東北大學(xué)機械設(shè)計課程設(shè)計zl10

1、目錄1 設(shè)計任務(wù)書1.1.1題目名稱設(shè)計膠帶輸送機的傳動裝置11.2工作條件1.1.3技術(shù)數(shù)據(jù)2.2電動機的選擇計算2.2.1選擇電動機系列2.2.2滾筒轉(zhuǎn)動所需要的有效功率2.2.3確定電動機的轉(zhuǎn)速2.3傳動裝置的運動及動力參數(shù)計算23.1分配傳動比2.總傳動比3各級傳動比的分配33.2各軸功率、轉(zhuǎn)速和轉(zhuǎn)矩的計算3I軸高速軸3軸中間軸3川軸低速軸3W軸傳動軸4V軸卷筒軸43.3開式齒輪的設(shè)計4.材料選擇4按齒根彎曲疲勞強度確定模數(shù)4齒輪強度校核5齒輪主要幾何參數(shù)74閉式齒輪設(shè)計.7.4.1減速器高速級齒輪的設(shè)計計算7.材料選擇7按齒面接觸疲勞強度確定中心距84.1.3驗算齒面接觸疲勞強度9驗

2、算齒根彎曲疲勞強度-10-齒輪主要幾何參數(shù)-11-4.2減速器低速級齒輪的設(shè)計計算-12-材料選擇-12-按齒面接觸疲勞強度確定中心距-12-驗算齒面接觸疲勞強度-14-驗算齒根彎曲疲勞強度-15-齒輪主要幾何參數(shù)-16-5軸的設(shè)計計算-16-5.1高速軸的設(shè)計計算-16-5.2中間軸的設(shè)計計算-17-5.3低速軸的設(shè)計計算-17-6低速軸的強度校核-19-6.1繪制低速軸的力學(xué)模型-19-6.2求支反力-19-6.3作彎矩、轉(zhuǎn)矩圖-20-作計算彎矩Mca圖-21-校核該軸的強度-21-6.6精確校核軸的疲勞強度-21-7低速軸軸承的選擇及其壽命驗算-23-確定軸承的承載能力-24-計算軸承的

3、徑向支反力-24-7.3作彎矩圖-24-7.4計算派生軸向力S-24-求軸承軸向載荷-24-7.6計算軸承的當量動載荷P-24-8鍵聯(lián)接的選擇和驗算-25-8.1低速軸上鍵的選擇與驗算-25-齒輪處-25-聯(lián)軸器處-25-8.2中間軸上鍵的選擇與驗算-25-8.3高速軸上鍵的選擇與驗算-26-9聯(lián)軸器的選擇-26-9.1低速軸軸端處-26-9.2高速軸軸端處-26-10減速器的潤滑及密封形式選擇-26-11參考文獻-29-1設(shè)計任務(wù)書1.1題目名稱設(shè)計膠帶輸送機的傳動裝置1.2工作條件工作年限工作班制工作環(huán)境載荷性質(zhì)生產(chǎn)批量102多灰塵稍微波動小批1.3技術(shù)數(shù)據(jù)題號滾筒圓周力F(N)帶速v(m

4、/s)滾筒宜徑D(mm)滾筒長度L(mm)ZL-101600044008502電動機的選擇計算2.1選擇電動機系列根據(jù)工作要求及工作條件應(yīng)選用三相異步電動機，封閉式結(jié)構(gòu)，電壓380伏,Y系列。2.2滾筒轉(zhuǎn)動所需要的有效功率PW1000160000.243.84kW1000傳動裝置總效率352齒承聯(lián)筒查表17-9得所以=0.9730.9970.96=0.8172.3確定電動機的轉(zhuǎn)速60v探筒軸轉(zhuǎn)速nW11.5r/minD所需電動機的功率PrPw44.70kW5.5kW0.817查表27-1，可選Y系列三相異步電動機電動機型號額定功率/kW同步轉(zhuǎn)速/(r/min)滿載轉(zhuǎn)速/(r/min)總傳動比Y

5、132S-45.515001440Y132M2-65.51000960為使傳動裝置結(jié)構(gòu)緊湊，選用Y132MJ6型，額定功率5.5kW,同步轉(zhuǎn)速1000r/min,滿載轉(zhuǎn)速960r/min。查表27-2,電動機中心高H=132mm外伸段DxE=38mm(80mm3傳動裝置的運動及動力參數(shù)計算3.1分配傳動比3.1.1總傳動比i匹箜083.48w11.53.1.2各級傳動比的分配查表17-9取i開i566減速器的傳動比i-83.4813.913i64.253高速級齒輪傳動比i121.30f.1.3013.913低速級齒輪傳動比i34-13竺3.271i124.2533.2各軸功率、轉(zhuǎn)速和轉(zhuǎn)矩的計算

6、P=kw,n=960r/min,T=9.55*/960=N*m3.2.1I軸高速軸P1Pr4.700.994.653kWn1960r/minI013P4.65103T19.559.5546.26Nm19603.2.2II軸中間軸P2P14.650.990.974.47kW2T21960i124.253八P2八9.559.55225.7r/mih344710189.13Nm2225.73.2.3m軸低速軸P3P24.470.990.974.29kW32225.769.0r/miT3i343.2719.55屋9.55334.2910593.76N69.0m3.2.4IV軸傳動軸P4P34.20kW

7、n369.0n469.0r/mini451P434.20103T49.5549.55581.30Nm69.03.2.5V軸卷筒軸P5P44.03kWn496.6庵11.5r/mini566P5c4.03103T59.559.553346.65Nmn511.53.3開式齒輪的設(shè)計3.3.1材料選擇小齒輪:45#鍛鋼，調(diào)質(zhì)處理，齒面硬度217-255HBS大齒輪:45#鍛鋼，正火處理，齒面硬度162-217HBS3.3.2按齒根彎曲疲勞強度確定模數(shù)按齒面硬度217HB爵日162HB"算初取小齒輪齒數(shù)Z520則大齒輪齒數(shù)Z6Z5i56206120計算應(yīng)力循環(huán)次數(shù)N560n4jLh6069.

8、01.0(1030082)1.99108N6N5i561.9910873.3210查圖5-19YN5YN61.0查圖5-18(b)Flim5270Mpa,Flim6200Mpa由式5-32YX5Y<61.0取YST2.0,SFmin1.4計算許用彎曲應(yīng)力由式5-31FlimYSTyySFmin2702.0F51.41.01.0385.7Mpa2002.0285.7Mpa查圖5-14YFa52.81,YFa62.21查圖5-15YSa51.56,Ys61.78則YFa5YSa52.811.560.01131.01.01.4385.7F5F6YFa6YSa62.211.780.0137692

9、85.7max丫Fa5YSa5,YFa6YSa60.013769F5F】6初選綜合系數(shù)KtYt1.1，查表5-8d0.5由式5-262KT4YFaYsaYdZ；f。21.15813000.01376939.383mm0.5202d5mZ51220240mmd6mZ65120600mmda5d5*2ham10021.05da6d6_*_一_2ham60021.05df5d5*2(hc)m1002df6d6*2(hc)m6002d5d6100600a110mm610mm1.01.0考慮開式齒輪工作特點m加大10%-15%取m=123.3.3齒輪強度校核220.25587.5mm0.255587.5

10、mmmmb6aa0.235070mm取b5b6670676mmdb5d5cos20.93.969db6d6cos20.563.816則小齒輪轉(zhuǎn)速為vd5n4601033.1410066.254601030.3467m/sVZ51000.3467201000.06934查圖5-4dkv1.005查表5-3kA1.1bd5701000.70由圖5-7(a)k1.18查表5-4k1.2計算載荷系數(shù)kkAkVkk1.11.0051.181.21.5654db593.969a5arccosarccos31.3215da5110db6563.816a6arccosarccos22.4387da66101，

11、Z5(tana5tan)Z6(tana6tan)J21.71520(tan31.3215tan20)120(tam22.4387tan20)0.75Y0.250.250.750.68731.715kY1.56540.68731.076與ktYt1.1相近，無需修正計算齒根彎曲應(yīng)力701005F5等YFa5Ysa5Y545082762.811.56bd5m199.305Mpa5安全%5穹5F6F5YFa6Ysa6199.305Mpa2.811.562.211.78222.094Mpa6安全3.3.4齒輪主要幾何參數(shù)Z520Z6120u6m5a350mmd5100mmd6600mmda5110mm

12、da6610mm87.5mmdf6587.5mmdb593.969db6563.816b576mmb670mm4閉式齒輪設(shè)計4.1減速器高速級齒輪的設(shè)計計算4.1.1材料選擇小齒輪:45#鍛鋼，調(diào)質(zhì)處理，齒面硬度217-255HBS大齒輪:45#鍛鋼，正火處理，齒面硬度162-217HBS按齒面硬度217HB爵日162HB"算計算應(yīng)力循環(huán)次數(shù)N_9Ni60njLh609601(1030082)2.764810Ni8N26.510i12查圖5-17Zni1.0,Zn21.05允許一定點蝕由式5-29ZxiZx21.0取SHlim1.0,ZwIQZlvr0.92精加工查圖5-16bHli

13、m1650Mpa,時噸515Mpa由式5-28ShFZniZxiZwZlvrmin6501.01.01.01.00.92598MpaHlim2ShminZN2ZX2ZwZlvr515101.051.01.00.9249749MpaHminH1,H2497.49Mpa小輪轉(zhuǎn)矩146260Nmm初定螺旋角13初取KtZ21.0,查表5-5Ze189.,Mpa4.1.2按齒面接觸疲勞強度確定中心距減速傳動0.4ui124.253取a端面壓力角tarctan(tann/cos)arctan(tan20/cos13)20.4829基圓螺旋角barctan(tancost)arctan(tan13cos2

14、0.4829)12.2035由式5-42coscos130.987由式5-41Zh2cosbcostsinto2coS12.20352.442cos20.4829°sin20.4829°由式5-39a(u1)32aU2ZhZeZz2 21.0462602.4418980.987497.49(4.2531)311953mm0.44.253取中心距a120mm估算模數(shù)mn(0.0070.02)a0.842.4mm取標準模數(shù)m2mm小齒輪齒數(shù)2acos2120cos13oZ1mu124.2531大齒輪齒數(shù)z2u4.25322.394.84取z122z29522.3實際傳動比ifH

15、4.313傳動比誤差-L100%I4.2534.313100%1.5%5%i4.253在允許范圍內(nèi)修正螺旋角mn(z2z1)2(2295)oarccosarccos12.838572a2120與初選13相近，Zh,Z可不修正輪分度圓直徑d1mnj/cos222/cos12.83857o45.13mm_od2mvz2/cos295/cos12.8385719487mm圓周速度vd1n1360104527m/s查表5-6取齒輪精度為8級4.1.3驗算齒面接觸疲勞強度電機驅(qū)動，稍有波動，查表5-3kA1.1vz11002.27220.499100查圖5-4bkv1.03齒寬

16、baa0.412048.0mmbd148.045.131.06查圖5-7aK1.08查表5-4K1.4載荷系數(shù)KKAKvKK1.713齒頂圓直徑da1d2h；m45.532*1.0*249.53mm._*一_一_da2d22ham194.872*1*2198.87mm端面壓力角tarctan(tann/cos)arctan(tan20/cos12.8386)20.4707齒輪基圓直徑db1d1cost45.13cos20.4707°42.28mm0db2d2cost194.87cos20.470718256mm端面齒頂壓力角at1arcco也arccos4228da149.5331.

17、392odb2182.56cc»oat2arccosarccos23.37da2198.87tant)Z2(tan招tant)2-Z(tanat1122(tan31.392)tan2Q4707o)95(tan233/tan20.470/)1.92bsinmn48sin12.83857°21.698由式5-43ZJ0.72V、1.92由式5-42Zcos由式5-41barctan(tancost)5-41ZH.2cosbcostsint.cos12.83857o0.9874oooarctan(tar12.83857cos20.4707)12.05232cos12.0523o&

18、#176;2.443cos20.4707osin20.4707ohZhZeZZ,2KTu12.44318984.25314.25321.713462600.720.9874.必484513466457MpaH49749Mpa4.1.4驗算齒根彎曲疲勞強度查圖5-18bFlim1270Mpa,Flim2200Mpa查圖5-19YN11.0YN21.0由式5-32Yx1Yx21.0取YST2.0SFmin1-4由式5-31Flim1YsTww'N1'X1SFmin27021.41-01-0385-7MpaFlim2YsTSFminYN2Yk220021.41.01.0285.7Mp

19、a_,33.oZv1乙/cos22/cos12.8385730.498Zv2Z2/COS395/COS312.838570131.695查圖5-14YFa1查圖5-15YSa12.75,YFa22.251.575,YSa21.80由式5-47計算Y,因1.6981.0,取1.0012.8537Y1一0110.893120120由式5-48Y0.250.75COSb0.250.75cos12.052寸0.62361.92由式5-442K、,777F1,'Fa1Ysa1''bd1mn21.713462604845.1322.751.5750.62360.89388.23Mp

20、af1Fa2Sa2QQQQf2F188.23V VY F1YSa182.500MpaF24.1.5齒輪主要幾何參數(shù)2.251.802.751.575Z122Z295u4.253m12.83857omn/cos2.05d145.53mmd2194.87mmda149.53mmda2198.87mmdf145.53-2*2*(10.25)43.03mmdf2194.87-2*2*(10.25)189.87mma1(d1d2)120mm2b55mmb248mmdbi42.28mmdb2182.56mm4.2減速器低速級齒輪的設(shè)計計算4.2.1材料選擇小齒輪：40Cr，調(diào)質(zhì)處理，齒面硬度241-286

21、HBS大齒輪:45#鍛鋼，調(diào)質(zhì)處理，齒面硬度217-235HBS按齒面硬度241HB爵日217HB"算N360n2jLh60225.71(1030082)6.5108N38N41.98710i34查圖5-17Zn31,Zn41.05允許一定點蝕由式5-29Zx3Zx41.0取Shlim1.0，Zw1.0,Zlvr0.92精加工查圖5-16bHlim3650Mpa,hlim4650Mpa由式5-28成Zn3Zx3ZwZlvr65011.01.00.92598MpaSHminL0Hlim47777ZN4ZX4ZWZLVRminSh6501.01.051.01.00.92627.9Mpah

22、minh3,h4598Mpa4.2.2按齒面接觸疲勞強度確定中心距小輪轉(zhuǎn)矩T2189130Nmm初定螺旋角13初取Ktz21.0,查表5-5Ze189.Mpa減速傳動ui343.271取a0.4取標準模數(shù)小齒輪齒數(shù)m2.5mm2acos2155cos13°z3mnu12.53.2711大齒輪齒數(shù)Z4UZ33.27128.28892.532取Z328Z493實際傳動比Z4i一933.321估算模數(shù)28.28828Z3mn(0.0070.02)a1.0853.1mm端面壓力角tarctan(tann/cos)arctan(tan20/cos13)20.4829基圓螺旋角barctan(t

23、ancost)arctan(tan13cos20.4829)12.2035由式5-42cos130.987由式5-41Zh2cos12.20352cosbcostsintcos20.4829sin20.48292.442由式5-39取中心距at2KTZhZeZZ(u1)3。2aU(3.2711)31.01891302.44218980.987215349mm20.43.271598a155mm傳動比誤差100%i3.2713321100%1.5%5%3.271在允許范圍內(nèi)修正螺旋角mn(Z4arccosZ3)2.5(2893)oarccos12.62892155與初選13相近，Zh,Z可不修正

24、輪分度圓直徑d3m/cos2.528/cos12.6289o71.74mmod4nz/cos2.593/cos12.628923826mm圓周速度v項238.47m/s6010查表5-6取齒輪精度為8級4.2.3驗算齒面接觸疲勞強度VZ3100電機驅(qū)動，稍有波動，查表5-3kA18.47252.12100查圖5-4bkv1.15齒寬baa0.415562.0mmbd362.071.740.864查圖5-7aK1.07查表5-4K1.4載荷系數(shù)KKAKVKK11.151.071.41.7227齒頂圓直徑da3d32h；m71.7421.02.576.74mm._*_da4d42ham238.26

25、21.02.5243.26mm端面壓力角ooo齒輪基圓直徑tarctan(tann/cos)arctan(tan20/cos12.6289)20.455db3d3cost71.74cos20.455°67.22mmdb4d4cost238.26cos20.455)223.24mm端面齒頂壓力角db3at3arccosda367.22oarccos28.8476.74db4at4arccosda423.41o1Z3(tanat321oo28(tan2884tan2Q45$)93tant)z4(tanat4tant)(tan2341°tan20>45)1.679bsin6

26、2sin12.6289o1.7259mn2.5FTFl由式5-43Z0.772*1.679由式5-42Z.coscos12.6289o0.9878由式5-41ooobarctan(tancost)arctan(ta126289cos2Q455)11.856由式5-41ZH2cosbcostsint2cos11.856°'cos20.455osin20.455o2.445hZhZeZZ2KT2u12.44518980.7720.987821.72271891303.271162071.7423.27157787MpaH598Mpa4.2.4驗算齒根彎曲疲勞強度查圖5-18bFl

27、im3290Mpa,flim4270Mpa查圖5-19YN31.0Yn41.0由式5-32YX3Yx41.0取Yst2.0Sfmin1.4由式5-31F3Flim3YSTyY2902YN3YX31.01.0414.2MpaS14SFmin."Yut、，、，2702F4Yn4Yx41.01.03857MpaSFmin1.4rr，3ZV3Z3/cos3o28/cos312.628930.135rr，3Zv4Z4/cos3o93/cos312.6289100.090查圖5-14YFa32.62,YFa42.24查圖5-15YSa31.67,Ysa41.82由式5-47計算Y,1.72591

28、.0,取1.0Y1112012.268911200.895由式5-48Y0.2520.75cosb0.75coS11.856°0.250.6781.6792KT2F3.bcmn145.34Mpaf3414.2MpaYFa3Ysa3YY21.72271891302.621.560.6780.8956271.742.5YFa4YSa4F4F3YFa3YSa32.241.82145.34135.42Mpaf42.621.674.2.5齒輪主要幾何參數(shù)Z328Z493u3.271m2.5d371.74mmd4238.26mmda376.74mmda4243.26mmdf371.74-2*(1

29、0.25)69.24mmdf4238.26-2*(1.00.25)235.76mma1一(d3d4)155mm2b370mmb462mmdb367.22mmdb4223.24mm12.6289°m/cos2.565軸的設(shè)計計算5.1高速軸的設(shè)計計算軸的材料為選擇45#,調(diào)質(zhì)處理，傳遞功率P4.7kW轉(zhuǎn)速n960r/min查表8-2A0110PdAo33j_110314718.678mmn,960由丁軸上有一個鍵槽，Md18.678(3%5%1)19.23819.612估定減速器高速軸外伸段軸徑查表17-2電機軸徑d電機38mm,軸伸長E80mmWJd0.81.0d電機0.81.038

30、30.438mm取d32mm根據(jù)傳動裝置的工作條件選用HL型彈性柱銷聯(lián)軸名義轉(zhuǎn)矩TP4.7103Kl9.559.5546.755Nm查表11-1工作情況系數(shù)K1.251.5,取K1.5n960KT1.546.75570.133Nm查表22-1選TL6公稱轉(zhuǎn)矩Tn250NmTcc70.133Nm許用轉(zhuǎn)速n3300r/minn960r/min軸孔直徑dmin30mm,dmax38mm取減速器高速軸外伸段軸徑d=32mm可選聯(lián)軸器軸孔d1d電機38mm,d232mm聯(lián)接電機的軸伸長E80mm聯(lián)接減速器高速軸外伸段的軸伸長L82mm5.2中間軸的設(shè)計計算軸的材料為選擇45#,調(diào)質(zhì)處理，傳遞功率P4.4

31、7kW，轉(zhuǎn)速n225.7r/min查表8-2A1101P4.47dA3110V29.76mmn225.7由丁軸上有一個鍵槽，則d29.76(3%5%1)30.65432.187取dmin40mm5.3低速軸的設(shè)計計算69.0r/min查軸的材料為選擇40Cr,調(diào)質(zhì)處理，傳遞功率P4.29kW，轉(zhuǎn)速n表8-2A01184.2911869.046.02mm由丁軸上有一個鍵槽，則d46.02(3%-5%1)47.4048.332取dmin48mm因為是小批生產(chǎn)，故軸外伸段采用圓柱形根據(jù)傳動裝置的工作條件選用HL型彈性柱銷聯(lián)軸P429103名乂轉(zhuǎn)矩T9.559.55593.76Nmn69.0查表11-

32、1工作情況系數(shù).k計算轉(zhuǎn)矩TcKT3742.2Nm查表22-1選TL9公稱直徑L1000NmTc742.2Nm許用轉(zhuǎn)速n2100r/minn69.0r/min6低速軸的強度校核6.1繪制低速軸的力學(xué)模型L90.0mmL2130.0mm作用在齒輪的圓周力Ft飽箜37604984.135Nd4238.26徑向力FrFttan4981.135tan20.45461857.873N軸向力FaFttan4984.135tan12.621115.241N6.2求支反力水平支反力Mb0Rax(L1L2)FtL20RaxFtL2LiL24984.135130.0130.0902945.171NX0,RBxFt

33、RAx4984.1352945.172038.965N垂直支反力dMb0RAz(LiL2)FrL2Fa0FrL2RazFa_2L21857.873130.01115.4119.12220.0493.90NRbzFrRaz1857.873(493.90)1363.973N771995410I6.3作彎矩、轉(zhuǎn)矩圖上圖水平彎矩MC點McxRaxLi2945.171*90265065.39Nmm垂直彎矩MzC點左MCzRAzL1-493.909044451.0NmmC點右M'CzRBzL21363.87130.017730.31Nmm合成彎矩McC點左MCV;1MXM2z268766.72Nm

34、mC點右M'CCz265657.72Nmm轉(zhuǎn)矩T593760Nmm6.1.4作計算彎矩Mca圖上圖該軸單向工作，轉(zhuǎn)矩產(chǎn)生的彎曲應(yīng)力按脈動循環(huán)應(yīng)力考慮取0.6C點左McaC.MC(TC)2.(268766.72)2(0.6593760)2446266.61NmmC點右2222Mcac'M；(Tc)2<(265657.72)2(0.60)2265657.72NmmD點McaDMD(Td)2.02(0.6593760)2356256Nmm6.1.5校核該軸的強度根據(jù)以上分析，C點彎矩值最大，而D點軸徑最小，所以該軸危險斷面是C點和D點所在剖面。軸的材料為40Cr查表8-1b73

35、6Mpa查表8-3bi69MpaC點軸徑McaC0.13446266.610.16940.626mm因為有一個鍵槽dC40.626(10.05)42.657mm54mm安全D點軸徑dD30.1b1McaD33562560.16937.74mm因為有一個鍵槽dD37.74(10.05)39.627mm48mmg<全6.6精確校核軸的疲勞強度5850410.082d50maxWTmaxmV11.875Mpa查表8-11344Mpa1199Mpa查附表1-40.730.78查附表1-50.9160.916查表1-50.34,0.211991.6030.9160.7811.8750.2111.8

36、75取S1.51.8,SS安全校核VI、VD的疲勞強度可剖面因配合（H7/r6）引起的應(yīng)力集中系數(shù)查附表1-1k2.598,k1.872VI剖面因過渡圓角引起的應(yīng)力集中系數(shù)查附表1-2DdrJ02Z0.042d50k1.895,k1.60VD剖面因鍵槽引起的應(yīng)力集中系數(shù)查附表1-16.82I-辰均為有應(yīng)力集中的剖面，均有可能是危險剖面。其中I-in剖面計算彎矩相同，u、m剖面相比較，只是應(yīng)力集中影響不同。可取應(yīng)力集中系數(shù)值較大的值進行驗算即可。同理vn、皿剖面承載情況也接近，可取應(yīng)力集中系數(shù)較大者進行驗算。校核I、II剖面的疲勞強度I剖面因鍵槽引起的應(yīng)力集中系數(shù)查附表1-1插值k1.808,k

37、1.603II剖面因過渡圓角引起的應(yīng)力集中系數(shù)查附表1-2Ddr因I、3 n剖面主要受轉(zhuǎn)矩作用，k起主要作用，按I鍵槽引起的應(yīng)力集中系數(shù)計59376023.75Mpa0.2050k1.808,k1.603中vi配合引起的應(yīng)力集中系數(shù)校核vn剖面VI剖面承受的彎矩和轉(zhuǎn)矩分別為：MeB26876672MCL113950/2340437.84N.mmL1290可剖面產(chǎn)生正應(yīng)力maxM12.663MpaWamax12.663Mpa,m0VD剖面產(chǎn)生的扭剪應(yīng)力及其應(yīng)力幅、平均應(yīng)力為T593760maxWt323.75Mpa0.2503maxam211.875Mpa查附表1-40.680.74查附表1-5

38、0.94,0.92查表1-50.34,0.21Q13447521Sk2.5987.52112.6330am0.920.781199187211.8750.2123.750.920.745.24SS7.5215.247.52125.2424.21取S1.51.8,SS安全其它剖面與上述剖面相比，危險性小，不予校核7低速軸軸承的選擇及其壽命驗算低速軸軸承選擇一對30210圓錐滾子軸承條件：d=50mm,專速n=r/min,工作環(huán)境多灰塵，載荷稍有波動，工作溫度低于100，預(yù)計壽命L10h28830038000h7.1確定軸承的承載能力查表21-3軸承30210的co=55200N7.2計算軸承的徑

39、向支反力R.RAxRAz2986.13NR2JRBxRBz2453.12N7.3作彎矩圖如前7.4計算派生軸向力S查表9-830210軸承Y=1.5,C=722000,e=5R12Y995.38NS2R22Y817.71N§,S2的方向如圖FaS1115.24995.38211Q62NS2817.71N故1松2緊ASi995.38N,A2SFa2110.62N7.6計算軸承的當量動載荷P由&2110.630.4R12986.13查表9-6X10.4,丫1.5由程辿應(yīng)0.86R22453.12e0.4查表9-6X20.4,Y21.5查表9-7fd1.1根據(jù)合成彎矩圖取fm11,

40、fm21PfdfmX1RYA1.110.42986.131.5*2110.63P2fdfm2X2R2Y2A21.110.42453.121.52110.624561.90NP2PP，故按Pi計算查表9-4ft110,106ftC虧10610172200忑L10hMrE60nP6096.64796.444796.44N3800OhL0h30210適用1453444.21h故圓錐滾子軸承8鍵聯(lián)接的選擇和驗算8.1低速軸上鍵的選擇與驗算8.1.1齒輪處選擇鍵16X10其參數(shù)為L=56mmt=mmR=b/2=8mmk=h-t=10-6=4mm,l=L-2R=56-2x8=40mmd=54mm齒輪材料為

41、40Cr,載荷平穩(wěn)，靜聯(lián)接n120Mpap查表2-12516600119.58MpaP120Mpa安全544402TPdkl8.1.2聯(lián)軸器處選擇鍵14X9,其參數(shù)為L=70mmt=5.5mm,R=b/2=7mmk=h-t=9-5.5=3.5mm,l=L-2R=70-2x7=56mmd=48mm45#鋼，載荷稍有波動，靜聯(lián)接查表2-1p120Mpa齒輪材料為2Tpdkl251600、人109.82Mpap120Mpa安全483.5568.2中間軸上鍵的選擇與驗算選擇鍵14X9GB1096-2003A型，其參數(shù)為L=40mmt=5.5mm,R=b/2=7mmk=h-t=9-=mm,l=L-2R=

42、50-2x7=26mmd=50mm齒輪材料為45#鋼，載荷稍有波動，靜聯(lián)接查表2-1120Mpa2T2189130P90.36Mpap120Mpa安全dkl463.5268.3高速軸上鍵的選擇與驗算選擇鍵10X8GB1096-2003A型，其參數(shù)為L=45mmt=5mmR=b/2=5mmk=h-t=8-5=3mm,l=L-2R=45-2x5=35mmd=32mm齒輪材料為45#鋼，載荷稍有波動，靜聯(lián)接查得p120Mpa2TPdkl由表2-1,25937635.34Mpap120Mpa安全323359聯(lián)軸器的選擇9.1低速軸軸端處選擇TL8聯(lián)軸器,GB/T4323-20023名義轉(zhuǎn)矩T9.55P9.555386528.90Nmn96.6計算轉(zhuǎn)矩TcKT31.5516.6774.9Nm公稱轉(zhuǎn)矩Tn774.9NmT774.9Nm許用轉(zhuǎn)速n4000r/minn196.6r/min減速器低速軸外伸段d148mm,L82mm9.2高速軸軸端處選擇TL5聯(lián)軸器，GB/T4323-20023名義轉(zhuǎn)矩T9.55P9.555.80540.246Nmn1440計算轉(zhuǎn)矩TcKT1.540.24660.