[毕业设计精品]设计用于传动设备用的二级圆柱斜齿轮减速器

课程设计说明书设计题目设计用于传动设备用的二级圆柱斜齿轮减速器机电工程学院04机械设计制造及自动化专业1班级设计者指导老师年月日目录一设计题目二系统中体方案的确定三电动机的选择四传动比的分配五各轴的转速,功率和转矩六齿轮的设计计算七轴的设计计算八轴的校核九轴承的校核十键的选择和校核十一减速器箱体的设计十二参考文献一设计题目设计用于传动设备用的两级圆柱斜齿轮减速器二系统中体方案的确定A1A0A2A3A4A6A7A5A8A10A10A11A5A1A0A10A10A12A9A8A13A16A14A11A5A3A4A18A19A15A17A20AA21为涡轮涡杆减速器A20BA21为二级圆柱圆锥减速器（C）为二级圆柱斜齿轮减速器系统方案总体评价A20AA21A22A23为整体布局最小，传动平稳，而且可以实现较大的传动比，但是由于涡杆传动效率低，功率损失大，很不经济。（B）方案布局比较小，但是圆锥齿轮加工较困难，特别的是大直径，大模数的锥轮，所以一般不采用。A24A25A26A27A22A23A28A20CA21A22A23A29三电动机的选择1卷筒轴的工作转速NWDVPI100060350143801000604368R/MIN工作机的的功率PWWTN9550卷同的工作效率W096T450NM代入数据得PW214KW电动机到运输带的总效率为42342211为联轴器的传动效率，2为轴的传动效率，3为齿轮的传动效率4为卷筒的传动效率。查机械设计课程设计表349901，9802，9703A304096代入G3176G3252得082所以电动机的效率PDWP820142261KW查机械设计课程设计表939G3882G4244电动机G3832G1756为G60132G546，G1421G1351功率为3KW，G2561G4219转速为960R/MIN。G3353传动比的G1491G28211计G3384总的传动比IWMNN684396021982传动比的G1491G2821G303651IG1512III4396五各轴的转速,功率和转矩A31A32A33MIN/9601RNNMPW214KW082PD261KWI219851I39642IMIN/192/12RINNMMIN/6843/223RINNMIN/684334RNNA34A35A3611DPP5821099612KWKWPP4529709805823212KWPP33297098045232232134PP262980990332G2757G2151MNNPT6725960582955095501112229550NPTMN861211924529550MNNPT42509684333295509550333MNNPT11494684326295509550444六齿轮的设计计算对高速级齿轮对（一）G3882G1351齿轮G2347G3832，G2106G1383G1289级，G1003G2424G1923齿数A37A38A39A40A41A42A43A44A45A46A47A38A48A49A41A50A51A52A38A53A54A41A55A56A53A57A37A58A59A37A60A61A62小齿轮G2184G3882用40G38R（G1336G4393），小齿轮G4087G1383为280G43G37G54，大齿轮G1003G242445G1585（G1336G4393），G4087G1383为240G43G37G54，二G4320G3757G104540G43G37G54。4G3882G4244小齿轮的齿数201Z，大齿轮齿数100512ZZG1146G3882G2532G3880G204014。（二）G799齿G2635G2052G1160G2972G1383设计由A63A64设计计G3384G1636G3252109G68G2089G3835计G338431112HEHDTTZZTKDMIN/9601RN2N192R/MINMIN/6843MIN/684343RNRNKWPKWPKWPKWP2623324525824321MNTMNTMNTMNT11494425098612167254321201Z1002Z1G277G3058G1351G1636G3252G2717的G1618计G3384数G4372G111G12G3275G3882G4219G1760系数61TKG112G12由A65A66G3533103G3882G30364332HZG113G12由A65A66G35331026查得890,75021AA64189075021AA（4）计G3384小齿轮转速由G2957G2635的计G3384可G4361MNT67251（5）查A65A66表10G26得1D（6）查A65A67106A68A69A66A70A71A72A73A74A75A76A77218189MPAZE（G26G12由G35331021G71G799齿G2635G4087G1383查得小齿轮的G2052G1160G2850G2328G2972G1383G1918G3755MPAHLIN6001G290大齿轮的G2052G1160G2850G2328G2972G1383G1918G3755MPAH5502LIMG118G12由G2045G1003G32521013计G3384G4075G2383G3894G1836G1201数811102944863008119606060HJLNN881210658915/10294485/NN（9）由G2045G1003G35331019查得G2052G1160G2850G2328G3280G2657系数9201HNK，9602HNKG1110G12计G3384G2052G1160G2850G2328G3864用G4075G2383G3036失效G1568率为1G8，G797G3046系数G541，由G2045G1003G1636G32521012得MPASKHHNH5526009201LIM11MPASKHHNH5285509602LIM22MPAHHH5402/5285522/112计G3384（1）计G3384G3275G3384小齿轮G1491G1383圆直径TD1，由计G3384G1636G3252得641MPAHLIN6001MPAH5502LIM811029448N821065891NMPAH5521MPAH5282MPAH540MMDT29355408189433256641110567261232412计算圆周速度SMSMNDVT/771/100060960293510006011PIPI（3）计算齿宽B及模数NTMMMDBTD2935293511MMZDMTNT7120/9702935/COS11MMMHNT853711252252179853/2935/HB（4）计算纵向重合度58612502013180TAN31801ZD（5）计算载荷系数K已知使用系数1AK。根据SMV/771A788A79A80A81A78A82A83A84A85108A86A87A88A89A90A91A92051VKA78A82A83A84A93A86A87HKA94A95A96A97A98A9945129351031011601180151103106011801513322BKDDH查教材表1013得331FK查教材表103得41FHKK，所以载荷系数132451410511FFVAKKKKK（6）按实际载荷系数校正所得的分度圆直径由教材（1010A）得823861132293511TTKKDD（7）计算模数88120/9708238/14COS11ZDMN（三）按齿根弯曲强度设计MMDT29351SMV/771MMB2935MMMNT71MMH853179/HB5861451HK132K82381D32121COS2FSFDNYYZYKTM1确定计算参数（1）计算载荷系数951331410511FFVAKKKKK（2）根据纵向重合度5861A100A101A102A1031028A104A105A106A107A108A109A110A111A112880YA1133A114A115A116A117A118A119A1125210914COS100COS912114COS20COS33223311ZZZZVV（4）查取齿形系数由教材表105查得1722,744221FAFAYY（5）查取应力校正系数由教材表105查得7981,565121SASAYY（6）由教材图1020查得小齿轮的弯曲疲劳强度极限MPAFE5001，大齿轮为MPAFE3802由教材图1018查得弯曲疲劳寿命系数8601FNK，902FNK；计算弯曲疲劳许用应力取弯曲疲劳安全系数S14,由教材式1012得MPAMPASKFEFNF1430741500860111MPAMPASKFEFNF292444138090222（7）计算大小齿轮的FSAFAYY0147901430765617442111FSAFAYY881NM951K52109912121VVZZMPAF143071MPAF2924420159902924479811722222FSAFAYY大齿轮数值大2设计计算MMMN32101599064120114COS88010567295123224对比计算结果，由齿面接触疲劳强度计算的模数M大于由齿根弯曲疲劳强度计算的模数，由于齿轮模数M的大小主要取决于弯曲强度所决定的承载能力，而齿面接触疲劳强度所决定的承载能力，仅与齿轮直径MZ有关，可取弯曲强度算得摸数15MM可满足弯曲强度，按接触强度得的分度圆直径MMD82381，算出小齿轮齿数11255114COS8238COS11NMDZ取251Z12525512ZZ3几何尺寸计算计算中心距MMMZZAN9811514COS25112525COS221将中心距圆整为116MM（2）按圆整后的中心距修正螺旋角216141625112525ARCCOS2ARCCOSAMZZN因值改变的不多，故参数HZK,等不必修正。（3）计算大小齿轮的分度圆直径MMMZDMMMZDNN1193614COS51125COS6638614COS5125COS2211（4）计算齿轮宽度MMDBD6638663811圆整后取MMBMMB45,4012014790111FSAFAYY015990222FSAFAYYMMMN51251Z1252ZMMA116MMA116614MMDMMD1193663821计算第二对齿轮（一）选定齿轮类型，精度等级，材料及齿数A120A121A122A123A124A125A126A127A128A129A130A121A131A132A124A133A134A135A121A136A137A124A138A139A136A140A120A141A142A120A143A144A145小齿轮均选用40CR（调质），小齿轮硬度为280HBS，大齿轮材料45钢（调质），硬度为240HBS，二者相差40HBS。4选择小齿轮的齿数221Z，大齿轮齿数71963964222Z，取972Z，初选螺旋角14（二）按齿面接触强度设计由A139A136设计计算公式109A进行计算31112HEHDTTZZTKD1确定公式内的各计算数值（1）试选载荷系数61TK（2）由A139A136图103选取4332HZ（3）由A139A136图1026查得880,77021AA65188077021AA（4）计算小齿轮转速由前面的计算可知MNT861211（5）查A139A136表107得1D（6）查A139A140A120A141A142A146A147A148A136A137A149A150A151A152A153A154A155218189MPAZE（7由图1021D按齿面硬度查得小齿轮的接触疲劳强度极限MPAHLIN6001；大齿轮的接触疲劳强度极限MPAH5502LIM8由教材式1013计算应力循环次数811106589163008111926060HJLNN781210773633963/10658913964/NNMMBMMB454012221Z972Z651MPAHLIN6001MPAH5502LIM811065891N（9）由教材图1019查得接触疲劳寿命系数，9601HNK，0712HNK10计算接触疲劳许用应力取失效概率为1，安全系数S1，由教材公式1012得MPASKHHNH5766009601LIM11MPASKHHNH55885500712LIM22MPAHHH255822/55885762/112计算（1）计算试算小齿轮分度圆直径TD1，由计算公式得MMDT72562558281894332396139656411102186161232512计算圆周速度SMSMNDVT/570/100060192725610006011PIPI（3）计算齿宽B及模数NTMMMDBTD7256725611MMZDMTNT50222/9707256/COS11MMMHNT625550225225208106255/7256/HB（4）计算纵向重合度7412502213180TAN31801ZD（5）计算载荷系数K已知G3248用系数1AK。G1620G2156SMV/570A1568A157A158A159A160由教材图108查得G1358载荷系数70VK，由教材表查得HK的计算公式G289721077363NMPAH5761MPAH55882MPAH25582MMDT72561SMV/570MMB7356MMMNT502MMH62550810/HB74146172561031011601180151103106011801513322BKDDH查教材表1013得361FK查教材表103得41FHKK，所以载荷系数43146141701FFVAKKKKK（6）按实际载荷系数校正所得的分度圆直径由教材（1010A）得MMKKDDTT64546141725611（7）计算模数41222/9707256/14COS11ZDMN（三）按齿根弯曲强度设计32121COS2FSFDNYYZYKTM1确定计算参数（1）计算载荷系数33136141701FFVAKKKKK（2）根据纵向重合度741由教材图1028查得螺旋角影响系数880YA1613A162A163A164A165A166A167A1682210614COS97COS082414COS22COS33223311ZZZZVV（4）查取齿形系数由教材表105查得1712,647221FAFAYY（5）查取应力校正系数由教材表105查得7971,581121SASAYY（6）由教材图1020查得小齿轮的弯曲疲劳强度极限MPAFE5001，大齿轮为MPAFE3802由教材图1018查得弯曲疲劳寿命系数901FNK，461HK431KMMD64541412NM331K22106082421VVZZ9402FNK；计算弯曲疲劳许用应力取弯曲疲劳安全系数S14,由教材式1012得MPAMPASKFEFNF433214150090111MPAMPASKFEFNF1425541380940222（7）计算大小齿轮的FSAFAYY0130204332158116472111FSAFAYY0153901425579711712222FSAFAYY大齿轮数值大2设计计算MMMN73101539065122114COS880102186133123225对比计算结果，由齿面接触疲劳强度计算的模数M大于由齿根弯曲疲劳强度计算的模数，由于齿轮模数M的大小主要取决于弯曲强度所决定的承载能力，而齿面接触疲劳强度所决定的承载能力，仅与齿轮直径MZ有关，可取弯曲强度算得摸数20MM可满足弯曲强度，按接触强度得的分度圆直径MMD64541，算出小齿轮齿数5126214COS6454COS11NMDZ取271Z11939642712ZZ3几何尺寸计算计算中心距MMMZZAN5715014COS2211927COS221将中心距圆整为151MM（2）按圆整后的中心距修正螺旋角MPAF433211MPAF142552013020111FSAFAYY015390222FSAFAYYMMMN2271Z1192ZMMA1512181415125111927ARCCOS2ARCCOSAMZZN因值改变的不G1407，G1667参数HZK,G1289不G929修正G100（3）计算大小齿轮的分度圆直径MMMZDMMMZDNN1246814COS2119COS8455814COS227COS2211（4）计算齿轮G2266度MMDBD8455845511圆整后取MMBMMB65,6012G3954算G1166G1358比04222527125119I5230100042298210422I所以满足设计要G3024G100七轴的设计计算（一）高速轴的设计计算1确定G4416的G4523小直径G3733按教材式（152）G1146G996G1657算G4416的G4523小直径G100G3882G4416的材G2424为40G38G85G1336G4393G1161G2360G100根据教材表153，取1060A，于G3262得MMNPAD741496058210633110MIN，由于G2199G2420G4002G1617G1999G1026，所以MMD771507017414MING4416的G4523小直径G3745G3062G3262安G4461G2387G4416G2934G1161G4416的直径G100为G2420G3248G4416的直径G1764G2387G4416G2934的G2244径G3757G3265应，G1667G3859G3517G3240G3882G2387G4416G2934的G3832G1756G100G2387G4416G2934的计算G4455G21511TKTACA，查教材表141取31AK，G4123NT41105672G1245G3110数据得MMNTCA103434查G119G1903G3808设计G2235G1105设计G120表G2821（G42G37G18G5543231G2884），G3882用G55G474G3832G1264G3839G4440G3783G2387G4416G2934G100G2387G4416G2934的G2244径G7122MM,所以814MMDMMD1246845521MMBMMB656012MMNTCA103434MMD22MIN2G4416的G1903G1650设计（1）根据G4416向定G3626的要G3024确定G4416G3176G1618G1389直径G1764G1065度1）为G2420满足G2387G4416G2934的G4416向定G3626要G3024，G422112G1389的G4119G936G1958G2420G4002G1617G4416G3466，所以MMDD22MIN122）G1146G996G3882取G4416承，因G3517G3240G3283G1278径向力G1764G4416向力，G1667G3882用圆G4467G1711G4496G4416承，根据G4416的结G1650G1764G4523小G4416的直径大小查G119G1903G3808设计G2235G1105设计G120表G2816（G42G37G18G552G2871G28G284）G3882用30205G3832G4416承MMMMMMTDD25165225所以，MMD2523，根据G4416承的G4119G1386G1008用G4416G1978定G3626，G1206表中可G4361MMD3034，45G1390的直径为齿轮的齿G1348圆直径，所以MMD664145，MMDDMMDD25,3023673456G100G854G2387G4416G2934与G4416G2821合的G6431G2244G1065度MML381，为G2420G876G4355G4416G1386G1267G3041G4378G3906G4221G854G2387G4416G2934G3176而不G3906G4221G4416的G1386面G3176，所以G1065度应取G1387G3796，G3733取MML361G100G4416承的G1386G1570的G4505G2266为25MM,取G1386G1570的G3571G1386面与G854G2387G4416G2934的距G2358为25MM，所以12G1389G3176的G4416G3466G1065MML5025252，所以MML882365012G4221确定G4416承的G3626G4386G3240应距G2358G3761G3480G2717G931S8MM，取齿轮距G2358G3761G3480G2717G931A12MMG100所以，2524282251623LMM取24MM，34L可由中G1975G4416算出G2303MML8321126521234，MMBL45145，G4416G1978MMD22MINMMDMMDMMDMMDMMDMMD25306641302522675645342312G4416承的G3832G1756为30205MMLMMLMMLMML4583248845342312的G1594度DH070，G4416G1836的G2266度HB41，所以取56G13891的G1065度为MML1056，所以2526281012251667L，取26MMG100（二）中间轴的设计计算1确定G4416的G4523小直径G3733按教材式（152）G1146G996G1657算G4416的G4523小直径G100G3882G4416的材G2424为40G38G85G1336G4393G1161G2360G100根据教材表153，取1060A，于G3262得MMNPAD772419245210633110MIN，由于G2199G2420G4002G1617G1999G1026，所以MMD52607017724MIN2G4416的G1903G1650设计A1691A170A171A172A173A174A175A176因为G4416的G4523小G4416与G4416承G3757G2821合，所以应G1566G3733确定G4416承的G3832G1756G1206而确定G4416的G4523小值，因G3517G3240G3283G1278径向力G1764G4416向力，G1667G3882用圆G4467G1711G4496G4416承G100查G119G1903G3808设计G2235G1105设计G120表G2816（G42G37G18G552G2871G28G284），根据G3176面计算的MMD526MIN，G3882G4244G4416承的G3832G1756为30206，G2915尺寸为MMMMMMTDD25176230所以，MMDD306712G4416G1978G1594度12070DH所以23G1389的直径MMHD3530223，MMDD352356，34G1389的直接G1927为齿轮的齿G1348圆直径MMD845934，45G1389的G4416G1978G1594MMH45235070，所以MMDHD4025645G100A1692A170A177A178A171A172A173A179A180G3733确定23G1389的G1065度MMLMML26106756G4416承的G3832G1756为30206MMDMMDMMDMMDMMDMMD30354084593530675645342312G4416G1836的G2266度HB41，取G69为10MMG1927MML1023G100确定12G1389的G1065度因为安G4461G4416承应距G2358G3761G3480G2717G931为8MM，齿轮距G2358G3761G3480G2717G931的距G2358为16MM，所以MML252710128251712，取MML2712G100确定34的G1065度34的G1065度G1289于齿轮的G2266度，所以MMBL65134G100确定45G1389的G1065度G4416G1836的G2266度HB41，取G69为10MMG1927MML1045G100确定56G1389的G1065度56的G1065度G4176G903应G1566G1289于齿轮的G2266度G37，G1260为G2420定G3626G4532用G1566G1389的G4416应小于齿G2266G37，MML3734056确定67G1389的G1065度75432/40453128251767L取MML4767三输出轴的设计计算1确定G4416的G4523小直径G3733按教材式（152）G1146G996G1657算G4416的G4523小直径G100G3882G4416的材G2424为45G1585，G1336G4393G1161G2360G100根据教材表153，取105，于G3262得MMNPAD139684326210533110MIN，由于G2199G2420G2406G1617G1999G1026，所以MMD7431201139MING4416的G4523小直径G3745G3062G3262安G4461G2387G4416G2934G1161G4416的直径G100为G2420G3248G4416的直径G1764G2387G4416G2934的G2244径G3757G3265应，G1667G3859G3517G3240G3882G2387G4416G2934的G3832G1756G100G2387G4416G2934的计算G4455G21511TKTACA，查教材表141取51AK，G4123NT511009425G1245G3110数据得MMNTCA10641375查G119G1903G3808设计G2235G1105设计G120表G2821（G42G37G18G5543231G2884），G3882用G43G474G3832G1264G3839G4440G3783G2387G4416G2934G100G2387G4416G2934的G2244径G7145MM,所以MMD45MIN2G4416的G1903G1650设计MML2712MML1023MML6534MML1045MML3756MML4367MMD45MIN（1）根据G4416向定G3626的要G3024确定G4416G3176G1618G1389直径G1764G1065度1）为G2420满足G2387G4416G2934的G4416向定G3626要G3024，G422167G1389的左G936G1958G2420G4002G1617G4416G3466，所以MMDD45MIN672）G1146G996G3882取G4416承，因G3517G3240G3283G1278径向力G1764G4416向力，G1667G3882用圆G4467G1711G4496G4416承，根据G4416的结G1650G1764G4523小G4416的直径大小查G119G1903G3808设计G2235G1105设计G120表G2816（G42G37G18G552G2871G28G284）G3882用30210G3832G4416承MMMMMMTDD75219050所以，MMD5012，根据G4416承的G4119G1386G1008用G4416G1978定G3626，G1206表中可G4361MMD5523，G4416G1978的G1594度853070DH取4MM，所以MMD6334，MMDDMMDD50,5512562345G100G854G2387G4416G2934与G4416G2821合的G6431G2244G1065度MML847，为G2420G876G4355G4416G1386G1267G3041G4378G3906G4221G854G2387G4416G2934G3176而不G3906G4221G4416的G1386面G3176，所以G1065度应取G1387G3796，G3733取MML821G100G4416承的G1386G1570的G4505G2266为20MM,取G1386G1570的G3571G1386面与G854G2387G4416G2934的距G2358为30MM，所以12G1389G3176的G4416G3466G1065MML5030206，所以MML135230208267G4221确定G4416承的G3626G4386G3240应距G2358G3761G3480G2717G931S8MM，取齿轮距G2358G3761G3480G2717G931A16MMG10023G1389的G1065度G4176G903G1289于齿轮的G2266，G1260为G2420齿轮能够G4416向定G3626应G1387G4002G3796，所以MML5736023，所以MML25472/6065128752112取MML4712G4416G1836的G2266HB41取G6911MMG1927MML1034MMD5012MMD5523MMD6334MMDMMD50555645MMD4567G4416承的G3832G1756为30210MML13567MML4712MML5723MML103445L可由中G1975G4416确定MML551022/40452/606512401045MML7529228752156取MML3056八轴的校核（一）输入轴的校核NFFNFFNDTFTANTRT331TAN498COSTAN,1328211111111画G4416的空G1975G3283力图将齿轮所G3283载荷简化为集中力，并通过轮G6431中截面G4532用于G4416G3176G100G4416的支点反力也简化为集中力通过载荷中心G4532用于G4416G3176；2G4532垂直平面G3283力图G1764水平平面G3283力图G3024出G4532用于G4416G3176的载荷G100并确定可能的危险截面G100将计算出的危险截面G1161的MMMVH,的值列G3110下表MML5545MML3056NFNFNFART3314981328111A181A182A183A184A185HA186A187A185VA188A189A190FNFNHNFNH93739121NFNVNFNV32017821A191A192MMMNMH51184MMNMMMNMVV175602334021A193A194A192MMNMMMNM541411756251184562582334051184222221A195A192MMNT256703按弯G2151合成应力校核G4416的强度已G4361材G2424为40G38G85G1585G1336G4393，由教材表151查得MPA701，由已G4361条件，对G4416G3176承G3283G4523大弯G2151G1764扭G2151的截面的强度进行校核G100根据教材式155以G3176表中的数据，并取60G4416的计算应力MPAMPAWTMCA7023149134102567060562583222221结论按弯G2151合成应力校核G4416的强度，G4416的强度足够G100（二）中间轴的校核NFFNFFNFFAARRTT331498,1328121212NFFNFNDTFTANRT1088TAN1638COSTAN,436523331画G4416的空G1975G3283力图将齿轮所G3283载荷简化为集中力，并通过轮G6431中截面G4532用于G4416G3176G100G4416的支点反力也简化为集中力通过载荷中心G4532用于G4416G3176；2G4532垂直平面G3283力图G1764水平平面G3283力图G3024出G4532用于G4416G3176的载荷G100并确定可能的危险截面G100NFNFNFART3314981328222NFNFNFART108816384365333A196A197将计算出的危险截面G1161的MMMVH,的值列G3110下表A198A199A200A201A202HA203A204A202VA205A206A207FNFNHNFNH2458353223NFNVNFNV3134123A208A209MMMNMMMNMHH13552021070823MMNMMMNMVV322305265323A210A211A209MMNMMMNM1398403223013552021753052653210708222223A212A209MMNT1218603按弯G2151合成应力校核G4416的强度已G4361材G2424为40G38G85G1585G1336G4393，由教材表151查得MPA701，由已G4361条件，对G4416G3176承G3283G4523大弯G2151G1764扭G2151的截面的强度进行校核G100根据教材式155以G3176表中的数据，并取60MPAMPAWTMCA7096138455101218606013984032222213MPAMPAWTMCA7013935101218606013984032222213结论按弯G2151合成应力校核G4416的强度，G4416的强度足够（三）输出轴的校核NFFNFFNFFAARRTT10881638,43653434341画G4416的空G1975G3283力图将齿轮所G3283载荷简化为集中力，并通过轮G6431中截面G4532用于G4416G3176G100G4416的支点反力也简化为集中力通过载荷中心G4532用于G4416G3176；2G4532垂直平面G3283力图G1764水平平面G3283力图G3024出G4532用于G4416G3176的载荷G100并确定可能的危险截面G100将计算出的危险截面G1161的MMMVH,的值列G3110下表NFNFNFART108816384365444A213A214A215A216A217HA218A219A217VA220A221A222FNFNHNFNH1614275121NFNVNFNV113175121A223A224MMMNMH224650MMNMMMNMVV1206001326321A225A226A224MMNMMMNM22465012060018953019038013263189530222221A227A224MMNT5094203按弯G2151合成应力校核G4416的强度已G4361材G2424为45G1585G1336G4393，由教材表151查得MPA601，由已G4361条件，对G4416G3176承G3283G4523大弯G2151G1764扭G2151的截面的强度进行校核G100根据教材式155以G3176表中的数据，并取60MPAMPAWTMCA608225510509420602246503222221结论按弯G2151合成应力校核G4416的强度，G4416的强度足够九轴承的校核G4416承的预期计算寿命HLH4800830021输入轴上轴承的校核（1）G3024G2406G1617G4416承G3283G1278的径向载荷由G4416的校核过G1105可G4361NFAE331NFNFNFNFNVNVNHNH320,178937,3912121所以NFFFNVNHR64291783912221121NFFFNVNHR19903209372222222HLH4800NFR64291NFR19902（2）计算G4416承的G4416向力查G119G1903G3808设计G2235G1105设计G120表G2816（G42G37G18G552G2871G28G284）得30205G3832G1756G4416承NCYER32200,61,370所以NYFFRD251346126429211NYFFRD413096121990222NFFFFNFFFFAEDDADAEDA41309,MAX4164041309331,MAX122211（3）G3024G4416承的G1358载荷EFFEFFRARA3101990413094916429416402211查教材表135得对G4416承161,4011YX对G4416承20,122YX查教材表136取冲击载荷因数21PF（四）计算G4416的寿命NFYFXFPARP9142341640616429402111111NFYFXFPAR以HHLHPCNL5950169142332200960601060103106161HHLHPCNL123084712118832200960601060103106162所以G4416承满足寿命要G3024G1002中间轴的校核（1）G3024G2406G1617G4416承G3283G1278的径向载荷由G4416的校核过G1105可G4361NFAE7573311088NFD251341NFD413092NFNFAA413094164021NP914231NP1211882HLH5950161HLH12308472NFNFNFNFNVNVNHNH2458,323531,3412121所以NFFFNVNHR9325232353412221121NFFFNVNHR224582458312222222（2）计算G4416承的G4416向力查G119G1903G3808设计G2235G1105设计G120表G2816（G42G37G18G552G2871G28G284）得30206G3832G1756G4416承NCYER41200,61,370所以NYFFRD5101661293252211NYFFRD276861222458222NFFFFNFFFFAEDDADAEDA2768,MAX215252768757,MAX122211（3）G3024G4416承的G1358载荷EFFEFFRARA31022458276847093252215252211查教材表135得对G4416承161,4011YX对G4416承20,122YX查教材表136取冲击载荷因数21PF（四）计算G4416的寿命NFYFXFPARP84489215256193252402111111NFYFXFPARP829492245812122222所以HHLHPCNL1393238448941200192601060103106161HHLHPCNL5645838294941200192601060103106162所以G4416承满足寿命要G3024G100NFR932521NFR224582NFD510161NFD27682NFNFAA27682152521NP844891NP829492HLH1393231HLH5645832（三）输出轴上轴承的校核（1）求两个轴承受到的径向载荷由轴的校核过程可知NFAE1088NFNFNFNFNVNVNHNH113,17511614,27512121所以NFFFNVNHR3261161427512221121NFFFNVNHR161811317512222222（2）计算轴承的轴向力查机械设计课程设计表916（GB/T2971994）得30210型号轴承NCYER72200,41,420所以NYFFRD611644123261211NYFFRD95774121618222NFFFFNFFFFAEDDADAEDA9577,MAX9166595771088,MAX122211（3）求轴承的动载荷EFFEFFRARA360161895775103261916652211查教材表135得对轴承161,4011YX对轴承20,122YX查教材表136取冲击载荷因数21PF所以NFYFXFPARP8475391665413261402111111NFYFXFPARP61941161812122222（四）计算轴的寿命NFR32611NFR16182NFD611641NFD95772NFNFAA95779166521NP847531NP619412HHLHPCNL325765584753722006843601060103106161HHLHPCNL647022961941722006843601060103106162所以轴承满足寿命要求。十键的选择和校核1输入轴上联轴器处的键（1）确定键的类型和尺寸由于是静连接，选用A型普通平键。由机械设计课程设计表914（GB/T10951979），查得当轴径MMD22时键取为66HB。参照半联轴器与轴配合的毂长MML36和普通平键的长度系列，取键长MML28。（2）强度验算