二級圓錐齒輪減速器設(shè)計(jì)說明書

word文檔可自由復(fù)制編輯一?設(shè)計(jì)任務(wù)書····················································································2二?電機(jī)的選擇計(jì)算1.擇電機(jī)的轉(zhuǎn)速·················································································22.工作機(jī)的有效功率···········································································23.選擇電動機(jī)的型號···········································································3三?運(yùn)動和動力參數(shù)的計(jì)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(shè)計(jì)計(jì)算1.閉式直齒輪圓錐齒輪傳動的設(shè)計(jì)計(jì)算·················································42.閉式直齒輪圓柱齒輪傳動的設(shè)計(jì)計(jì)算·················································6五?軸的設(shè)計(jì)計(jì)算減速器高速軸I的設(shè)計(jì)·······························································9減速器低速軸II的設(shè)計(jì)····························································113.減速器低速軸III的設(shè)計(jì)··································································14六?滾動軸承的選擇與壽命計(jì)算1.減速器高速I軸滾動軸承的選擇與壽命計(jì)算·········································162.減速器低速II軸滾動軸承的選擇與壽命計(jì)算········································173.減速器低速III軸滾動軸承的選擇與壽命計(jì)算·····································18七?鍵聯(lián)接的選擇和驗(yàn)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(jì)算1.減速器的熱平衡計(jì)算·······································································212.潤滑油的選擇···············································································22九?參考文獻(xiàn)···················································································23計(jì)算內(nèi)容計(jì)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(jī)的輸出功率Pr=Pw/η=2.4/0.808=3kw選擇電動機(jī)的型號查參考文獻(xiàn)[1]表4-12.2得表1.1方案號電機(jī)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(jī)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(jī)。動和動力參數(shù)的計(jì)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(shí)際總傳動比i實(shí)=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(biāo)號均已在圖1.1中標(biāo)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(jī)Y132S-6p=3kwn=960r/mini=15.072i12=3.762i23=4n0=960r/minn1=960r/minn2=303.67r/minn3=63.829r/minn4=63.829r/min3.計(jì)算內(nèi)容計(jì)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(shè)計(jì)計(jì)算1.閉式直齒輪圓錐齒輪傳動的設(shè)計(jì)計(jì)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(xiàn)[2]（以下簡稱[2]）式（5—33），計(jì)算應(yīng)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(jì)算取[σH]=[σH]2=533.6Mpac．按齒面接觸強(qiáng)度設(shè)計(jì)小齒輪大端模數(shù)（由于小齒輪更容易失效故按小齒輪設(shè)計(jì)）：取齒數(shù)Z1=21，則Z2=Z1i12=3.762×32=79，取Z2=79∵實(shí)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(dāng)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(jì)算內(nèi)容計(jì)算結(jié)果此資料來自舉哥設(shè)計(jì)工作室，淘寶網(wǎng)搜索店鋪舉哥設(shè)計(jì)工作室進(jìn)入店鋪搜索二級圓錐齒輪減速器可獲得此設(shè)計(jì)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(jì)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(jì)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(yàn)算齒面接觸疲勞強(qiáng)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(jì)算內(nèi)容計(jì)算結(jié)果σH=470.899﹤[σH]=533.6Mpa∴小齒輪滿足接觸疲勞強(qiáng)度，且大齒輪比小齒輪接觸強(qiáng)度高，故齒輪滿足接觸強(qiáng)度條件f．齒輪彎曲疲勞強(qiáng)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(jì)算許用彎曲應(yīng)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(jì)算齒跟彎曲應(yīng)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(qiáng)度2.閉式直齒輪圓柱齒輪傳動的設(shè)計(jì)計(jì)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(xiàn)[2]（以下簡稱[2]）式（5—33），計(jì)算應(yīng)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(jì)算內(nèi)容計(jì)算結(jié)果[σH]2=σHP2ZN2ZX2ZWZLVR/SHmin=560×1.16×0.92=597.63MPa∵[σH]1>[σH]2，∴計(jì)算取[σH]=[σH]2=560.28Mpac.按齒面接觸強(qiáng)度計(jì)算中心距（由于小齒輪更容易失效故按小齒輪設(shè)計(jì)）：∵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(jì)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(shè)計(jì)：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(shí)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(jì)算內(nèi)容計(jì)算結(jié)果e.驗(yàn)算齒面接觸疲勞強(qiáng)度按電機(jī)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(qiáng)度，且大齒輪比小齒輪接觸強(qiáng)度高，故齒輪滿足接觸強(qiáng)度條件f．齒輪彎曲疲勞強(qiáng)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(jì)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(jì)算許用彎曲應(yīng)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(jì)算內(nèi)容計(jì)算結(jié)果∵[σF1]﹥[σF2]，∴[σF]=[σF2]=300Mpa由[2]式5-24計(jì)算齒跟彎曲應(yīng)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(qiáng)度五，軸的設(shè)計(jì)計(jì)算減速器高速軸I的設(shè)計(jì)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(xiàn)[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(jī)伸軸用聯(lián)軸器聯(lián)接。并考慮用柱銷聯(lián)軸器，因?yàn)殡姍C(jī)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(jì)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(jì)算內(nèi)容計(jì)算結(jié)果∴垂直面內(nèi)D點(diǎn)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(diǎn)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(jì)算扭矩：T=T1=29.545N·mI.校核高速軸I：根據(jù)參考文獻(xiàn)[3]第三強(qiáng)度理論進(jìn)行校核：由圖1.2可知，D點(diǎn)彎矩最大，故先驗(yàn)算D處的強(qiáng)度，∵M(jìn)D＜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(qiáng)度要求。2.減速器低速軸II的設(shè)計(jì)選擇材料：因?yàn)橹饼X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(yīng)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(jì)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(jì)算內(nèi)容計(jì)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(diǎn)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(diǎn)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(diǎn)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(diǎn)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(jì)算內(nèi)容計(jì)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(jì)算扭矩：T=T2=86.955N·mg.校核低速軸II強(qiáng)度，由參考文獻(xiàn)[3]第三強(qiáng)度理論進(jìn)行校核：由圖1.3可知，D點(diǎn)彎矩最大，故先驗(yàn)算D處的強(qiáng)度，∵M(jìn)D＞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(diǎn)軸徑較小故也應(yīng)進(jìn)行校核：∵M(jìn)C＞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(qiáng)度要求3.減速器低速軸III的設(shè)計(jì)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(jì)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(diǎn)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(jì)算內(nèi)容計(jì)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(diǎn)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(jì)算扭矩：T=T3=393.197N·mg.校核低速軸III：根據(jù)參考文獻(xiàn)[3]第三強(qiáng)度理論校核：由圖1.2可知，D點(diǎn)彎矩最大，故先驗(yàn)算D處的強(qiáng)度，∵M(jìn)D＞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(qiáng)度要求。六，滾動軸承的選擇與壽命計(jì)算1.減速器高速I軸滾動軸承的選擇與壽命計(jì)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(dāng)A/R≤е時，X=1，Y=0；當(dāng)A/RPAGE\#"'頁：'#'

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'"b.計(jì)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(jì)算內(nèi)容計(jì)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(shí)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(jì)算軸承當(dāng)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(jì)算軸承壽命又PB＜PC，故按PC計(jì)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(jì)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(dāng)A/R≤е時，X=1，Y=0；當(dāng)A/RPAGE\#"'頁：'#'

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'"b.計(jì)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(jì)算內(nèi)容計(jì)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(shí)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(jì)算軸承當(dāng)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(jì)算軸承壽命又PB＞PA，故按PB計(jì)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(jì)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(jì)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(jì)算內(nèi)容計(jì)算結(jié)果d.計(jì)算軸承當(dāng)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(jì)算軸承壽命又PB＜PC，故按PC計(jì)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(yàn)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(qiáng)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(qiáng)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(jì)算內(nèi)容計(jì)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(qiáng)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(qiáng)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