設(shè)計膠帶輸送機的傳動裝置機械設(shè)計課程設(shè)計

1、機械設(shè)計課程設(shè)計機械設(shè)計課程設(shè)計說明書目錄1設(shè)計任務(wù)書31.1 題目名稱設(shè)計膠帶輸送機的傳動裝置31.2 工作條件41.3 技術(shù)數(shù)據(jù)42電動機的選擇計算42.1 選擇電動機系列42.2 滾筒轉(zhuǎn)動所需要的有效功率42.3 確定電動機的轉(zhuǎn)速53傳動裝置的運動及動力參數(shù)計算53.1 分配傳動比53.1.1 總傳動比53.1.2 各級傳動比的分配53.2 各軸功率、轉(zhuǎn)速和轉(zhuǎn)矩的計算63.2.1 I軸（高速軸）63.2.2 n軸（中間軸）63.2.3 出軸（低速軸）63.2.4 IV軸（傳動軸）63.2.5 V軸（卷筒軸）63.3 開式齒輪的設(shè)計73.3.1 材料選擇73.3.2 按齒根彎曲疲勞強度確定

2、模數(shù)73.3.3 齒輪強度校核83.3.4 齒輪主要幾何參數(shù)94閉式齒輪設(shè)計104.1 減速器高速級齒輪的設(shè)計計算104.1.1 材料選擇104.1.2 按齒面接觸疲勞強度確定中心距104.1.3 驗算齒面接觸疲勞強度124.1.4 驗算齒根彎曲疲勞強度-13-4.1.5 齒輪主要幾何參數(shù)-14-4.2 減速器低速級齒輪的設(shè)計計算-14-4.2.1 材料選擇-14-4.2.2 按齒面接觸疲勞強度確定中心距-15-4.2.3 驗算齒面接觸疲勞強度-16-4.2.4 驗算齒根彎曲疲勞強度-18-4.2.5 齒輪主要幾何參數(shù)-19-5軸的設(shè)計計算-19-5.1 高速軸的設(shè)計計算-19-5.2 中間軸

3、的設(shè)計計算-20-5.3 低速軸的設(shè)計計算-20-6低速軸的強度校核-21-6.1 繪制低速軸的力學(xué)模型-21-6.2 求支反力-21-6.3 作彎矩、轉(zhuǎn)矩圖-23-6.4 .4作計算彎矩Mca圖-24-6.5 .5校核該軸的強度-24-6.6 精確校核軸的疲勞強度-24-7低速軸軸承的選擇及其壽命驗算-26-7.1 確定軸承的承載能力-26-7.2 計算軸承的徑向支反力-26-7.3 作彎矩圖-26-7.4 計算派生軸向力S-26-7.5 求軸承軸向載荷-27-7.6 計算軸承的當量動載荷P-27-8鍵聯(lián)接的選擇和驗算-28-8.1 低速軸上鍵的選擇與驗算-28-8.1.1 齒輪處-28-8

4、.1.2 聯(lián)軸器處-28-8.2 中間軸上鍵的選擇與驗算-28-8.3 高速軸上鍵的選擇與驗算-28-9聯(lián)軸器的選擇-28-9.1 低速軸軸端處-29-9.2 高速軸軸端處-29-10減速器的潤滑及密封形式選擇-29-11參考文獻-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82多灰塵平穩(wěn)小批1.3 技術(shù)數(shù)據(jù)題號滾筒圓周力F(N)帶速v(m/s)滾筒直徑D(mm)滾筒長度L(mm)ZL-15180000.2540010002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38

5、0伏,Y系列。2.2 滾筒轉(zhuǎn)動所需要的有效功率PW1000170000.244.5kW1000傳動裝置總效率25彈聯(lián)剛聯(lián)閉齒開齒軸承筒查表17-9得彈性聯(lián)軸器的效率彈聯(lián)0.995剛性聯(lián)軸器的效率剛聯(lián)0.99閉式齒輪的嚙合效率閉齒0.97(8級精度)開式齒輪的嚙合效率開齒0.95滾動軸承的效率軸承0.98滾筒的效率筒0.96傳動裝置的總效率彈聯(lián)剛聯(lián)25閉齒開齒軸承卷筒一一一一一一一一2一一一一一5一一一0.9950.990.970.950.980.960.76252.3 確定電動機的轉(zhuǎn)速滾筒軸轉(zhuǎn)速nW0v11.94r/minD所需電動機的功率PrPw5.9kW7.5kW0.7625查表27-1,

6、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Y132M-47.515001440111.87Y132M-67.5100097094.21為使傳動裝置結(jié)構(gòu)緊湊，選用Y132MH4型，額定功率7.5kW,同步轉(zhuǎn)速1500r/min,滿載轉(zhuǎn)速1440r/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巫1440120.6nW11.943.1.2 各級傳動比的分配查表17-9取i開i566減速器的傳動比i減上螫苴20.1i開6高速級齒輪傳動比

7、i12#135豈J1.3520.15.21低速級齒輪傳動比i342013.86ii25.213.2 各軸功率、轉(zhuǎn)速和轉(zhuǎn)矩的計算3.2.1 0軸P=5.9kw,n=1440r/min,T=9.55*5.9/1440=40.246N*m3.2.2 I軸（高速軸）P1Pr彈聯(lián)5.90.9955.8705kWn0n11440r/mini013P15.870510T19.559.5538.93Nmn114403.2.3 II軸（中間軸）P2P1軸承閉齒5.87050.9950.975.666kWn11440n2-373.06r/mini123.8617n3n2373.063.8696.6r/minP35

8、.38610T39.559.55516.6Nmn396.63.2.4 IV軸（傳動軸）P4P3軸承剛聯(lián)5.3860.980.995.225kWn4n3i4596.696.634.605 10361.147664848.7N mmTCP4cT49.55P25.666 10T2 9.55 9.55145.04N mn2373.063.2.3田軸（低速軸）P3P 2 軸承 閉齒 5.6660.980.975.386kW9.55n43.2.5 V軸（卷筒軸）P5P4軸承開齒5.2250.990.954.864kW596.6n5-16.1r/mini5663P54.86410T59.559.552885

9、.17Nmn512.13.3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217HBSW162HBW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)N560n4jLh6066.2541.0(1030082)1.908108N6N5i561.908 10863.180 107查圖 5-18(b)查圖5-19Yn5Yn61.0Flim5270MPa,Flim6200Mpa由式5-32YX5YX61.0取YST2.0,S

10、Fmin1.4計算許用彎曲應(yīng)力由式5-31fFlimYsTYnYxSFmin270 2.01.41.0 1.0385.7Mpa200 2.01.41.0 1.0285.7Mpa查圖5-14YFa52.81,YFa62.21查圖5-15YSa51.56,YSa61.78YFa5YSa52.811.56則上2竺二0.011365385.7YFa6Ysa62.211780.013769285.7HYFaYsa取上_SamaxYFa5YSa5YFa6YSa6F50.013769初選綜合系數(shù)KtYt1.1,查表5-8d0.5由式5-262KT4YFaYsaYq321.15082760.013769dZ；

11、f-20.5204.254mm考慮開式齒輪工作特點m加大10%-15%取m=53.3.3齒輪強度校核dsmZs520100mmd6mZ65120600mmda5ds*2ham10021.05110mmda6d6*2hma60021.05610mmd52(h*、c)m10021.00.25587.5mmd6*2(h*、c)m60021.00.255587.5mmd52d6100600350mmb6aa0.2a35070mm取b5b6670676mmdb5d5cos20.93.969db6d6cos20.563.816則小齒輪轉(zhuǎn)速為d5jv360103.1410066.254360100.3467

12、m/sVZ51000.3467201000.06934查圖5-4(d)kv1.005查表5-3kA1.1bd5701000.70 由圖 5-7(a) k 1.18查表5-4k1.2計算載荷系數(shù)kkAkvk k1.1 1.005 1.18 1.2 1.5654db5a5arccosda5arccos93.96911031.3215db6a6arccosda6563.816 arccos61022.4387Z5 (tana5 tan)Z6 (tan a6 tan )20 (tan31.3215tan 20 ) 120 (tam22.4387tan 20 )F52KmiYFa5Ysa5丫70 100

13、 5199.305Mpa5安全YFa5Ysa5F6 F5Y YTFa6T sa6199.305Mpa2.81 1.562.21 1.78222.094Mpa6安全1.715Y0.25”0.25盆0.6873kY1.56540.68731.076與ktYt1.1相近，無需修正計算齒根彎曲應(yīng)力21.5654508276八，八2.811.563.3.4齒輪主要幾何參數(shù)Z520 Z6 120 u 65 a 350mmd5 100mm d6600mmda5110mm da6 610mmdf587.5mmdf6587.5mmdb593.969db6563.816b576mmb670mm4閉式齒輪設(shè)計4.1

14、 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217HBSW162HBW算_9N160n1jLh6014401(830082)3.4610N2N16.63108i12查圖5-17Zni1.0,Zn21.05(允許一定點蝕)由式5-29ZxiZx21.0取SHlim1.0,Zw1.0,Zlvr0.92(精加工)查圖5-16(b)Hlim1650Mpa,h515Mpa由式5-28H lim1SH minZN1ZX1ZwZLVR6501.01.0 1.01.00.92 59

15、8Mpa-Hm2ZN2ZX2ZvZLVR5151.051.01.00.9249749MpaSHmin1.0HminH1,H2497.49Mpa4.1.2 按齒面接觸疲勞強度確定中心距小輪轉(zhuǎn)矩T158705Nmm初定螺旋角13初取Ktz21.0,查表5-5ZE189.8v'Mpa減速傳動ui125.21取a0.4端面壓力角tarctan(tann/cos)arctan(tan20/cos13)20.4829基圓螺旋角barctan(tancost)arctan(tan13cos20.4829)12.2035由式5-42Z.coscos130.987由式5-41Zh2cos b cos t

16、 sin t2 COs12.2035；2.442cos20.4829 sin20.4829由式5-39取中心距(u八.KTi Zh ZeZ Z1)3 ).2aU H1.0 58705 2.442 1898 0.987(5.21 1)32 0.4 5.21497.49141.8mma 145mm估算模數(shù)mn(0.007 0.02)a 0.99 2.8mm取標準模數(shù) m 2mm小齒輪齒數(shù)2acos 2 145 cos13Zi 20.4m u 125.21 1大齒輪齒數(shù)z2uz1 5.21 20.4 106.27取乙21z2106實際傳動比i實學(xué)署504傳動比誤差在允許范圍內(nèi)i理i實i 100%i理

17、5.04 5.215.21100%3.1 % 5%修正螺旋角mn(Z2 Zi)arccos22 (23 104) arccos2 13012.3329與初選 13相近，Zh , Z可不修正輪分度圓直徑d1mnz1 /cos2 21/cos12.332942.99mmd2 mn Z2 / cos2 106/cos12.3369 217.00mm圓周速度v就342.99 144060 1033.24m/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5-3kA1.1vzi2.36623八八0.681100100查圖5-4(d)kv1.007齒寬baa0.4145

18、58.0mmb 52.0d147.08661.34查圖5-7(a)K1.12查表5-4K1.4載荷系數(shù)KKAKVKK1.72v1- J-t-t-irJ-，一_*_齒頂圓直徑da1d12ham46.99mmda2d22ham221.00mm端面壓力角齒輪基圓直徑tarctan(tann/cos)arctan(tan20/cos128386)20.4707db1d1cost42.99cos20.470740.275mmdb2d2cost221.00cos20.470720330mm端面齒頂壓力角dg40.275at1arccosarccosda146.9931.00823.09db2at2arcc

19、osda2203.30arccos221.001zi(tanatitant)Z2(tanat2tant)2121(tan31.008tan20.4707)106(tan23.09tan20.4707)21.971bsinmn58sin12.33291.9722由式5-43Z1j-10.712,1.971由式5-42Z.cos.cos12.33290.9883由式5-41barctan(tancost)arctan(tar12.3329cos20.4707)11.5759由男5-41Zh2cosbcostsint2cos11.57592.445cos20.4707sin20.4707hZhZeZ

20、Z2KT1u1bd12u2.445189.80.7120.987450.70MpaH安全4.1.4驗算齒根彎曲疲勞強度查圖5-18(b)Fiim1270Mpa,Fiim2200Mpa查圖5-19Yn11.0Yn21.0由式5-32Yx1Yx21.0取YST2.0SFmin1.4由式5-31f1Flim1YSTYnH270 1.971 58705 5.21 1p .58 47.086625.211.01.0385.7MpaSFmin1.4285.7MpaFlim2YSTYN2YX220021.01.0SFmin1.4機械設(shè)計課程設(shè)計ZV1Z1/C0S321/cos312.332922.52433

21、Zv2Z2/COS106/cos12.3329113.691查圖5-14YFa12.75,YFa22.25查圖5-15Ysa11.575,Ysa21.80由式5-47計算Y,因1.9721.0,取1.00.897“.12.332911120120-41 -由式5-48Y0.25八一20.75cosb0.250.75cos211.57591.9710.6152由式5-44F12KT1bd1mnYFa>sa1Y丫21.971587065842.9922.751.5750.61520.897110.92MpaF1安全YFa2Ysa2110922.251.80F2F1110.92YF1YSa12

22、.751.575103.714Mpaf2安全4.1.5齒輪主要幾何參數(shù)乙21Z2106u5.21m212.3329mtmn/cos2.05d142.99mmd2217.00mmda146.99mmda2221.00mmdf140.275mmdf2203.30mm1a-(d1d2)145mmb166mmb258mmdb144.113mmdb2182.56mm4.2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241-286HBS大齒輪:45#鍛鋼，調(diào)質(zhì)處理，齒面硬度217-235HBS按齒面硬度241HBS?口217HBW算N360n3jLh60373.061

23、(830082)8.92108N38N4-2.3710i34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5-16(b)Hlim3650Mpa,Hlim4650Mpa由式5-28H lim3SH minZN3ZX3ZwZLVR6501.01. 1.0 1.0 0.92 598MpaZnZx,ZwZlvrSH min6501.01.05 1.0 1.0 0.92 627.9Mpahminh3,h4598Mpa4.2.2 按齒面接觸疲勞強度確定中心距小輪轉(zhuǎn)矩T2145040Nmm初定螺旋角13初取Kt

24、z21.0,查表5-5ZE189.8,；Mpa減速傳動ui343.86取a0.4端面壓力角tarctan(tann/cos)arctan(tan20/cos13)20.4829基圓螺旋角barctan(tancost)arctan(tan13cos20.4829)12.2035由式5-42Z,coscos130.987由式5-41 ZH2 cos b,cos t sin t2 Cos12.20352.442 cos20.4829 sin20.4829由式5-39取中心距at(u 1)3 KT1ZhZeZ Z 22 aU H(3.413 1)3.21.0 145040 2.442 1898 0.

25、9872 04 3.86627914667mma 150mm估算模數(shù)mn(0.0070.02)a1.053mm取標準模數(shù)m2.5mm小齒輪齒數(shù)2acos mn u 12 150 cos132.5 3.86 124.058大齒輪齒數(shù)Z4UZ33.8624.058 95.863取Z325z496實際傳動比i實z4963.84Z325在i理i實13.863.84傳動比誤差i100%J"100%0.52%5%i理3.86在允許范圍內(nèi)修正螺旋角arccosmn(z4-z3-)arccos2.5(2794)12.6222155與初選13相近，Zh,Z可不修正輪分度圓直徑 d3 mn 4 / co

26、s2.5 25/cos12.6264.050mmd4 mnZ4 / cos2.596/cos12.62244.942mm圓周速度vd3n231.25m/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電機驅(qū)動，稍有波動，查表5-3kA1VZ-31001.25251000.313查圖5-4(d)kv1.03齒寬baa0.415060.0mmbd360.064.0500.937查圖5-7(a)K1.08查表5-4K1.4載荷系數(shù)KKAKvKK11.031.081.41.557齒頂圓直徑da3d32ham64.05021.02.569.050mmda4d42ham245.9422

27、1.02.5250.942mm端面壓力角tarctan(tann/cos)arctan(tan20/cos12.62)20.4546齒輪基圓直徑db3d3cost64.050cos20.454660.012mmdb4d4cost245.942cos20.454623Q435mm端面齒頂壓力角at3arccos強arccos0.744 1.807"01229.645da369.050a3dat4arccos-23.324da41hZ3(tanat3tant)Z4(tanat4tant)21 c,c、cc，cc、25(tan29.645tan20.4546)96(tan23.324tan

28、20.4546)21.807bsin60sin12.621.7256mn2.5由式5-43Z1-由式5-42Z由式5-41cos12.620.9878barctan(tancost)arctan(tan2.62cos20.4546)11.85由式5-41 ZH12cos b cos t sin t2 cos11.85 cos20.4546 sin20.45462.444H ZhZeZ Z2KT2 u 1bd2 u2.444 189.8 0.772 0.98782 1.807 145040 3.86 1?260 64.0503.86480.649MpaH安全4.2.4驗算齒根彎曲疲勞強度查圖5-

29、18(b)尸小290Mpa,f9270Mpa查圖5-19Yn31.0Yn41.0由式5-32Yx3Yx41.0取YST2.0SFmin1.4由式5-31 f 3F lim 3YST 77"YN3YX3S=F min290 21.41.0 1.0 414.2MpaFlim4YSTYn4vx427021.01.0385.7MpaSFmin1.4ZV3Z3/cos325/cos312.6225.174V333_3_Zv4Z4/cos96/cos12.6296.794查圖5-14YFa32.62,Yf942.27查圖5-15YSa31.6,YSa41.80由式5-47計算Y ,因 1.807

30、 1.0,取1.0Y11112.260.89812012022 ,0.75cos b 八小 0.75 cos 11.85 由式 5-48 Y0.25 0.25 1.8070.5482KT22 1.807 145040F3-YFa3Ysa3Y Y2.62 1.56bd3 mn60 65.040 2.5n0.898 0.898120.215Mpa F 3安全F4 F3 YFa4YSa4120.215YFa3YSa32.27 1.782.62 1.6138.8Mpa4.2.5齒輪主要幾何參數(shù)Z325 Z4 96u 3.86m 2.512.62mtmn / cos2.5664.050mmd4245.9

31、42mmda369.050mmda4250.942mm56.887 mm227.31mmb3d b312(d3 d4)70mm b460.012mm150mm60mmdb4 230.435mm5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P5.9kW轉(zhuǎn)速n960r/min查表8-2Ao110dAo 3P-5.9110317.57mmn1440由于軸上有一個鍵槽，則d17.57(3%5%1)18.1018.45dmind取dmin32mm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E80mm則d0.81.0d由和0.81.03830.438

32、mm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P59103名義轉(zhuǎn)矩T9.559.5540.246Nmn1440查表11-1工作情況系數(shù)K1.251.5，取K1.5計算轉(zhuǎn)矩TcKT1.540.24660.369Nm查表22-1選TL6公稱轉(zhuǎn)矩Tn250NmTc59.688Nm許用轉(zhuǎn)速n3300r/minn11440r/min軸孔直徑dmin30mm,dmax38mm取減速器高速軸外伸段軸徑d=32mm打選聯(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P5.3

33、86kW,轉(zhuǎn)速n208.696r/min查表8-2A。118P5.386dA03110328.7mmn373.06由于軸上有一個鍵槽，則d28.7(3%5%1)29.56130.135dmind取dmin40mm5.3 低速軸的設(shè)計計算軸的材料為選擇40Cr,調(diào)質(zhì)處理，傳遞功率P4.699kW,轉(zhuǎn)速n61.147r/min查表8-2A0118dA031P1183佟竺645.08mm由于軸上有一個鍵槽，則、n、96.6d45.08(3%5%1)46.432447.334dmind取dmin50mm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)軸名義轉(zhuǎn)矩T9.55-

34、9.555.38610532.033Nmn96.6計算轉(zhuǎn)矩TcKT3665.04Nmc查表22-1選TL8查表11-1工作情況系數(shù).T取1.25公稱直徑Tn710NmTc665.04Nm許用轉(zhuǎn)速n2100r/minn96.6r/min減速器低速軸外伸段d150mm,L112mm從動端d20mm,L112mm6低速軸的強度校核6.1 繪制低速軸的力學(xué)模型L1124.4mmL260.8mm作用在齒輪的圓周力Ft,霓翳例。04。徑向力FrFttan4330.045tan20.45461615.028N軸向力FaFttan4330.045tan12.62969.446N6.2 求支反力水平支反力Mb0

35、Rax(LiL2)FtL20FtL2L1L26095.01460.8124.460.82000.955X0,RBxFtRAx6095.0142000.9554094.059N垂直支反力d一Mb0Raz(LiL2)FrL2Fa0RFrL2Fai2273.32960.81356.570120.409-Li L2124.4 60.8Raz2135.663NRBzFrRAz2273.329(135.663)2408.992NF,IQ2777015iMrrnrn9127期中ee1號產(chǎn)產(chǎn)蛭加、TS3247O1100«S.Mhlhmm6.3 作彎矩、轉(zhuǎn)矩圖（上圖）水平彎矩MxC點McxRa3138

36、6.885139192777.015Nmm垂直彎矩MzC點左MczRAzL165.6691399127.991NmmC點右M'czRBzL21680.69765.5110085.654Nmm合成彎矩McC點左Mcv'MXMT192992.995Nmmccxczc點右M'c'M221995.110NmmJ/xJ/z轉(zhuǎn)矩T532470Nmm6.4 .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.M<2一(一Tc)2,(192992.995)2(0.6532470)2373249.306NmmC點右MCac

37、,Mc2(Tc)2.(221995.110)2(0.60)2221995.110NmmD點McaD.MD(TD)2.02(0.6532472)2319482Nmm6.5 .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8-1B736Mpa查表8-3b169MpaMcaC508630.646C點軸徑dc3.ca3-41.929mm-0.1b10.169因為有一個鍵槽dc41.929(10.05)42.934mm62mm安全D點軸徑dD3-'McaDJ440336739.962mm,0.1b110.16940.96

38、7mm 50mm 安全因為有一個鍵槽dD39.962(10.05)6.6精確校核軸的疲勞強度I-IX均為有應(yīng)力集中的剖面，均有可能是危險剖面。其中I-田剖面計算彎矩相同，H、m剖面相比較，只是應(yīng)力集中影響不同?？扇?yīng)力集中系數(shù)值較大的值進行驗算即可。同理即、Vffl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,k1.603II剖面因過渡圓角引起的應(yīng)力集中系數(shù)查附表1-20.025550r22.5-2d50因I、H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max27.299MpaT

39、5324703WT0.20503max213.650Mpa查表8-11344Mpa1199Mpa查附表1-40.730.78查附表1-50.9160.916查表1-50.34,0.211991.6030.9160.7820.1340.2120.134取S1.51.8,SS安全校核VI、VD的疲勞強度VI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1-24.028J 68 J0 4Li192993.058139139 50/2158282N.mmvn剖面產(chǎn)生正應(yīng)力max12.663M par2-0.033d60k1.8

40、95,k1.60VD剖面因鍵槽引起的應(yīng)力集中系數(shù)查附表1-1k1.808,k1.603按VI配合引起的應(yīng)力集中系數(shù)校核即剖面VI剖面承受的彎矩和轉(zhuǎn)矩分別為：amax12.663Mpa,vn剖面產(chǎn)生的扭剪應(yīng)力及其應(yīng)力幅、平均應(yīng)力為T532420WT0.250312.325Mpamaxam-26.162Mpa查附表1-40.680.74查附表1-50.94,0.92查表1-50.34,0.213442.5980.92 0.7812.325 06.7211991.8720.92 0.746.162 0.21 12.32510.188S S22S2 s29.262 7.916,9.262 2 7.91

41、6210.288取 S 1.5 1.8, S S 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30211圓錐滾子軸承條件：d=55mm$速n=61.147r/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Loh 2 8 8 300 38000 h7.1 確定軸承的承載能力查表 21-3 軸承 30212 的 c0=74500N7.2 計算軸承的徑向支反力RR；XR：z1388.439NR2. RBx RBZ3389.228N7.3 作彎矩圖（如前）7.4 計算派生軸向力S查表 9-8 30212 軸承 Y=1.5, C=

42、97800 , e=0.4S1R1 2Y 462.813NS2R22Y1129.743NSi，S2的方向如圖7.5求軸承軸向載荷Fa S1969.460 462.8131432.273N S2 1129.743NA S1462.813N, A2 S1Fa1432.259N7.6計算軸承的當量動載荷由 Ah462.8130.333 eR11388.4390.4查表 9-6 X11,Y10由2 1432.259 0.423 eR23389.2280.4查表9-6X204丫21.5查表9-7fd 1.1根據(jù)合成彎矩圖取fm11, fm2P2fd fmi X1R1YlAfdfm2 X2R2Y2 A21.1 11.11388.439 01527.283N0.4 4750.217 1.5 2025.0865431.