二級圓錐齒輪減速器設計說明書

word文檔可自由復制編輯一?設計任務書····················································································2二?電機的選擇計算1.擇電機的轉(zhuǎn)速·················································································22.工作機的有效功率···········································································23.選擇電動機的型號···········································································3三?運動和動力參數(shù)的計算分配傳動比·············································································3各軸的轉(zhuǎn)速·············································································3各軸的功率·············································································44.各軸的轉(zhuǎn)矩····················································································4四?傳動零件的設計計算1.閉式直齒輪圓錐齒輪傳動的設計計算·················································42.閉式直齒輪圓柱齒輪傳動的設計計算·················································6五?軸的設計計算減速器高速軸I的設計·······························································9減速器低速軸II的設計····························································113.減速器低速軸III的設計··································································14六?滾動軸承的選擇與壽命計算1.減速器高速I軸滾動軸承的選擇與壽命計算·········································162.減速器低速II軸滾動軸承的選擇與壽命計算········································173.減速器低速III軸滾動軸承的選擇與壽命計算·····································18七?鍵聯(lián)接的選擇和驗算1.聯(lián)軸器與高速軸軸伸的鍵聯(lián)接·························································192.大圓錐齒輪與低速軸II的的鍵聯(lián)接···················································19大圓柱齒輪與低速軸III的的鍵聯(lián)接···········································20八?潤滑油的選擇與熱平衡計算1.減速器的熱平衡計算·······································································212.潤滑油的選擇···············································································22九?參考文獻···················································································23計算內(nèi)容計算結(jié)果一對圓錐滾子軸承的效率η3=0.98一對球軸承的效率η4=0.99閉式直齒圓錐齒傳動效率η5=0.95閉式直齒圓柱齒傳動效率η6=0.97b.總效率η=η1η22η33η4η5η6=0.96×0.992×0.983×0.99×0.95×0.97=0.808c.所需電動機的輸出功率Pr=Pw/η=2.4/0.808=3kw選擇電動機的型號查參考文獻[1]表4-12.2得表1.1方案號電機類型額定功率同步轉(zhuǎn)速滿載轉(zhuǎn)速總傳動比1Y100L2-431500142022.2942Y132S-63100096015.072根據(jù)以上兩種可行同步轉(zhuǎn)速電機對比可見，方案2傳動比小且質(zhì)量價格也比較合理，所以選擇Y132S-6型電動機。動和動力參數(shù)的計算分配傳動比總傳動比i=15.072各級傳動比：直齒輪圓錐齒輪傳動比i12=3.762，直齒輪圓柱齒輪傳動比i23=4實際總傳動比i實=i12i34=3.762×4=15.048,∵Δi=0.021﹤0.05，故傳動比滿足要求滿足要求。各軸的轉(zhuǎn)速（各軸的標號均已在圖1.1中標出）n0=960r/min，n1=n0=960r/min，n2=n1/i12=303.673r/min，n3=n2/i34=63.829r/min，n4=n3=63.829r/min各軸的功率η=0.808Pr=3kw選用三相異步電動機Y132S-6p=3kwn=960r/mini=15.072i12=3.762i23=4n0=960r/minn1=960r/minn2=303.67r/minn3=63.829r/minn4=63.829r/min3.計算內(nèi)容計算結(jié)果p0=pr=3kw，p1=p0η2=2.970kw,p2=p1η4η3=2.965kw,p3=p2η5η3=2.628kw,p4=p3η2η3=2.550kw4.各軸的轉(zhuǎn)矩，由式：T=9.55Pi/ni可得：T0=29.844N·m,T1=29.545N·m,T2=86.955N·m,T3=393.197N·m,T4=381.527N·m四，傳動零件的設計計算1.閉式直齒輪圓錐齒輪傳動的設計計算a．選材：小齒輪材料選用45號鋼，調(diào)質(zhì)處理，HB=217~255，σHP1=580Mpa，σFmin1=220Mpa大齒輪材料選用45號鋼，正火處理，HB=162~217，σHP2=560Mpa，σFmin2=210Mpab.由參考文獻[2]（以下簡稱[2]）式（5—33），計算應力循環(huán)次數(shù)N：N1=60njL=60×960×1×8×11×250=1.267×10eq\o(\s\up5(9),\s\do2())N2=N1/i2=1.267×10/3=2.522×10eq\o(\s\up5(8),\s\do2())查圖5—17得ZN1=1.0，ZN2=1.12，由式（5—29）得ZX1=ZX2=1.0，取SHmin=1.0，ZW=1.0，ZLVR=0.92，∴[σH]1=σHP1ZLVRZWZX1ZN1/SHmin=580×0.92=533.6Mpa，[σH]2=σHP2ZN2ZX2ZWZLVR/SHmin=560×1.12×0.92=577Mpa∵[σH]1>[σH]2，∴計算取[σH]=[σH]2=533.6Mpac．按齒面接觸強度設計小齒輪大端模數(shù)（由于小齒輪更容易失效故按小齒輪設計）：取齒數(shù)Z1=21，則Z2=Z1i12=3.762×32=79，取Z2=79∵實際傳動比u=Z2/Z1=79/21=3.762，且u=tanδ2=cotδ1，∴δ2=72.2965eq\o(\s\up5(o),\s\do2())=72eq\o(\s\up5(o),\s\do2())1635，δ1=17.7035eq\o(\s\up5(o),\s\do2())=17eq\o(\s\up5(o),\s\do2())4212，則小圓錐齒輪的當量齒數(shù)zm1=z1/cosδ1=21/cos17.7035eq\o(\s\up5(o),\s\do2())=23，zm2=z2/cosδ2=79/cos72.2965eq\o(\s\up5(o),\s\do2())=259.79p0=3kwp1=2.970kwp2=2.965kwp3=2.628kwp4=2.550kwT0=29.844N·mT1=29.545N·mT2=86.955N·mT3=393.197N·mT=381.527N·mσHP1=580Mpa，σFmin1=220MpaσHP2=560Mpa，σFmin2=210Mpa[σH]=533.6Mpa圓錐齒輪參數(shù)Z1=21Z2=79δ1=17eq\o(\s\up5(o),\s\do2())4212δ2=72eq\o(\s\up5(o),\s\do2())16354.計算內(nèi)容計算結(jié)果此資料來自舉哥設計工作室，淘寶網(wǎng)搜索店鋪舉哥設計工作室進入店鋪搜索二級圓錐齒輪減速器可獲得此設計的整套資料，下面為此套資料的文件列表截圖由[2]圖5-14，5-15得YFa=2.8，Ysa=1.55，YFa2=2.23，Ysa2=1.81ZH=√2/cosα×sinα=√2/cos20eq\o(\s\up5(o),\s\do2())×sin20eq\o(\s\up5(o),\s\do2())=2.5由[2]表11-5有ZE=189.8，取Kt·Zeq\o(\s\up5(2),\s\do2(εt))=1.1，由[2]取K=1.4又∵T1=28.381N·m，u=3.762，фR=0.3由[2]式5-56計算小齒輪大端模數(shù)：m≥√4KT1YFaYsa/{фRZeq\o(\s\up7(2),\s\do3(1))[σF]（1-0.5фR）2√u2+1}將各值代得m≥1.498由[2]表5-9取m=3㎜d．齒輪參數(shù)計算：大端分度圓直徑d1=mz1=3×21=63㎜，d2=mz2=3×79=237㎜齒頂圓直徑da1=d1+2mcosδ1=63+6cos17.7035=68.715㎜，da2=d2+2mcosδ2=237+6cos72.2965eq\o(\s\up5(o),\s\do2())=238.827㎜齒根圓直徑df1=d1-2.4mcosδ1=63-7.2cos17.7035eq\o(\s\up5(o),\s\do2())=56.142㎜df2=d2-2.4mcosδ2=237-7.2×cos72.2965eq\o(\s\up5(o),\s\do2())=231.808㎜齒輪錐距R=√d1+d2/2=122.615㎜，大端圓周速度v=∏d1n1/60000=3.14×63×960/60000=3.165m/s，齒寬b=RфR=0.3×122.615=36.78㎜由[2]表5-6，選齒輪精度為8級由[1]表4.10-2得Δ1=（0.1～0.2）R=（0.1～0.2）305.500=30.05～60.1㎜取Δ1=10㎜，Δ2=14㎜,c=10㎜輪寬L1=（0.1～0.2）d1=（0.1～0.2）93=12.4㎜L2=（0.1～0.2）d2=（0.1～0.2）×291=39㎜e．驗算齒面接觸疲勞強度：按[2]式5-53σH=ZHZE√2KT1√u+1/[bdeq\o(\s\up7(2),\s\do3(1))u（1-0.5фR）2]，代入各值得圓錐齒輪參數(shù)m=3㎜d1=63㎜d2=237㎜da1=68.715㎜da2=238.827㎜df1=56.142㎜df2=231.808㎜R=122.615㎜v=3.165m/sb=36.78㎜Δ1=10㎜Δ2=14㎜c=10㎜L1=12.4㎜L2=39㎜5.計算內(nèi)容計算結(jié)果σH=470.899﹤[σH]=533.6Mpa∴小齒輪滿足接觸疲勞強度，且大齒輪比小齒輪接觸強度高，故齒輪滿足接觸強度條件f．齒輪彎曲疲勞強度校核：按[2]式5-55由[2]圖5-19得YN1=YN2=1.0，由[2]式5-32及m=2﹤5㎜，得YX1=YX2=1.0取YST=2.0，SFmin=1.4，由[2]式5-31計算許用彎曲應力：[σF1]=σFmin1YFa1Ysa1YST/SFmin=220×2.0/1.4=314.29Mpa[σF2]=σFmin2YFa2Ysa2YST/SFmin=210×2.0/1.4=300Mpa∵[σF1]﹥[σF2]，∴[σF]=[σF2]=300Mpa由[2]式5-24計算齒跟彎曲應力：σF1=2KT1YFa1Ysa1/[b1md1（1-0.5фR）]=2×1.4×80070×2.8×1.55/0.85×2×28.935×62=181.59﹤300MpaσF2=σF1YFa2Ysa2/（YFa1Ysa1）=181.59×1.81×2.23/（2.8×1.55）=178.28﹤300Mpa∴兩齒輪滿足齒跟彎曲疲勞強度2.閉式直齒輪圓柱齒輪傳動的設計計算a．選材：小齒輪材料選用45號鋼，調(diào)質(zhì)處理，HB=217~255，σHP1=580Mpa，σFmin1=220Mpa大齒輪材料選用45號鋼，正火處理，HB=162~217，σHP2=560Mpa，σFmin2=210Mpab.由參考文獻[2]（以下簡稱[2]）式（5—33），計算應力循環(huán)次數(shù)N：N1=60njL=60×960×1×8×11×250=1.267×10eq\o(\s\up5(9),\s\do2())，N2=N1/i23=1.267×10/3=2.522×10eq\o(\s\up5(8),\s\do2())查圖5—17得ZN1=1.05，ZN2=1.16，由式（5—29）得ZX1=ZX2=1.0，取SHmin=1.0，ZW=1.0，ZLVR=0.92，[σH]1=σHP1ZLVRZWZX1ZN1/SHmin=580×1.05×0.92=560.28MPa[σH]=533.6Mpa[σF]=300MpaσHP1=580MpaσFmin1=220MpaσHP2=560MpaσFmin2=210Mpa6.計算內(nèi)容計算結(jié)果[σH]2=σHP2ZN2ZX2ZWZLVR/SHmin=560×1.16×0.92=597.63MPa∵[σH]1>[σH]2，∴計算取[σH]=[σH]2=560.28Mpac.按齒面接觸強度計算中心距（由于小齒輪更容易失效故按小齒輪設計）：∵u=i34=4，фa=0.4，ZH=√2/cosα·sinα=√2/cos200·sin200=2.5且由[2]表11-5有ZE=189.8，取Kt·Zeq\o(\s\up5(2),\s\do2(εt))=1.1∴[2]式5-18計算中心距：a≥（1+u）√KT1（ZEZHZε/[σH]）2/（2uφa）=5×√1.1×86955×2.5×189.8/（2×4×0.4×560.28）=147.61㎜由[1]表4.2-10圓整取a=160㎜d．齒輪參數(shù)設計：m=（0.007～0.02）a=180（0.007～0.02）=1.26～3.6㎜查[2]表5-7取m=2㎜齒數(shù)Z1=2a/m（1+u）=2×160/2（1+4）=32Z2=uZ1=4×32=128取Z2=128則實際傳動比i=149/31=4分度圓直徑d1=mz1=2×32=64㎜，d2=mz2=2×128=256㎜齒頂圓直徑da1=d1+2m=68㎜，da2=d2+2m=260㎜齒基圓直徑db1=d1cosα=64×cos20o=60.14㎜db2=d2cosα=256×cos20o=240.56㎜齒根圓直徑df1=d1-2.5m=64-2.5×2=59㎜df2=d2-2.5m=256-2.5×2=251㎜圓周速度v=∏d1n2/60×103=3.14×256×63.829/60×103=1.113m/s，中心距a=（d1+d2）/2=160㎜齒寬b=aΦa=0.4×160=64㎜由[2]表5-6，選齒輪精度為8級[σH]=560.28Mpa圓柱齒輪參數(shù)m=2㎜Z1=32Z2=128d1=64㎜d2=256㎜da1=8㎜da2=260㎜db1=60.14㎜db2=240.56㎜df1=59㎜df2=251㎜v=1.113m/sa=160㎜b=64㎜7.計算內(nèi)容計算結(jié)果e.驗算齒面接觸疲勞強度按電機驅(qū)動，載荷平穩(wěn)，由[2]表5-3，取KA=1.0；由[2]圖5-4（d），按8級精度和VZ/100=∏dn/60000/100=0.30144，得Kv=1.03；由[2]表5-3得Ka=1.2；由[2]圖5-7和b/d1=72/60=1.2，得KB=1.13；∴K=KvKaKAKB=1.03×1.2×1.0×1.13=1.397又∵ɑa1=arccosdb1/da1=arccos（60.14/68）=28.0268eq\o(\s\up5(o),\s\do2())=28eq\o(\s\up5(o),\s\do2())136；ɑa2=arccosdb2/da2=arccos（2240.56/260）=22.0061eq\o(\s\up5(o),\s\do2())=22eq\o(\s\up5(o),\s\do2())017∴重合度εa=[z（tanɑa1-tanɑ）+z（tanɑa1-tanɑ）]/2∏=[32（tan28.0268eq\o(\s\up5(o),\s\do2())-tan20）+128（tan22.0061eq\o(\s\up5(o),\s\do2())-tan20）]=1.773即Zε=√（4-εa）/3=0.862，且ZE=189.8，ZH=2.5∴σH=ZHZEZε√2KT1（u+1）/bd21PAGE\#"'頁：'#'

'"u=2.5×189.8×0.862√2×1.397×83510×5.8065/（72×622×5.024）=240.63﹤[σH]=560.28PAGE\#"'頁：'#'

'"∴小齒輪滿足接觸疲勞強度，且大齒輪比小齒輪接觸強度高，故齒輪滿足接觸強度條件f．齒輪彎曲疲勞強度校核：按Z1=32，Z2=128，由[2]圖5-14得YFa1=2.56，YFa2=2.18；由[2]圖5-15得Ysa1=1.65，Ysa2=1.84由[2]式5-23計算Y=0.25+0.75/εa=02.5+0.75/1.773=0.673由[2]圖5-19得YN1=YN2=1.0，由[2]式5-32切m=2﹤5㎜，得YX1=YX2=1.0取YST=2.0，Sfmin=1.4，由[2]式5-31計算許用彎曲應力：[σF1]=σFmin1YFa1Ysa1YST/Sfmin=220×2.0/1.4=314.29Mpa[σF2]=σFmin2YFa2Ysa2YST/Sfmin=210×2.0/1.4=300Mpa[σF1]=314.29Mpa[σF2]=300Mpa8.計算內(nèi)容計算結(jié)果∵[σF1]﹥[σF2]，∴[σF]=[σF2]=300Mpa由[2]式5-24計算齒跟彎曲應力：σF1=2KT1YFa1Ysa1Y/bd1m=2×1.397×83510×2.56×1.65×0.673/（2×64×64）=71.233﹤300MpaσF2=σF1YFa2Ysa2/YFa1Ysa1=71.233×1.84×2.18/（2.56×1.65）=67.644﹤300Mpa∴兩齒輪滿足齒跟彎曲疲勞強度五，軸的設計計算減速器高速軸I的設計a.選擇材料：由于傳遞中小功率，轉(zhuǎn)速不太高，故選用45優(yōu)質(zhì)碳素結(jié)構(gòu)鋼，調(diào)質(zhì)處理，按[2]表8-3查得σB=637Mpa，[σb]-1=59Mpab.由扭矩初算軸伸直徑：按參考文獻[2]有d≥A√p/n∵n0=960r/min，p1=2.97kw，且A=0.11~0.16∴d1≥16~23㎜取d1=20㎜c.考慮I軸與電機伸軸用聯(lián)軸器聯(lián)接。并考慮用柱銷聯(lián)軸器，因為電機的軸伸直徑為dD=38㎜，查[1]表4.7-1選取聯(lián)軸器規(guī)格HL3（Y38×82，Y30×60），根據(jù)軸上零件布置，裝拆和定位需要該軸各段尺寸如圖1.2a所示該軸受力計算簡圖如圖1.2b，齒輪1受力：（1）圓周力Ft1=2T1/dm1=2×29.545/（64×10-3）=915.52N，（2）徑向力Fr1=Ft1·tanα·cosδ1=915.52×tan200·cos17.70350=317.44N，（3）軸向力Fa1=Ft1·tanα·sinδ1=915.52×tan200·sin17.70350=101.33N，e.求垂直面內(nèi)的支撐反力：∵ΣMB=0，∴Rcy=Ft1（L2+L3）/L2=915.52（74+55）/74=1595.97.97N∵ΣY=0，∴RBY=Ft1-Rcy=915.52-1595.97=-680.45N，[σF]=300MpaσB=637Mpa，[σb]-1=59Mpad1=20㎜選用柱銷聯(lián)軸器HL3（Y38×82，Y30×60）Ft1=915.52NFr1=317.44NFa1=101.33NRcy=1595.97NRBY=-680.45N9.計算內(nèi)容計算結(jié)果∴垂直面內(nèi)D點彎矩Mdy=0，Meq\o(\s\up5(1),\s\do2(dy))=RcyL3+RBY（L2+L3）=1595.97×55-680.45×129=3662.14N·㎜=3.662N·mf.水平面內(nèi)的支撐反力：∵ΣMB=0，∴RCz=[Fr1(L3+L2)-Fa1dm1/2]/L2=[317.44（74+55）-680.45×64]/74=419.07N，∵ΣZ=0，∴RBz=Fr1-RCz=317.44-419.07=-101.63N，∵水平面內(nèi)D點彎矩MDz=0，Meq\o(\s\up5(1),\s\do2(Dz))=RCzL3+RBz(L3+L2)=419.07×55-101.63×129=-7.095N·m合成彎矩：MD=√Meq\o(\s\up5(2),\s\do2(Dz))+Meq\o(\s\up5(2),\s\do2(Dy))=0N·m，Meq\o(\s\up5(1),\s\do2(D))=√Meq\o(\s\up5(12),\s\do2(Dy))+Meq\o(\s\up5(12),\s\do2(Dz))=7.98N·m作軸的扭矩圖如圖1.2c所示，計算扭矩：T=T1=29.545N·mI.校核高速軸I：根據(jù)參考文獻[3]第三強度理論進行校核：由圖1.2可知，D點彎矩最大，故先驗算D處的強度，∵MD＜Meq\o(\s\up5(1),\s\do2(D))，∴取M=Meq\o(\s\up5(1),\s\do2(D))=7.98N·m，又∵抗彎截面系數(shù)：w=∏d3min/32=3.14×203/32=1.045×10eq\o(\s\up5(-6),\s\do2())meq\o(\s\up5(3),\s\do2())∴σ=√Meq\o(\s\up5(2),\s\do2())+Teq\o(\s\up5(2),\s\do2())/w=√7.98eq\o(\s\up5(2),\s\do2())+29.545eq\o(\s\up5(2),\s\do2())/1.045×10eq\o(\s\up5(-6),\s\do2())=39.132≤[σb]-1=59Mpa故該軸滿足強度要求。2.減速器低速軸II的設計選擇材料：因為直齒圓柱齒輪的小輪直徑較?。X跟圓直徑db1=62㎜）需制成齒輪軸結(jié)構(gòu)，故與齒輪的材料和熱處理應該一致，即為45優(yōu)質(zhì)碳素結(jié)構(gòu)鋼，調(diào)質(zhì)處理按[2]表8-3查得σb=637Mpa，[σb]-1=59Mpa該軸結(jié)構(gòu)如圖1.3a，受力計算簡圖如圖1.3b齒輪2受力（與齒輪1大小相等方向相反）：Ft2=915.52N，F(xiàn)r2=317.44N，F(xiàn)a2=101.33N，齒輪3受力：Mdy=0Meq\o(\s\up5(1),\s\do2(dy))=3.662N·mRCz=419.07NRBz=-101.63NMDz=0Meq\o(\s\up5(1),\s\do2(Dz))=-7.095N·mMD=0N·m，Meq\o(\s\up5(1),\s\do2(D))=7.98N·mT=29.545N·mM=7.98N·mσb=637Mpa，[σb]-1=59MpaFt2=915.52NFr2=317.44NFa2=101.33N10.計算內(nèi)容計算結(jié)果（1）圓周力Ft3=2T2/dm3=2×86.955/（64×10-3）=2693.87N（2）徑向力Fr3=Ft2·tanα=2693.87×tan200=980.49Nc.求垂直面內(nèi)的支撐反力：∵ΣMB=0，∴RAy=[Ft2（L2+L3）+Ft3L3]/（L1+L2+L3）=[915.52（70+63）+2693.87×63]/183=1919.26N∵ΣY=0，∴RBY=Ft2+Ft3-Rcy=915.52+2693.87-1919.26=1690.13N∴垂直面內(nèi)C點彎矩：MCy=RAyL1=1919.26×21.5=41.26N·m，Meq\o(\s\up7(1),\s\do3(Cy))=RBY（L2+L3）-Ft3L2=1690.13×133-2693.87×70=41.26N·m，D點彎矩：MDy=RBYL3=1690.13×63=92.96N·m，Meq\o(\s\up7(1),\s\do3(Dy))=Ray（L1+L2）-Ft2L2=1919.26×120-915.52×70=92.96N·md.水平面內(nèi)的支撐反力：∵ΣMB=0，∴RAz=[Fr2(L3+L2)+Fr3L3-Fa2dm2/2]/（L1+L2+L3）=[317.44×133＋980.49×63-101.33×238.827/2]/128=750.70N∵ΣZ=0，∴RBz=Fr2+Fr3-RAz=317.44+980.49-750.70=547.23N，∵水平面內(nèi)C點彎矩：MCz=RAzL1=750.70×50=23.65N·m，M1Cz=RBz(L3+L2)-Fr3L2=547.23×133-980.49×70=-10.55N·m，D點彎矩：MDz=RBzL3=547.23×63=30.10N·m，M1Dz=RAz（L1+L2）-Fa2dm2/2-Fr2L2=750.70×120-101.33×164.9/2-317.44×70=29.92N·me.合成彎矩：MC=√Meq\o(\s\up5(2),\s\do2(Cz))+Meq\o(\s\up5(2),\s\do2(Cy))=47.56N·mMeq\o(\s\up5(1),\s\do2(C))=√Meq\o(\s\up5(12),\s\do2(Cy))+Meq\o(\s\up5(12),\s\do2(Cy))=42.59N·mFt3=2693.87NFr3=980.49NRAy=1919.26NRBY=1690.13NMCy=41.26N·mMeq\o(\s\up7(1),\s\do3(Cy))=41.26N·mMDy=92.96N·mMeq\o(\s\up7(1),\s\do3(Dy))=92.96N·mRAz=750.70NRBz=547.23NMCz=23.65N·mM1Cz=-10.55N·mMDz=30.10N·mM1Dz=29.92N·mMC=47.56N·mMeq\o(\s\up5(1),\s\do2(C))=42.59N·m11.計算內(nèi)容計算結(jié)果MD=√Meq\o(\s\up5(2),\s\do2(Dz))+Meq\o(\s\up5(2),\s\do2(Dy))=97.71N·m，Meq\o(\s\up5(1),\s\do2(D))=√Meq\o(\s\up5(12),\s\do2(Dy))+Meq\o(\s\up5(12),\s\do2(Dz))=97.66N·mf.作軸的扭矩圖如圖1.3c所，計算扭矩：T=T2=86.955N·mg.校核低速軸II強度，由參考文獻[3]第三強度理論進行校核：由圖1.3可知，D點彎矩最大，故先驗算D處的強度，∵MD＞Meq\o(\s\up5(1),\s\do2(D))，∴取M=Meq\o(\s\up5(1),\s\do2(D))=97.71N·m，∵抗彎截面系數(shù)：w=∏d3min/32=3.14×303/32=2.65×10-6m3∴σ=√M2+T2/w=√97.712+86.9552/2.65×10-3=44.27≤[σb]-1=59Mpa（2）.由于C點軸徑較小故也應進行校核：∵MC＞Meq\o(\s\up5(1),\s\do2(C))，∴取M=Meq\o(\s\up5(1),\s\do2(C))=47.56N·m，∵抗扭截面系數(shù)：w=∏d3min/32=3.14×303/32=2.65×10-6m3∴σ=√M2+T2/w=√47.562+86.9552/2.65×10-6=35.14≤[σb]-1=59Mpa故該軸滿足強度要求3.減速器低速軸III的設計a.選擇材料：由于傳遞中小功率，轉(zhuǎn)速不太高，故選用45優(yōu)質(zhì)碳素結(jié)構(gòu)鋼，調(diào)質(zhì)處理，按[2]表8-3查得σB=637Mpa，[σb]-1=59Mpab.該軸受力計算簡圖如圖1.2b齒輪4受力（與齒輪1大小相等方向相反）：圓周力Ft4=2693.87N，徑向力Fr4=980.49Nc.求垂直面內(nèi)的支撐反力：∵ΣMC=0，∴RBY=Ft4L1/（L1+L2）=2693.87×71/（125+71）=1157.52N∵ΣY=0，∴Rcy=Ft4-RBY=2693.87-1157.52=1536.35N，∴垂直面內(nèi)D點彎矩MDy=RcyL1=1536.35×55=84.50N·m，Meq\o(\s\up5(1),\s\do2(Dy))=RBYL2=1157.52×125=84.50N·md.水平面內(nèi)的支撐反力：MD=97.71N·mMeq\o(\s\up5(1),\s\do2(D))=97.66N·mT=86.955N·mM=47.56N·mσB=637Mpa[σb]-1=59MpaFt4=2693.87NFr4=980.49NRBY=1157.52NRcy=1536.35NMDy=84.50N·mMeq\o(\s\up5(1),\s\do2(Dy))=84.50N·m12.計算內(nèi)容計算結(jié)果 ∵ΣMC=0，∴RBz=Fr4L1/（L1+L2）=980.49×70/196=421.31N∵ΣZ=0，∴RCz=Fr4-RBz=980.49-421.31=559.18N，∵水平面內(nèi)D點彎矩MDz=RCzL1=559.18×71=30.75N·m，Meq\o(\s\up5(1),\s\do2(Dz))=RBzL2=421.31×125=30.76N·m合成彎矩：MD=√Meq\o(\s\up5(2),\s\do2(Dz))+Meq\o(\s\up5(2),\s\do2(Dy))=90.20N·m，Meq\o(\s\up5(1),\s\do2(D))=√Meq\o(\s\up5(12),\s\do2(Dy))+Meq\o(\s\up5(12),\s\do2(Dz))=89.92N·m作軸的扭矩圖如圖1.2c所，計算扭矩：T=T3=393.197N·mg.校核低速軸III：根據(jù)參考文獻[3]第三強度理論校核：由圖1.2可知，D點彎矩最大，故先驗算D處的強度，∵MD＞Meq\o(\s\up5(1),\s\do2(D))，∴取M=MD=90.20N·m，又∵抗彎截面系數(shù)：w=∏d3min/32=3.14×423/32=7.27×10-6m3∴σ=√M2+T2/w=√90.202+393.1972/7.27×10-6=55.73≤[σb]-1=59Mpa故該軸滿足強度要求。六，滾動軸承的選擇與壽命計算1.減速器高速I軸滾動軸承的選擇與壽命計算高速軸的軸承既承受一定徑向載荷，同時還承受軸向外載荷，選用圓錐滾子軸承，初取d=40㎜，由[1]表4.6-3選用型號為30208，其主要參數(shù)為：d=40㎜，D=80㎜，Cr=59800N，е=0.37，Y=1.6，Y0=0.9，Cr0=42800查[2]表9-6當A/R≤е時，X=1，Y=0；當A/RPAGE\#"'頁：'#'

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'"b.計算軸承D的受力（圖1.5），（1）支反力RB=√Req\o(\s\up5(2),\s\do2(BY))+Req\o(\s\up5(2),\s\do2(Bz))=√36.252+269.272=271.70N，RC=√Req\o(\s\up5(2),\s\do2(cy))+Req\o(\s\up5(2),\s\do2(Cz))=√1184.792+353.692=1236.46N（2）附加軸向力（對滾子軸承S=Fr/2Y）RBz=421.31NRCz=559.18NMDz=30.75N·mMeq\o(\s\up5(1),\s\do2(Dz))=30.76N·mMD=90.20N·mMeq\o(\s\up5(1),\s\do2(D))=89.92N·mT=393.197N·mM=90.20N·m選用圓錐滾子軸承30208（GB/T297-94）RB=271.70NRC=1236.46N13.計算內(nèi)容計算結(jié)果∴SB=RB/2Y=271.70/3=90.57N，SC=RC/2Y=1236.46/3=412.15Nc.軸向外載荷FA=Fa1=101.33Nd.各軸承的實際軸向力AB=max（SB，F(xiàn)A-SC）=FA-SC=310.82N，AC=（SC，F(xiàn)A+SB）=SC=412.15N計算軸承當量動載由于受較小沖擊查[2]表9-7fd=1.2，又軸I受較小力矩，取fm=1.5∵AB/RB=310.82/271.70=1.144＞е=0.37，取X=0.4，Y=1.6，∴PB=fdfm（XRB+YAB）=1.8×（0.4×271.7+1.6×310.82）=1090.79N∵AC/RC=412.15/1236.46=0.33＜е=0.37，取X=1，Y=0，∴PC=fdfm（XRC+YAC）=1.2×1.5×1×1236.46=2225.63N計算軸承壽命又PB＜PC，故按PC計算，查[2]表9-4得ft=1.0∴L10h=106（ftC/P）/60n1=106（59800/2225.63）10/3/（60×960）=0.12×106h，按每年250個工作日，每日一班制工作，即L1=60.26＞L=11年故該軸承滿足壽命要求。2.減速器低速II軸滾動軸承的選擇與壽命計算a.高速軸的軸承既承受一定徑向載荷，同時還承受軸向外載荷，選用圓錐滾子軸承，初取d=35㎜，由[1]表4.6-3選用型號為30207，其主要參數(shù)為：d=35㎜，D=72㎜，Cr=51500N，е=0.37，Y=1.6，Y0=0.9，Cr0=37200查[2]表9-6當A/R≤е時，X=1，Y=0；當A/RPAGE\#"'頁：'#'

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'"b.計算軸承D的受力（圖1.6）1.支反力RB=√Req\o(\s\up5(2),\s\do2(BY))+Req\o(\s\up5(2),\s\do2(Bz))=√1919.262+547.232=1995.75NSB=90.57NSC=412.15NFA=101.33NAB=310.82NAC=412.15NPB=1090.79NPC=2225.63N選用圓錐滾子軸承30207（GB/T297-94）RB=1995.75N14.計算內(nèi)容計算結(jié)果RA=√Req\o(\s\up5(2),\s\do2(Ay))+Req\o(\s\up5(2),\s\do2(Az))=√750.702+353.692=922.23N2.附加軸向力（對滾子軸承S=Fr/2Y）∴SB=RB/2Y=1995.75/3.2=623.67N，SA=RA/2Y=922.23/3.2=288.20Nc.軸向外載荷FA=Fa2=101.33N各軸承的實際軸向力AB=max（SB，F(xiàn)A+SA）=SB=623.67N，AA=（SA，F(xiàn)A-SB）=FA-SB=522.34Ne.計算軸承當量動載由于受較小沖擊查[2]表9-7fd=1.2，又軸I受較小力矩，取fm=1.5∵AB/RB=623.67/1995.75=0.312＜е=0.37，取X=1，Y=0∴PB=fdfm（XRB+YAB）=1.2×1.5×1995.75=3592.35N∵AA/RA=522.34/922.23=0.566＞е=0.37，取X=0.4，Y=1.6∴PA=fdfm（XRA+YAA）=1.8×（0.4×922.23+1.6×522.34）=2168.34N計算軸承壽命又PB＞PA，故按PB計算，查[2]表9-4得ft=1.0∴L10h=106（ftC/P）/60n2=106（51500/3592.35）10/3/（60×303.673）=0.1833×106h，按每年250個工作日，每日一班制工作，即L1=91.65＞L=11年故該軸承滿足壽命要求。3.減速器低速III軸滾動軸承的選擇與壽命計算a.高速軸的軸承只承受一定徑向載荷，選用深溝球軸承，初取d=55㎜，由[1]表4.6-3選用型號為6211，其主要參數(shù)為：d=55㎜，D=100㎜，Cr=33500N，Cr0=25000b.計算軸承D的受力（圖1.5）支反力RB=√Req\o(\s\up5(2),\s\do2(BY))+Req\o(\s\up5(2),\s\do2(Bz))=√1157.522+421.312=1231.81N，RC=√Req\o(\s\up5(2),\s\do2(cy))+Req\o(\s\up5(2),\s\do2(Cz))=√1536.352+559.182=1634.95Nc.軸向外載荷FA=0NRA=922.23NSB=623.67NSA=288.20NFA=101.33NAB=623.67NAA=522.34NPB=3592.35NPA=2168.34N選用深溝球軸承6211（GB/T276-94）RB=1231.81NRC=1634.95NFA=0N15.計算內(nèi)容計算結(jié)果d.計算軸承當量動載由于受較小沖擊查[2]表9-7fd=1.2，又軸I受較小力矩，取fm=1.5∴PB=fdfmRB=1.2×1.5×1231.8=2256.5N∴PC=fdfmRC=1.2×1.5×1×1634.95=2942.91N計算軸承壽命又PB＜PC，故按PC計算，查[2]表9-4得ft=1.0∴L10h=106（ftC/P）/60n3=106（33500/2942.91）10/3/（60×63.829）=27.41×106h，按每年250個工作日，每日一班制工作，即L1=399.45＞L=11年故該軸承滿足壽命要求。七，鍵聯(lián)接的選擇和驗算1.聯(lián)軸器與高速軸軸伸的鍵聯(lián)接采用圓頭普通平鍵（GB1095-79，GB1096-79），由d=30㎜，查[1]表4.5-1得b×h=8×7，因半聯(lián)軸器長為60㎜，故取鍵長L=50㎜，即d=30㎜，h=7㎜，L1=L-b=42㎜，T1=28.38N·m，由輕微沖擊，查[2]表2-10得[σP]=100Mpa∴σP=4T/dhL1=4×29.844/（30×7×42）=12.87＜[σP]=100Mpa故此鍵聯(lián)接強度足夠。 小圓錐齒輪與高速軸I的的鍵聯(lián)接采用圓頭普通平鍵（GB1095-79，GB1096-79），由d=20㎜，查[1]表4.5-1得b×h=6×6，因小圓錐齒輪寬為55㎜，故取鍵長L=42㎜即d=20㎜，h=6㎜，L1=L-b=36㎜，T1=29.844N·m，由輕微沖擊，查[2]表2-10得[σP]=100Mpa∴σP=4T/dhL1=4×29.844/（20×6×36）=27.63＜[σP]=100Mpa故此鍵聯(lián)接強度足夠。大圓錐齒輪與低速軸II的的鍵聯(lián)接PB=2256.5NPC=2942.91NL=50㎜d=30㎜h=7㎜L1=42㎜T1=28.38N·mL=42㎜d=20㎜h=6㎜L1=36㎜T1=29.844N·m16.計算內(nèi)容計算結(jié)果采用圓頭普通平鍵（GB1095-79，GB1096-79），由d=50㎜，查[1]表4.5-1得b×h=14×9，因大圓錐齒輪寬為50㎜，故取鍵長L=44㎜即d=50㎜，h=9㎜，L1=L-b=30㎜，T2=86.955N·m，由輕微沖擊，查[2]表2-10得[σP]=100Mpa∴σP=4T/dhL1=4×86.955/（50×9×30）=25.76＜[σP]=100Mpa故此鍵聯(lián)接強度足夠。大圓柱齒輪與低速軸III的的鍵聯(lián)接采用圓頭普通平鍵（GB1095-79，GB1096-79），由d=60㎜，查[1]表4.5-1得b×h=18×11，因大圓柱齒輪寬為64㎜，故取鍵長L=54㎜，即d=60㎜，h=11㎜，L1=L-b=36㎜，T3=393.197N·m，由輕微沖擊，查[2]表2-10得[σP]=100Mpa∴σP=4T/dhL1=4×393.197/（60×11×36）=66.19＜[σP]=100Mpa故此鍵聯(lián)接強度足夠。5.低速軸III與輸出聯(lián)軸器的鍵聯(lián)接采用圓頭普通平鍵（GB1095-79，GB1096-79），由d=42㎜，查[1]表4.5-1得b×h=12×8，因半聯(lián)軸器長為84㎜，故取鍵長L=72㎜，即d=42㎜，h=8㎜，L1=L