7Y1P4YP4Y 3960.98 4205.573740.2311906.78N2、求支座反力：P .Px戌1705.982 11906.78212028.37NP12028.37RaRb26014.19N2二、轴承寿命计算A、B两点均选用：53511Cr = 92200 Nn = r/minPRa9021.29NP 6014.19 1.5Lh106 3-1 51、键的挤压强度 p 式中：T 转矩，N轴的直径，0)60n P 60 1100.76V轴键联接的强度验算2TD k lmmPmm键与轮毂的接触高度, 键的工作长度，对于10)335078h9021.299

16、2200mm 平键 k=h/2A型键l=L-bp键联接的许用比压，MpaT = N m D = 40mm k = h/2 = 8/2 = 4mml = 70-12 = 58mm p = 100120Mpap 2 31&42 1000 68.19MPa40 42、键的剪切强度式中：T 转矩，N轴的直径，键的宽度，582T D b l mmmmmm键的工作长度，对于 A型键l=L-bt 键联接的许用剪应力，MpaT= N m D =40mm b = 12mm l = 58mm t = 90 MPa22.73MPa2 316.42 100040 12 58 3-1 6叫轴的轴承寿命计算-、轴的受力分

17、析：1、传动件作用在轴上的力：输入扭矩 T7 = mPt72000T7d；2000 6.87127.42107.83NPr7 Pt7tg 107.83tg 22 48 1045.33N2、求支座反力：(1) 水平面的反力：mPr7b45.3355Rax28.01Na b3455RbxPr7Rax45.33 28.01 17.32N(2) 垂直面的反力:R7 ba b107.83 5534 5566.64NRbyR7 Ray107.83 66.64 41.19N72.29N44.68N合成反力：Ra、rAxRAy28.012 66.642Rb rBxRBY17.322 41.192二、轴承寿命计

18、算：P RA fp 72.29 1.5 108.44N占岸）60n P10660 1453（ 16800）3k 108.44）42652300hB点选用：110Cr = 16800 Nn = 1453 r/minP RbfP 44.68 1.5 67.02N106Cr10616800 3Lh（）（）180674853h60n P 60 145367.02 3-2牵引部 3-2 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 T1 = m(1) Z 1齿轮对轴的作用力Pt12000T1d；2000 220.1578.695595.37NPr1 P/g 5595.37t

19、g21 20 462186.73N(2) 渐开线花键因制造安装误差所产生的径向力2000T1mz0.22000220.152 180.22446.11NPO2=Pb12、求支座反力：(1) 水平面的反力:Pr1 Cb c2186.73 51238 51385.89NRbxPr1 Rax2186.73 385.89 1800.84 N(2) 垂直面的反力:厂Pti c 5595.37 51 门“Ray987.42Nb c 23851RbyR1 Ray5595.37 987.42 4607.95NP O1产生的支座反力：Poi(a b c)b c2446.11 (9 238 51)238 5125

20、22.29NRbO1RaO1 PO1 2522.29 2446.11 76.18NPo2产生的支座反力：P2(b c d) 2446.11 (238 5111.5)2543 45Nb c23851RAO2RBO2巳22543.45 2446.1197.34N(5)合成反力:Ra:. RaxrAyRAO1RAO2.385.8922987.422522.2997.343679.78NRbRBxrByRBO1RBO2、1800.84224607.9576.182543.457566.98二、轴承寿命计算：A 点选用：42212E Cr = 88800 N n = r/minP Ra fP 3679.

21、78 1.5 5519.67N防)6 10309943h106/ 88800 巧60 565.245519.67B点选用：53512Cr = 110000 N n = r/min加)28029hP Rb fP 7566.98 1.511350.47N6 1010/88800 、三60 565.2411350.47三、渐开线花键强度验算:挤压强度P2Tz h l DmpT= mW = z =18 h = m = 2mml = 45mm D m = m - z = 2X 18 =36mmp =100140Mpa2 220.15 100010.07MPa0.75 18 2 45 36 3-2 2 H

22、轴的轴承寿命计算一、轴的受力分析：Pt22000T2d22000 506.18184.635483.18N1、传动件作用在轴上的力：输入扭矩 T2 = mPr2 Pt2tg 5483.18tg21 20 462142.89N不考虑效率损失：Pt2 R2Pr2 Pt2tg 5483.18tg20 14 012021.07N水平方向：PXPr2 Pr2 2142.89 2021.07 121.82N垂直方向：Py R2 FL 5483.18 5483.1810966.36N由一只轴承在轴上A点PaxPx 121.82NPAY PY 10966.36NPAPAXPAY121.822 10966.36

23、2 10967.04N二、轴承寿命计算:A点选用：53609Cr = 128000 Nn = r/minP Ra fP 10967.04 1.516450.56NLh加）6 1010/ 128000 、三( )360 240.9216450.5664576.35h 3-2 3皿轴的轴承寿命计算一、轴的受力分析：1、传动件作用在轴上的力：输入扭矩 T3(1) Z 3 齿轮对轴的作用力Pt32000T32000 585.515413 37Nd3216.32Pr3Pt3tg5413.37tg20 14 011995.34N(2) 渐开线花键因制造安装误差所产生的径向力2000T3Po3mz2、求支座

24、反力：0.22000 58551 0.24 351672.89N(1)水平面的反力:Pr3 cb c1995.34 1411141117.39NRbxPr3 Rax1995.34 1117.39 877.95N(2) 垂直面的反力：厂Pt3 c 5413.37 14Ray一3031.49Nb c 1114RbyR3 Ray 5413.37 3031.49 2381.88N(3) P。产生的支座反力：RaoPo(abc) 1672.89 (3411 14)o94o 02Nbc11143948. 02RboRaoPo3948.02 1672.892275.13N(4)合成反力：4813.66NRb

25、rBx rBy Rbo877.952 2381.882 2275.13二、轴承寿命计算：A 点选用：61924 Cr = 55300 N n = r/mi nP RA fp 7178.89 1.510768.34N611059h10( 55300 )360 204.11( 10768.34)P RB fp 4813.66 1.57220.49NLh 3-2 410-（吕）60n P双行星机构、轴承寿命计算:10660 204.11（55300 ）3k 7220.4936683h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 p 585.51 1.15太阳轮对行

26、星轮的切向力673.34N m厂200CTa2000 673.34P A tACCs dA 3 67.678内齿圈对行星轮的切向力6632.78NPtBCRac（2）求支座反力： 由两轴承支承在轴上A、B两点，二 PA PB P PtAC PtBC 6632.78N2 2厂PA（b c） PB c 6632.78（37 23.5） 6632.78 23.5R1223723.56753.38NR2papbri6632.786632.78 6753.386512.18N2、轴承寿命计算:选用两只22208ECr = 89700 N.“anx Zcncx (nA Znx) Za nCXZ动载系数Fk

27、 =旋转系数F n =nex = r/min(204.1136.857) 132298.83r/ minPAFK Fn6632.78 1.5 1.110944.09N187213L106(C)106( 89700 篙h 60ncx ( P)60 98.83 ( 10944.09)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太阳轮对行星轮的切向力3617.07 N mc200CTa2000 3617.07PtACACs dA 3 67.678内齿圈对行星轮的切向力35630.19NPBCRaC(2)求支座反力:由两轴承支承在轴

28、上二 Ra RbA、B两点PRacRbc2 235630.19NRi36278NPA(b c) Pb c 35630.19(3723.5)35630.19 23.522 3723.5R2PAPBR1 35630.1935630.193627834982.38N2、轴承寿命计算:选用两只22208E. nACr = 89700 N nXZCcx = r/min动载系数Fk =LhnncxPaCX (nA ZrAx)Za旋转系数FkFnFn10660ncx岸）、渐开线花键强度验算：2T挤压强度P1、对一级太阳轮轴(血8576.655)1317.847r/min35630.19221.5 1.158

29、789.8N10689700 戸 3819h60 17.84758789.8d; pT= ml = 20mm35 h = m = 4mm=4X 35 =140mmp =100140Mpa2 585.51 1000T= m3.98MPa0.75 35 4 20 1402、对二级太阳轮轴13 h = m = 5mml = 30mm D m = m - z = 5X 13 =65mmp =100140Mpa66.17MPa2 3145.28 10000.75 13 5 30 65 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)

30、Z 10齿轮对轴的作用力Pt102000T52000 16896141543.1N1d 1039.79 6Pr10Ptg 141543.1tg2051517.48N(2)渐开线花键因制造安装误差所产生的径向力2000T5P05mz2、求支座反力：0.22000 168965 210.264365.7N(1)水平面的反力:Pr10Cb c51517.48 87115 8722188.22NRBXPr10 Rax51517.48 22188.22 29329.26N(2)垂直面的反力：Ray 甌上 1415438760961.63Nb c 11587RbyP10141543.160961.6380

31、581.47N(3) P。产生的支座反力:RaoPo(a b c) 64365.7 (55 115 87)81891Nb c115 87RboRao Po 81891 64365.7 17525.3N合成反力：RA- RaxrAyRao,22188.22260961.63281891146765NRb- J RbxrByRbo29329.26280581.47217525.3103278.3N、轴承寿命计算:Cr = 315000 N n = r/minA点选用：42224EP RA fp 146765 1.5220147.5NLh10 (5)60n P10660 6.655315000 )2

32、20147.51038267hB点选用：3053124Cr = 262000 N n = r/min14424hP Rb fP 103278.3 1.5154917.45N、渐开线花键强度验算：挤压强度 P 2T-z h l W =T= 16896N- m只p21z =21h = m =5mml = 55mmD m = m - z = 5X 21 =105mmp =100140Mpa2 16896 10000.75 21 5 55 10574.3MPa 3-3截割部 3-3 1 I轴的轴承寿命计算T1 = m一、轴的受力分析：1、传动件作用在轴上的力：输入扭矩(1) Z 1齿轮对轴的作用力Pt

33、12000T1d；2000 857.41123.4913887.12NPr1P/g13887.12tg 24 03 296199.81N(2)渐开线花键因制造安装误差所产生的径向力PO 2000T1 0.2 2 857.46 0.2 7145.5Nmz3 162、求支座反力：(1)水平面的反力：P r1c6199.81 53.5Rax3029.13Nbc5653.5RBXP r1Rax6199.81 3029.133170.68N垂直面的反力:rPt1c13887.12 53.5Ray6785.03Nbc5653.5RBYP11Ray13887.126785.037102.09N(3) P。产

34、生的支座反力：RaoP(b C a) 7145.5 (56 535 2)be5653.5RBOPO Rao 7145.5 7014.99 130.51N14445.49N合成反力：Ra . RAxRAyRao.3029.132 6785.032 7014.99RB,R；x R；y Rbo3170.682 7102.092 130.51二、轴承寿命计算：A 点选用：NJ2217EC Cr = 187000 N n = 1470 r/mi nP RA fp 14445.49 1.521668.24N7908.23N加）6 1010/ 187000 、亍( )360 147021668.241494

35、8hB 点选用：53515 Cr = 145000 N n = 1470 r/minP Rb fP 7908.23 1.511862.35NLh6 1010/ 145000( )360 147011862.3547700h三、渐开线花键强度验算：挤压强度 P 2T pz h l DmT= mW = z =16 h = m =3mml = 70mm D m = m - z = 3X 16 =48mmp =100140Mpa14.18MPap 2 857.46 10000.75 16 3 70 48 3-3 2 H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 = m20

36、00T2d22000 1260.74185.2413609.05NPr2R2tg 13609.05tg24 03 296075.67N不考虑效率损失：Pt2 Pt2Pr2Pt2tg13609.05tg21 11 475277.62N水平方向：PxP r2P r26075.675277.62798.05N垂直方向：PyR2 R213609.0513609.0527218.1N2、求支座反力由两只轴承支承在轴上A、B两点PX798.05“二 PaxPbxX399.025N2 2Py27218.1PAYPBYy13609.05 N2 2(1) 水平面的反力：434.71Nc Pax (b c) Pb

37、x c 399.025 (3450)399.025 50& Xa b c39 3450P2XPAXPbx R1X 798.05 434.71 363.34N(2) 垂直面的反力：14826.12NcPay (b c) Pby c 13609.05 (34 50) 13609.05 50Riya b c393450F2y Pay Pby R1y 27218.114826.1212391.98N(3) 合成反力：RR1XR1Y.434.71214826.12214832.49NR2R2XR2Y363.34212391.98212397.31N二、轴承寿命计算：A、B两点均选用53514Cr = 1

38、40000 Nn = 980 r/minPaPbPAx FAY. 399.0252 13609.052 13614.89NP Ra fP 13614.89 1.520422.34N6on 岸)6 1010/ 140000 、空( )360 98020422.3410408h 3-3 3皿轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩 T3 = m(1) Z 3齿轮对轴的作用力R32000T32000 1811.7113617.78Nd3266.08Pr3Pt3tg13617.78tg21 11475281N(2)Z4齿轮对轴的作用力2000T32000 1811.71R4

39、24451.18Nd4148.19Rr4R4tg 24451.18tg24 03 2910916.07N2、求支座反力(1)水平面的反力：厂 Pr3 (b c) Pr4 c 5281(83.5 69)10916.07 69Raxa b c58 83.5 69247.71NPbxPaxPr4 Rr3 247.71 10916.07 52815882.78N(2)垂直面的反力:只人丫R3 (bc)Pmc 13617.78 (83.569)24451.1869 仃880 49NAYabc58 83.5 69PBY Pt3 Pt4 Ray 13617.78 24451.18 17880.49 2018

40、8.47N合成反力：RarAx RAY247.712 17880.492 17882.21NRb. RBx RBy5882782 20188.47221028.11N二、轴承寿命计算:A点选用：53520Cr = 275000 N n = r/minPRa fP17882.21 1.526823.32NLh的）6 1010/ 275000 、可( )360 668.18226823.3258392hB 点选用：42318E Cr = 295000 N n = r/minP Rb fp 21028.11 1.531542.17NLh的）6 1010/ 295000、( )360 668.1823

41、1542.1742992h三、键的强度验算：1、键的挤压强度PT= N m D =120mm2TD k lpk = h / 2 = 18/2 = 9mml = 54mmp =100 120 MPa2 1811.71 1000120 9 5462.13MPa2、键的剪切强度T= N mD b lD =120mm b = 32mml = 54mmt = 90 MPa17.47MPa2 1811.71 1000120 32 54 3-3 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 = mPt52000T4d52000 3156.4263.4523962.04NPr

42、5P5tg 23962.04tg24 03 2910697.69N不考虑效率损失：Pt5 P5Pr5Pt5tg 23962.04tg22 34 169960.26N(1) P5、Pr5在X、丫方向的力Pr5xPr5 cos9960.26cos40.737547.81NIXPt5XP5si n23962.04 si n40.7315635.12NPr5YPr5Sin9960.26sin 40.736499.02NIYPt5Y Pt5 cos 23962.04cos40.7318158.26NR1Xpax(b C)Pbx ca b c6242.62 (46126.5)6242.62 126.560

43、46 126.58028.14NP5X1Pr5XPt5X7547.8115635.1223182.93NP5YPt5Y1Pr 5Y18158.266499.0211659.24 N在X、丫方向的合力PxP5XP r523182.9310697.6912485.24 NP丫R5 P5Y 23962.04 11659.24 35621.28 N2、求支座反力由两只轴承支承在轴上A、B两点- PaxPBXPx12485.246242.62N22PayPbyPl35621.2817810.64N22(1)水平面的反力:R2XPaxPbxRx 12485.24 8028.14 4457.1 N(2)垂直

44、面的反力:(46126.5) 17810.64 126.56046 126.522904.87NcPay (b c) Pby c 17810.64R1Ya b c(3) 合成反力：R1RxR：. 8028.142 22904.872 24271.05NR2R；x R；y4457.12 12716.412 13474.90N二、轴承寿命计算：A B 两点均选用 53519 Cr = 248000 N n =minPa PbPAxPAY6242.622 17810.642 18872.98NP Ra fp 18872.98 1.528309.47NLhR ()60n P10660 375.8522

45、4800028309.471061456h 3-3 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 Ts = m(1) Z 6齿轮对轴的作用力Pt62000T5d62000 3093.27260.5223746.89NPr6Pt6tg 23764.89tg22 34 169870.83N(2)渐开线花键因制造安装误差所产生的径向力2000T5P。5mz2、求支座反力：0.22000 3093.274 210.214729.86N(1)水平面的反力:Pr6 cb c9870.83 5967594622.06NRbxPr6 Rax 9870.83 4622.06 5248

46、.77N(2)垂直面的反力：rby23746911H9.58N12627.31Nbe 675923746.89 11119.58(3) P。产生的支座反力:RaoP(a b e)14729.86 (24 6759)17535 55Nb e6759RBO Rao Po17535.55 14729.86 2805.69N合成反力：Ra.rAxrAyRao4622.06211119.58217535.5529577.50NRb.rBxrByRbo5248.77212627.3122805.6916480.43N二、轴承寿命计算：A点选用：42228Cr =288000 Nn :=r/mi nPRaf

47、P29577.501.544366.25N106Cr106 /10288000 Lh(r)(22627h60nP60375.85244366.25B点选用：42226Cr =245000 Nn :=r/mi nP Rb fp 16480.43 1.524720.65N10245000&)360 375.85224720.65106106Cr“(十)60n P、渐开线花键强度验算:Lh92722.66h挤压强度P2Tz h l Dm pT= mW =z =21 h = m = 4mml = 52mm D m = m - z = 4X21 = 84mmp =100140Mpa22.48MPa2 3

48、093.27 10000.75 21 4 52 84 3-3 6行星轮心轴的轴承寿命计算、轴的受力分析:1、传动件作用在轴上的力：输入扭矩 Ta Ta Kfp 3093.27 1.153557.26N m太阳轮对行星轮的切向力20161.3NP 200CTa 2000 3557.26 tACCs dA 4 88.22内齿圈对行星轮的切向力PBC RaC2、求支座反力：由五只轴承支承在轴上RiP b a b40322.6 5555.5 5520070.07 NPPtACPtBC20161.3240322.6NPaPbPRacRbc40322.68064.52N555R2P R1 40322.6

49、20070.07 20252.53N选用五只292206ECr=36200 Nn nAnxZcncxZa、轴承寿命计算:ex = 248 r/minncx动载系数Fk =(“a nx) ZaZC旋转系数Fn =(37585284.07) 17 248r/min20Pa FkFn 8064.521.51.113306.46N(壬巴)1889h13306.461匚248106(CL)P 60 3-3 7 W轴的轴承寿命计算一、轴的受机力分析：1、已知：W重PL 机长(6470mm)卩磨擦系数n滚筒转速min)滚筒轴实际牵引阻力Lh60ncx牵引力(22T)Fa轴向力(2T)滚筒直径(850mm)扭矩 m)(1)P式中：PoxoX=P牵-(F 1 + 2F2 + F 3 )F1：机器与溜子摩擦力F1W 0.3 13500 4050kgfF2：牵引链偏心力矩