第三章軸承壽命計(jì)算

1、第三章軸、軸承和鍵的計(jì)算§3-1液壓部§3-1I軸的軸承壽命計(jì)算Ti=295.74Nm一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩(1) Z1齒輪對(duì)軸的作用力Pt12000d；2000295.74127.424641.97NPr1Pt1tg'4641.97tg2248101951.57N(2) 漸開(kāi)線花鍵因制造安裝誤差所產(chǎn)生的徑向力P。2000T1mz0.22000295.743150.22628.8N2、求支座反力:(1) 水平面的反力:RaxPr1Cbc1951.573633361018.21NRbxPr1Rax1951.571018.21933.36N

2、垂直面的反力：Pt1cbc4641.973633362421.90NRbyPt1Ray4641.972421.902220.07N(3) Po產(chǎn)生的支座反力：廠Po(bca)2628.8(33366.5)“Rao2381.16Nbc3336RboPoRao2628.82381.16247.64N(4)合成反力：RaRaxRayRao1018.2122421.9022381.165008.39NRB.RbxRbyRbo.933.3622220.072247.642655.93N二、軸承壽命計(jì)算：A點(diǎn)選用：42216ECr=130000Nn=1453r/minPRafP5008.391.57512

3、.59NLh106(60n610Cr、10/130000、虧一)()3P6014537512.59153731hB點(diǎn)選用：42217ECr=:155000Nn=1453r/minLh6on岸)61010/155000、行()36014533983.902289079hPRBfp2655.931.53983.90N三、漸開(kāi)線花鍵強(qiáng)度驗(yàn)算:擠壓強(qiáng)度P2TzhlDmp式中：T轉(zhuǎn)矩，NmmW各齒載荷不均勻系數(shù)，一般取屮=0.70.8z齒數(shù)h齒的工作高度，mml齒的工作（配合）長(zhǎng)度，mmDm平均直徑，mmp許用比壓，MpaT=295.74NmW=0.75z=15h=m=3mml=55mmDm=mz=3X

4、15=45mmp=100140Mpa2295.7410000.7515355457.08MPa§3-1H軸的軸承壽命計(jì)算一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩T2=382.56NmI2OOOT22000382.56“Pt2'24551.85Nd2168.09Pr2Pt2tg'4551.85tg2248101913.68N不考慮效率損失：P't2P2Pr'2Pt2tg'4551.85tg2243161906.05N(1)Pt2、Pr2在X、Y方向的力Pr2XPr2cos1913.68cos11.711873.85NXR2XPt2si

5、n4551.85sin11.71923.84NPr2YPr2sin1913.68sin11.71388.40NYR2YPt2cos4551.85cos11.714457.11NP2XPr2XPt2X1873.85923.842797.69NP2YR2YPr2Y4457.11388.404068.71NP，2、Pr2在X、丫方向的力Pr2XPr2cos1906.05cos27.261694.36NIXPt2XPt2sin4551.85sin27.262084.88NPr'2丫Pr'2sin1906.05sin27.26873.03NIYPt2YR2cos4551.85cos27.

6、264046.31NP2XPr2XPt2X1694.362084.883779.24NP2YPt2YPr2Y4046.31873.033173.28N在X、丫方向的合力PxP2XP2X3779.242797.69981.55NPyP2YP2Y4068.713173.287241.99N2、求支座反力：P.PXP2981.5527241.9927308.21NRaRb7308.2123654.11N、軸承壽命計(jì)算:A、B兩點(diǎn)均選用：53511Cr=92200Nn=1100.76r/min3654.111.55481.17N184650h106601100.7610/92200、乜)35481.1

7、7§3-13皿軸的軸承壽命計(jì)算一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩T2=306.74Nm2000T3Pt3；3d32000306.744460.70N137.53Pr3Pt3tg4460.70tg2243161867.88N不考慮效率損失:Pt3Pt3Pr3Pt3tg4460.70tg2243161867.88N(1)Pt3、Pr3在X、Y方向的力Pr3XPr3COS1867.88cos27.261660.43NXR3XPt3sin4460.70sin27.262043.13NPr3YPr3sin1867.88sin27.26855.54NYPt3YPt3cos446

8、0.70cos27.263965.28NP3XPr3XR3X1660.432043.133703.56NP3YPt3YPr3Y3965.28855.543109.74NP3、Pr3在X、丫方向的力Pr3XPr3cos1867.88cos15.171802.79N1XPt3XPt3sin4460.70sin15.171167.29NPr3YPr'3sin1867.88sin15.17488.79N1YPt3Y1Pt3cos4460.70cos15.174305.26NP3XPr3XR3X1802.791167.292970.08NP3YPt3YPr3Y4305.26488.793816.

9、47N在X、丫方向的合力PxP3XP3X3703.562970.08733.48NPYP3YP3Y3109.743816.476926.21N(4) 漸開(kāi)線花鍵因制造安裝誤差所產(chǎn)生的徑向力P。mz2000306.742212921.33N2、求支座反力:(1)水平面的反力:RaxPxcbc733.4835.552.535.5295.89NRbxPxRax733.48295.89437.59N(2) 垂直面的反力:PYcbc6926.2135.552.535.52794.10NRbyPyRay6926.212794.104132.11NPo產(chǎn)生的支座反力:P°(abc)Rao,bc30

10、87.31N2921.33(552.535.5)52.535.5RboRaoPo3087.312921.33165.98N(4)合成反力:RaJrAxRAyRao<295.8922794.1023087.315897.03NRb.RBxRbo437.5924132.112165.984321.20N、軸承壽命計(jì)算:A點(diǎn)選用:42514ECr=145000N=1345.37r/minRafP5897.031.58845.55NLh610（CL）106（145000）60n（P）601345.37（8845.55Cr106103138617hB點(diǎn)選用:53511Cr=92200Nn=1345

11、.37r/minRbP4321.201.56481.8NLh程（工）60nP601345.37Cr10610/92200-3-）36481.886389h三、漸開(kāi)線花鍵強(qiáng)度驗(yàn)算:擠壓強(qiáng)度P2ThlDmpT=306.74NmW=0.75z=21h=m=2mml=27mm=mz=2X21=42mmp=100140Mpa2306.7410000.75212274217.17MPa§3-14W軸的軸承壽命計(jì)算、軸的受力分析:1、傳動(dòng)件作用在軸上的力：輸入扭矩T4=367.41NPt42000T4d42000367.41168.094371.59NPr4Pt/g4371.59tg2243161

12、830.57N不考慮效率損失:Pt4Pt4Pr4Pt4tg4371.59tg2247511837.42NPt4、Pr4在X、丫方向的力Pr4XPr4COS1830.57cos15.171766.78NXR4XPt4sin4371.59sin15.171143.97NPr4YPr4sin1830.57sin15.17479.03NYPt4YR4cos4371.59cos15.174219.26NP4XPr4XPt4X1766.781143.972910.75NP4YR4YPr4Y4219.26479.033740.23NP，4、Pr4在X、丫方向的力1Pr4X1Pr4cos1837.42cos4

13、.721831.89Nx'Pt4XPt4sin4371.59sin4.72359.721Pr4Y1Pr4sin1837.42sin4.72151.19N1YPt4YR4cos4371.59cos4.724356.76NP4X1Pr4XPt4X1831.89359.722191.61NP4YR4YPr'4Y4356.76151.194205.57NZ7作用在軸上的力：輸入扭矩T7=272.77Nm2000T72000272.77R714281.43Nd7127.42Pr7Pt7tg'4281.43tg2248101799.99NPt7、Pr7在X、Y方向的力Pr7XPr7

14、cos1799.99cos54.281050.89NXP:7XPt7sin4281.43sin54.283476.01NPr7YPr7sin1799.99sin54.281461.38NYPt7YPt7cos4281.43cos54.282499.6NP7XPt7XPr7X3476.011050.892425.12NP7YP7YPr7Y2499.61461.383960.98N在X、Y方向的合力PxP7XP4xP4X2425.122191.612910.751705.98NFYP7YP4YP4Y3960.984205.573740.2311906.78N2、求支座反力：PPX2Q1705.98

15、211906.78212028.37NRaRb212028.376014.19N2二、軸承壽命計(jì)算：A、B兩點(diǎn)均選用：53511Cr=92200NPRafP6014.191.59021.29Nn=1100.76r/min106601100.7610/92200、虧)39021.2935078h§3-15V軸鍵聯(lián)接的強(qiáng)度驗(yàn)算1、鍵的擠壓強(qiáng)度2TDklp式中：T轉(zhuǎn)矩，Nmm2316.4210004045868.19MPa2、鍵的剪切強(qiáng)度2TDblD軸的直徑，mmk鍵與輪轂的接觸高度，mm，平鍵k=h/2l-鍵的工作長(zhǎng)度，對(duì)于A型鍵l=L-bp鍵聯(lián)接的許用比壓，MpaT=316.42NmD

16、=40mmk=h/2=8/2=4mml=70-12=58mmp=100120Mpa式中：T轉(zhuǎn)矩，Nmm軸的直徑，mmb鍵的寬度，mml鍵的工作長(zhǎng)度，對(duì)于A型鍵l=L-bT鍵聯(lián)接的許用剪應(yīng)力，Mpal=58mmT=316.42NmD=40mmb=12mmT=90MPa2316.42100040125822.73MPa§3-16叫軸的軸承壽命計(jì)算T7=6.87Nm一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩Pt72000T7d720006.87127.42107.83NPr7Pt7tg'107.83tg22481045.33N2、求支座反力：(1)水平面的反力:Pr7ba

17、b45.3355345528.01NRbxPr7Rax45.3328.0117.32N(2)垂直面的反力:R7bab107.8355345566.64NRbyPt7Ray107.8366.6441.19N合成反力：Ra.RAxRAy28.01266.64272.29NRb一RBxRBy17.32241.19244.68N、軸承壽命計(jì)算:A點(diǎn)選用：110Cr=16800Nn=1453r/minPRAfp72.291.5108.44NLh610（16800）3601453（108.44）42652300hB點(diǎn)選用：110Cr=16800Nn=1453r/minPRbfP44.681.567.02N

18、Lh-10-（善）60nP10（竺00）3180674853h60145367.02§3-2牽引部§3-2I軸的軸承壽命計(jì)算一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩(1)Z1齒輪對(duì)軸的作用力T1=220.15NmPt12000T1d；2000220.1578.695595.37NPr1P>1tg'5595.37tg2120462186.73N(2)漸開(kāi)線花鍵因制造安裝誤差所產(chǎn)生的徑向力型匹0.2mz2000220.152180.22446.11NPO2=PO12、求支座反力：(1)水平面的反力:Pr1Cbc2186.735123851385.89N

19、RbxPr1Rax2186.73385.891800.84N（2）垂直面的反力：RayPtic5595.3751987.42N23851RbyPt1Ray5595.37987.424607.95NPoi產(chǎn)生的支座反力:RAO1Poi(abc)沁1(923851)2522.29N23851Rbo1Rao1Po12522.292446.1176.18NRBO2Po2(bcd)2446."(23851“5)2543.45N23851PO2產(chǎn)生的支座反力:RaRbRbxRbyRBO1RBO21800.8424607.95276.182543.457566.98Rao2RBO2PO22543.

20、452446.1197.34N(5) 合成反力：Rao2385.892987.4222522.2997.343679.78N、軸承壽命計(jì)算:A點(diǎn)選用:42212ECr=88800N=565.24r/minLhB點(diǎn)選用:LhRafP3679.781.55519.67NCr(二)60nP53512Rb10660565.24(88800'5519.67Cr=110000NP7566.981.511350.47N10660565.2410)309943h=565.24r/min(8880011350.4710)228029h三、漸開(kāi)線花鍵強(qiáng)度驗(yàn)算:擠壓強(qiáng)度P2TzhlDmpT=220.15Nm

21、W=0.75z=18h=m=2mml=45mmDm=mz=2X18=36mmp=100140Mpa10.07MPa2220.1510000.751824536§3-22H軸的軸承壽命計(jì)算一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩T2=506.18NmPt22000T2d22000506.18184.635483.18NPay&10966.36NPr2Pt2tg'5483.18tg2120462142.89N不考慮效率損失：P't2R2Pr2Pt2tg5483.18tg2014012021.07N水平方向：PxPr2Pr22142.892021.071

22、21.82N垂直方向：PyP2p25483.185483.1810966.36N由一只軸承在軸上A點(diǎn).121.82210966.36210967.04N、軸承壽命計(jì)算:A點(diǎn)選用：53609Cr=128000Nn=240.92r/minPRafP10967.041.516450.56N10106Cr1061280002Lh(-1)()364576.35h60nP60240.9216450.56§3-23皿軸的軸承壽命計(jì)算-、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩T3=585.51NmZ3齒輪對(duì)軸的作用力Pt3啤2°°0宓5413.37Nd3216.32Pr

23、3R3tg'5413.37tg2014011995.34N(2)漸開(kāi)線花鍵因制造安裝誤差所產(chǎn)生的徑向力Po2000I10.2mz2000585.510.24351672.89N2、求支座反力：(1)水平面的反力:RbxPr3Cbc1995.341411141117.39NPr3Rax1995.341117.39877.95N(2)垂直面的反力:3031.49NR3c5413.3714bc1114RbyPt3Ray5413.373031.492381.88N(3)Po產(chǎn)生的支座反力:RaoPo(abc)1672.89(341114)3948.02N1114RboRaoPo3948.021

24、672.892275.13N(4)合成反力：RaJrAxrAyRaoV1117.392_3031.4923948.027178.89Nn=204.11r/min11059hRbo.877.9522381.8822275.134813.66N二、軸承壽命計(jì)算：A點(diǎn)選用：61924Cr=55300NPRafP7178.891.510768.34N610（55300）360204.11（10768.34B點(diǎn)選用：61924Cr=55300Nn=204.11r/minPRbfp4813.661.57220.49N6Lh36683h10（55300）360204.11（7220.49）§3-2

25、雙行星機(jī)構(gòu)一、軸承壽命計(jì)算：一級(jí)行星輪心軸1、軸的受力分析：(1)傳動(dòng)件作用在軸上的力：輸入扭矩TaTaKfp585.511.15673.34Nm太陽(yáng)輪對(duì)行星輪的切向力2000TaCsdA2000673.34367.6786632.78N內(nèi)齒圈對(duì)行星輪的切向力PBCPC(2)求支座反力：由兩軸承支承在軸上A、B兩點(diǎn)R1PaPbPtACPtBC6632.78NPA（bc）Pbc6632.78（3723.5）6632.7823.5223723.56753.38NR2PaPBR16632.786632.786753.386512.18N2、軸承壽命計(jì)算:選用兩只22208ECr=89700Nncx=

26、98.83r/min2nAnxZcncxZA(nAnX)ZA(204.1136.857)132298.83r/min動(dòng)載系數(shù)Fk=1.5旋轉(zhuǎn)系數(shù)Fn=1.1PPaFkFn6632.781.51.110944.09N610187213106/89700、三Lh()36098.8310944.09二級(jí)行星輪心軸1、軸的受力分析：(1)傳動(dòng)件作用在軸上的力：輸入扭矩TaTaKfp3145.281.153617.07Nm太陽(yáng)輪對(duì)行星輪的切向力Rac2000TaCsdA20003617.07367.67835630.19N內(nèi)齒圈對(duì)行星輪的切向力PBCPC(2)求支座反力：由兩軸承支承在軸上A、B兩點(diǎn)Pa

27、PBPPc強(qiáng)35630.19Nl=30mmDm=mz=5X13=65mmRiPA(bc)Pbc35630.19(3723.5)35630.1923.536278Nabc223723.5R2PaPbR,35630.1935630.193627834982.38N2、軸承壽命計(jì)算:選用兩只22208ECr=89700Nncx=17.847r/min“anxZcnCXZA10660nCXCr61010/89700()36017.84758789.83819h-ncx(nAnx)Za(36.8576.655)13Zc11!1/11III122動(dòng)載系數(shù)Fk=1.5旋轉(zhuǎn)系數(shù)Fn=1.1PPaFkFn356

28、30.191.51.158789.8N三、漸開(kāi)線花鍵強(qiáng)度驗(yàn)算:擠壓強(qiáng)度P1、對(duì)一級(jí)太陽(yáng)輪軸2TzhlDmpT=585.51NmW=0.75z=35h=m=4mml=20mmDm=mz=4X35=140mmp=100140Mpa3.98MPaP2585.5110000.75354201402、對(duì)二級(jí)太陽(yáng)輪軸T=3145.28NmW=0.75z=13h=m=5mmp=100140Mpa66.17MPa23145.2810000.751353065§3-25V軸的軸承壽命計(jì)算一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩T5=16896Nm(1)Z10齒輪對(duì)軸的作用力Pt102000

29、T5200016896141543.1N1d1039.796Pr101Retg141543.1tg2051517.48N(2)漸開(kāi)線花鍵因制造安裝誤差所產(chǎn)生的徑向力P。mz2000168965210.264365.7N2、求支座反力:(1)水平面的反力:Pr10Cbc51517.48871158722188.22N51517.4822188.2229329.26N(2)垂直面的反力:Pt10cbc141543.1871158760961.63NRbyPt10Ray141543.160961.6380581.47NPo產(chǎn)生的支座反力:RaoPo(abc)64365.7(5511587)81891

30、N11587RBORaoPo8189164365.717525.3N合成反力：RaRaxRayRao.22188.22260961.63281891146765NfBifRBXRBYRbo29329.26280581.47217525.3103278.3N、軸承壽命計(jì)算:A點(diǎn)選用:42224ECr=315000Nn=6.655r/minRaP1467651.5220147.5NLh獸岸）60nP(315000606.655'220147.51061038267hB點(diǎn)選用:3053124Cr=262000Nn=6.655r/minRbP103278.31.5154917.45NLh蠱岸）

31、106606.65510154947.45(26200014424h三、漸開(kāi)線花鍵強(qiáng)度驗(yàn)算:擠壓強(qiáng)度P2TzhlDmpT=16896NmW=0.75z=21h=m=5mml=55mmDm=mz=5X21=105mmp=100140Mpa21689610000.752155510574.3MPa§3-3截割部§3-3I軸的軸承壽命計(jì)算一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩Ti=857.46Nm(1)Zi齒輪對(duì)軸的作用力FO2000Timz0.22000857.460.23167145.5Nc2000T1Pt1'd12000857.4113887.12N1

32、23.49Pr1P1tg13887.12tg2403296199.81N(2)漸開(kāi)線花鍵因制造安裝誤差所產(chǎn)生的徑向力2、求支座反力:(1)水平面的反力:Fr1cbc6199.8153.55653.53029.13NRbxPr1Rax6199.813029.133170.68N(2)垂直面的反力:Pt1cbc13887.1253.55653.56785.03NRbyPt1Ray13887.126785.037102.09N(3) Po產(chǎn)生的支座反力:RaoPo(bca)7145.5(5653.52)701499Nbc5653.5RboPORao7145.57014.99130.51N(4) 合成

33、反力:Ra:Rax3029.1326785.0327014.9914445.49NRbo3170.6827102.092130.517908.23N、軸承壽命計(jì)算:A點(diǎn)選用:NJ2217ECCr=187000Nn=1470r/minRap14445.491.521668.24NLh但(二)60nP601470Cr10610/187000、虧)321668.2414948hB點(diǎn)選用:53515Cr=145000Nn=1470r/minRbP7908.231.511862.35NLh1066014701011862.35、漸開(kāi)線花鍵強(qiáng)度驗(yàn)算:擠壓強(qiáng)度P2ThlDmPT=8

34、57.46NmW=0.75z=16h=m=3mml=70mm=mz=3X16=48mmp=100140Mpa2857.4610000.75163704814.18MPa§3-32H軸的軸承壽命計(jì)算、軸的受力分析:1、傳動(dòng)件作用在軸上的力：輸入扭矩T2=1260.74NmPt22000T220001260.74d2185.2413609.05NPr2Ft2tg13609.05tg2403296075.67N不考慮效率損失：P't2Pt2Pr'2Pt2tg'13609.05tg2111475277.62N水平方向:PxPr2Pr26075.675277.62798

35、.05N垂直方向：PYP2P213609.0513609.0527218.1N2、求支座反力由兩只軸承支承在軸上A、B兩點(diǎn)PaxPbx電798.05399.025N22PAYPBY13609.05N22(1)水平面的反力：R1XPax(bC)PBXc399.025(3450)399.02550434.71Nabc393450P2XPAXPBXR1X798.05434.71363.34N(2)垂直面的反力:RyPAY(bc)PBYc13609.05(3450)13609.055014826.12Nabc393450P2YPayPbyR1Y27218.114826.1212391.98N(3)合成

36、反力:R1.R1Xr1Y.434.71214826.12214832.49NR2,R2XR2Y、363.34212391.98212397.31N二、軸承壽命計(jì)算：A、B兩點(diǎn)均選用53514Cr=140000Nn=980r/minPAPBPAxpAy399.025213609.05213614.89NPRafP13614.891.520422.34NLh6on61010/140000七()36098020422.3410408h§3-33皿軸的軸承壽命計(jì)算一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩T3=1811.71Nm(1)Z3齒輪對(duì)軸的作用力R32000T3200018

37、11.7113617.78Nd3266.08Pr3Fhtg13617.78tg2111475281NZ4齒輪對(duì)軸的作用力Pt42000T3d420001811.71148.1924451.18NPr4R4tg'24451.18tg24032910916.07N2、求支座反力(1)水平面的反力:RaxPr3(baPbxPaxPr4c)Pmc5281(83.5be58Rr3247.7110916.0769)10916.0769247.71N83.56952815882.78N(2)垂直面的反力:R3(bc)feabc13617.78(83.569)24451.18695883.569178

38、80.49NPbyPt3Pt4Ray13617.7824451.1817880.4920188.47N合成反力：RaVrAxRAyv'247.71217880.49217882.21NRBRBxRBy5882.78220188.47221028.11N、軸承壽命計(jì)算:A點(diǎn)選用：53520Cr=275000Nn=668.182r/minPRAfp17882.211.526823.32N61010/275000、可58392h()360668.18226823.32B點(diǎn)選用：42318ECr=295000Nn=668.182r/minA為軒土女廠廠卩只.2Tr1、鍵的擠壓強(qiáng)度DklT=18

39、11.71NmD=120mmk=h/2=18/2=9mmPRbfP21028.111.531542.17N106CrS60n(P)10610295000飛)342992h60668.18231542.17、鍵的強(qiáng)度驗(yàn)算：54mmp=100120MPa-21811.71100062.13MPap1209542、鍵的剪切強(qiáng)度2TDblT=1811.71NmD=120mmb=32mmT=90MPal=54mm21811.711000120325417.47MPa§3-3W軸的軸承壽命計(jì)算-、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩T4=3156.4NmPt52000T4d52000

40、3156.4263.4523962.04NPr5R5tg'23962.04tg24032910697.69N不考慮效率損失：P't5Pt5Pr5Pt5tg'23962.04tg2234169960.26N(1)R5、Pr5在X、丫方向的力Pr5xPr5cos9960.26cos40.737547.81NIXPt5XR5sin23962.04sin40.7315635.12NPr5YPr5sin9960.26sin40.736499.02NIYPt5YPt5cos23962.04cos40.7318158.26NP5XPr'5XPt5X7547.8115635.1

41、223182.93NP5丫Pt5YPr'5Y18158.266499.0211659.24N在X、丫方向的合力PXP5XPr523182.9310697.6912485.24NPyR5F5y23962.0411659.2435621.28N2、求支座反力由兩只軸承支承在軸上A、B兩點(diǎn)-PaxPbxPx12485.2422Py35621.28PAYPBY22(1)水平面的反力:PAX(bc)PBXcl、Xabc6242.62N17810.64N6242.62(46126.5)6242.62126.56046126.58028.14NR2XPaxPbxRx12485.248028.1444

42、57.1N(2)垂直面的反力:cPay(bc)Pbyc17810.64(46126.5)17810.64126.5Riyabc6046126.5P2YPayPbyR1Y35621.2822904.8712716.41N22904.87N(3)合成反力：R1R：R：8028.14222904.87224271.05NR2.R；xR；y4457.1212716.41213474.90N二、軸承壽命計(jì)算：A、B兩點(diǎn)均選用53519Cr=248000Nn=375.852r/minPaPb.PAxPAY6242.62217810.64218872.98NPRafP18872.981.528309.47N

43、需岸)61010/248000、三()360375.85228309.4761456h§3-35V軸的軸承壽命計(jì)算一、軸的受力分析：1、傳動(dòng)件作用在軸上的力：輸入扭矩T5=3093.27Nm(1)Z6齒輪對(duì)軸的作用力Pt62000T5d620003093.27260.5223746.89NPr6Pt6tg'23764.89tg2234169870.83N(2)漸開(kāi)線花鍵因制造安裝誤差所產(chǎn)生的徑向力P?？找?.2mz20003093.274210.214729.86N2、求支座反力：(1)水平面的反力:RaxPr6c9870.83594622.06Nbe6759RbxPr6Ra

44、x9870.834622.065248.77N（2）垂直面的反力：Pt6Cbe23746.8959675911119.58NRbyPt6Ray23746.8911119.5812627.31NPo產(chǎn)生的支座反力：RaoPo（abc）14729.86（246759）17535.55Nbc6759RboRaoPo17535.5514729.862805.69N合成反力：Rav'rAxrAyRaoV4622.06211119.58217535.5529577.50NRBR；xRByRbo5248.77212627.3122805.6916480.43N二、軸承壽命計(jì)算：Lh10-（牛）60n

45、P_10（245000）60375.85224720.6592722.66ha點(diǎn)選用：42228Cr=288000Nn=375.852r/minPRafP29577.501.544366.25N106Cr106/28800010Lh（）(）322627h60nP60375.85244366.25B點(diǎn)選用：42226Cr=:245000Nn=375.852r/minPRbfp16480.431.524720.65N三、漸開(kāi)線花鍵強(qiáng)度驗(yàn)算:擠壓強(qiáng)度P2TzhlDmpT=3093.27NmW=0.75z=21h=m=4mml=52mmDm=mz=4X21=84mmp=100140Mpa22.48MPa23093.27100