畢業(yè)設(shè)計(jì)錐斜軸系1

1、重慶工商大學(xué)2009屆畢業(yè)“論文”設(shè)計(jì)題 目： B650帶式輸送機(jī)驅(qū)動(dòng)裝置 子 題 目： 軸系設(shè)計(jì)計(jì)算 專 業(yè)： 機(jī)械設(shè)計(jì)及自動(dòng)化 姓 名： × × × 班 級(jí)： × × × 指導(dǎo)教師： 王 永 安 起止日期： 2012年1月18日至2012年5月18日 目 錄1 設(shè)計(jì)題目······················&

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8、·25.1 高速軸的設(shè)計(jì)計(jì)算···············································

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11、;················55.4軸承的設(shè)計(jì)································&#

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14、183;···············································127 參考文獻(xiàn)·

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16、············121. 設(shè)計(jì)題目1.1 主標(biāo)題：B650帶式輸送機(jī)驅(qū)動(dòng)裝置設(shè)計(jì)。1.2副標(biāo)題：軸系設(shè)計(jì)計(jì)算2. 工況條件：B650帶式輸送機(jī)由電動(dòng)機(jī)驅(qū)動(dòng)，傳動(dòng)滾筒驅(qū)動(dòng)合力F=6500N，輸送機(jī)帶速=2.5m/s，輸送機(jī)傳動(dòng)滾筒直徑D=500mm（包膠），輸送機(jī)工作壽命10年（每天工作8小時(shí)，每年工作300天），單向運(yùn)轉(zhuǎn)，有粉塵，室內(nèi)工作。3. 減速器類型采用錐-斜齒輪直角軸兩級(jí)齒輪減速器。4. 動(dòng)力參數(shù)4.1驅(qū)動(dòng)裝置所需的動(dòng)力參數(shù)列于下表：軸編號(hào)電動(dòng)機(jī)減速器傳動(dòng)滾筒

17、O軸軸軸軸軸轉(zhuǎn)速r/minn0=970n1=970n2=381.89n3=95.49n4=95.49功率kWP0=20.2P1=20.06P2=18.86P3=17.38P4=17.09轉(zhuǎn)矩N·mT0=60.23T1=59.78T2=338.82T3=1378.2T4=1709.2兩軸連接聯(lián)軸器齒輪齒輪聯(lián)軸器傳動(dòng)比ii01=1i12=2.54i23=4i34=1傳動(dòng)效率0=0.991=0.942=0.963=0.984.2齒輪受力情況列于下表：齒輪位置軸軸軸z1=19z2=66z3=21z4=84圓周力Ft / NFt1=1592.5Ft2=1592.5Ft3=7879.5Ft4=7

18、879.5徑向力Fr / NFr1 =539.3Fr2 =539.3Fr3 =2936.2Fr4 =2936.2軸向力Fa / NFa1=212.4Fa2=212.4Fa3=1729.5Fa4=1729.5法向力Fn / NFn1=1694.7Fn2=1694.7Fn3=8584.8Fn4=8584.85. 軸系的設(shè)計(jì)計(jì)算5.1高速軸的設(shè)計(jì)計(jì)算1）已知條件高速軸（軸I）傳遞功率P1=20.06kW，n1=970r/min，小齒輪大端分度圓直徑d1=91mm，齒寬中點(diǎn)處分度圓直徑dm1=（1-0.5R）d1=75.075mm，齒輪寬度b=60mm。2）軸的材料選擇選用45號(hào)鋼，調(diào)制處理，熱處理硬

19、度HB217255。3）軸的強(qiáng)度計(jì)算軸的強(qiáng)度計(jì)算均按照實(shí)心軸進(jìn)行計(jì)算（1）按扭轉(zhuǎn)強(qiáng)度計(jì)算 d1 = A = 115×=31.56mm式中：T1高速軸傳遞的扭矩，T1=59.78N.m； 許用切應(yīng)力，查表5-1-7得=35MPa，A=115按照表5-1-8，該軸增大后的直徑31.56+31.56×5%=33.14mm（2）按彎矩合成強(qiáng)度計(jì)算校核 = -1d = 式中：軸截面的工作應(yīng)力，MPaM軸截面的合成彎矩，N.mm脈動(dòng)循環(huán)系數(shù)，=0.6T軸截面的轉(zhuǎn)矩，N.mm-1許用彎曲應(yīng)力，MPa，查表5-1-1得，-1=215MPaM= =63115Nmm= =19.95MPa &l

20、t; -1符合設(shè)計(jì)要求4）支承點(diǎn)的載荷計(jì)算根據(jù)軸的支點(diǎn)布置，可取軸承1和軸承2的跨度L1=80mm，軸承2與齒輪寬度中點(diǎn)距離L2=120mm。則Fr1=×Ft =×1592.54=637NFr2=×Ft =×1592.54=956N5.2 中間軸的設(shè)計(jì)計(jì)算1）已知條件中間軸（軸II）傳遞功率P2=18.86kW，n2=381.89r/min，傳遞轉(zhuǎn)矩T2=338.82N.m，小齒輪分度圓直徑d3=86mm，齒輪寬度60mm。2）軸的材料選擇選用45號(hào)鋼，調(diào)制處理，熱處理硬度HB217255。3）軸的強(qiáng)度計(jì)算軸的強(qiáng)度計(jì)算均按照實(shí)心軸進(jìn)行計(jì)算（1）按扭轉(zhuǎn)強(qiáng)度

21、計(jì)算 d2 = A = 115×=42.19mm式中：T2中間軸傳遞的扭矩，T2=338.82N.m； 許用切應(yīng)力，查表5-1-7得=35MPa，A=115按照表5-1-8，該軸增大后的直徑42.19+42.19×5%=44.3mm（2）按彎矩合成強(qiáng)度計(jì)算校核 = -1d = 式中：軸截面的工作應(yīng)力，MPaM軸截面的合成彎矩，N.mm脈動(dòng)循環(huán)系數(shù)，=0.6T軸截面的轉(zhuǎn)矩，N.mm-1許用彎曲應(yīng)力，MPa，查表5-1-1得，-1=215MPaM= =361578Nmm= =47.7MPa < -1符合設(shè)計(jì)要求4）支承點(diǎn)的載荷計(jì)算根據(jù)軸的支點(diǎn)布置，可取軸承1和錐齒輪的距離

22、L1=100mm，錐齒輪和小斜齒輪的跨距L2=150mm，小斜齒輪與軸承2的跨度L3=100mm。則Fr3=×Ft =×7879.5=2251NFr4=×Ft =×7879.5=5628N5.3 低速軸的設(shè)計(jì)計(jì)算1）已知條件低速軸（軸）傳遞功率P3=17.38kW，n3=95.49r/min，傳遞轉(zhuǎn)矩T3=1378.2N.m，齒輪分度圓直徑d4=344mm，齒輪寬度95mm。2）軸的材料選擇選用45號(hào)鋼，調(diào)制處理，熱處理硬度HB217255。3）軸的強(qiáng)度計(jì)算軸的強(qiáng)度計(jì)算均按照實(shí)心軸進(jìn)行計(jì)算（1）按扭轉(zhuǎn)強(qiáng)度計(jì)算 d3 = A = 115×=65.

23、17mm式中：T3低速軸傳遞的扭矩，T3=1378.2N.m； 許用切應(yīng)力，查表5-1-7得=35MPa，A=115按照表5-1-8，該軸增大后的直徑65.17+65.17×5%=68.43mm（2）按彎矩合成強(qiáng)度計(jì)算校核 = -1d = 式中：軸截面的工作應(yīng)力，MPaM軸截面的合成彎矩，N.mm脈動(dòng)循環(huán)系數(shù)，=0.6T軸截面的轉(zhuǎn)矩，N.mm-1許用彎曲應(yīng)力，MPa，查表5-1-1得，-1=215MPaM= =1446312Nmm= =52MPa < -1符合設(shè)計(jì)要求4）支承點(diǎn)的載荷計(jì)算Fr5= =2446 NFr6=6136N5.4 軸承的設(shè)計(jì) 軸軸承的設(shè)計(jì)校核1）初選軸承型

24、號(hào)：按照軸的軸徑和工作條件，初選軸承型號(hào)為30207，由表6-1-54查得，Cr=51.5kN，C0r=37.2kN，e=0.37，Y=1.6。2）計(jì)算兩軸承所受的軸向力S1、S2和軸向載荷Fa1和Fa2由表6-1-21： S1=199N S2=298.8N因?yàn)椋?S1+Fa1=199+214.4=413.4>S2所以： Fa1=S1=199N Fa2= S1+ Fa1=413.4N3）當(dāng)量載荷軸承=0.31<e=0.37，因此，由表6-1-20查得X1=1，Y1=0 P1=fp·Fr1由表6-1-19，取fp =1.5P1=1.5× 637=956N軸承=0.

25、43>e=0.37，因此，由表6-1-20查得X2=0.4，Y2=1.5P2= fp(X2Fr2+Y2Fa2)=1.5（0.4×956+1.5×413.4）=1504N4）軸承壽命由于P1<P2，因此按P2計(jì)算L10h=2240139h>20000h滿足要求。 軸軸承的設(shè)計(jì)校核1）初選軸承型號(hào)：按照軸的軸徑和工作條件，初選軸承型號(hào)為30209，由表6-1-54查得，Cr=64.2kN，C0r=47.8kN，e=0.4，Y=1.5。2）計(jì)算兩軸承所受的軸向力S3、S4和軸向載荷Fa3和Fa4由表6-1-21： S3=662N S4=1876N因?yàn)椋?S3+F

26、a3=662+1729.5=2391.5>S4所以： Fa3=S3=662N Fa4= S3+ Fa4=2391.5N3）當(dāng)量載荷軸承=0.29<e=0.4，因此，由表6-1-20查得X3=1，Y3=0 P3=fp·Fr3由表6-1-19，取fp =1.5P3=1.5× 2251=3376.5N軸承=0.42>e=0.4，因此，由表6-1-20查得X4=0.4，Y4=1.5P4= fp(X4Fr4+Y4Fa4)=1.5（0.4×5628+1.5×2391.5）=8758N4）軸承壽命由于P3<P4，因此按P4計(jì)算L10h=156277h>20000h滿足要求。 軸軸承的設(shè)計(jì)校核1）初選軸承型號(hào)：按照軸的軸徑和工作條件，初選軸承型號(hào)為30314，由表6-1-54查得，Cr=208kN，C0r=162kN，e=0.35，Y=1.7。2）計(jì)算兩軸承所受的軸向力S5、S6和軸向載荷Fa5和Fa6由表6-1-21： S5=719N S6=1805N因?yàn)椋?S5+Fa5=719+1729.5=2448.5>S4所以： Fa5=S5=719N Fa6= S5+ Fa5=2448.5N3）當(dāng)量載荷軸承=0.29<