[车辆交通类论文精品]奥迪100前驱动桥的设计

1汽车设计课程设计计算说明书设计题目奥迪100前驱动桥的设计2CONTENTS设计任务书3主减速器的设计计算4差速器的设计计算12驱动桥传动装置的设计计算15设计小结18参考资料193汽车设计课程设计任务书1）、题目奥迪100前桥部分设计验算与校核2）、设计内容及要求1主减速器部分包括主减速器齿轮的受载情况；锥齿轮主要参数选择；主减速器强度计算；齿轮的弯曲强度、接触强度计算。2差速器齿轮的主要参数；差速器齿轮强度的校核；行星齿轮齿数和半轴齿轮齿数的确定。3半轴部分强度计算当受最大牵引力时的强度；制动时强度计算。3）、主要技术参数轴距L2687MM发动机最大功率60KW/5500R/MIN最大扭矩140MN/3300R/MIN140I631I总重AM18604）、要上交材料AUTOCAD装配图一张A3纸打印零件图1张手绘4号或3号图纸计算设计说明书1份打印AUTOCAD装配图电子文档1份5）、参考文献1王望予等汽车设计M第3版,北京机械工G1006G1998版G12050,20002G19484G4490G10802等汽车G7512G17908M北京机械工G1006G1998版G12050,20003G1134G13447,G14499G1818G21666奥迪100G17747车零部件G11458G5417MG990G9035G990G9035G1144G17902大G4410G1998版G12050,19944G14005G1134G5208等G17747车与G17743G3423G2842G11004汽车M北京G1166G8677G1144G17902G1998版G12050,19935G2028G5811G1461G13546G14891G3290锥齿轮与G2464曲G19766齿轮G1268动M北京G1166G8677G1144G17902G1998版G12050G71219804设计内容结果主减速器G3534G7424参数选择与设计计算主减速G8616I0、G20549动桥的G12175G3332G19400G19565和计算载G14667G712G7171主减速器设计的G2419G3999数G6466G712G6117G1216G7693G6466G159321G5483G2052的数G6466G1038主减速G8616I0G324G171G712G20549动桥G12175G3332G19400G19565G1038G75G32144MM。1G709主减速齿轮计算载G14667的确定G7696G18336G7874齿制锥齿轮计算载G14667G7389G1209G991G989G12193确定G7053G8873G68G17G6365发动机最大G17728矩和最G1314档G1268动G8616确定G1186动锥齿轮的计算G17728矩G55G70G72MNNIIIKTKTFEDCE222031/1901463111701/01MAXG5347G1025DKG29G10479接G12175G2524器G1147G10995的动载G13007数G712G11013G5627G14033G13007数JF确定MAX001160195AJEMGFT当161950MAXEATGM时G1866G1025G712AMG1038汽车G9397载G17148G18339AMG7291G27G250G46G741691201708079186019501950MAXETGMAQ10IDKF则取MAXETG252G252发动机最大G17728矩G712G11013G5062G11705G5483MAXETG321G260MNG30G78G252G252G9094力G2476矩器G2476矩G13007数G712G78G321G301IG252G252G2476速器一档G1268动G8616G7121IG323G17G25FIG252G252分动器G1268动G8616G712FIG321G300IG252G252主减速器G1268动G8616G7120IG324G171G252G252发动机G2052G987G2533G1268动轴G1055G19400的G1268动G6940率G712G247490；NG252G252G20549动桥数G11458G712NG321G30G69G17G6365G20549动轮打G9381G17728矩确定G1186动锥齿轮的计算G17728矩CSTMNIRMGTMMRCS35326995013084085031911422TCE1901841NMTCS289946NMMIN,1901841NM5G5347G1025G7122GG252G252汽车G9397载G10378G5589G991一G1022G20549动器G990的G19757载G14667G49G15算G54832GG321G27G250/G21G13G28G17G27G32G28114G49G302MG252G252汽车最大G2164速度时G2530轴负G14667G17728移G13007数G712G24742MG321G173G30FG252G252轮胎与路G19766附着G13007数G712查资料G5483FG320G17G275；RRG252G252车轮滚动半径G712查G5483RRG320G1730G274MG30MIG252G252主减速器G1186动齿轮G2052车轮G1055G19400G1268动G8616G712MIG321G30MG252G252主减速器主动齿轮G2052车轮G1055G19400G1268动G6940率G712G2474MG320G17G285；G70G17G6365汽车日常行驶平均G17728矩确定G1186动锥齿轮计算G17728矩TRCFMMFRTING5347G1025G712TFG252G252汽车日常行驶平均牵引力G712IHRATFFFGFG1866G1025AGG1038整车重力G712AGG7291G27G21G21G27G49G30RFG1038滚动阻力G13007数G712FG320G17015；HFG1038汽车正常行驶时的平均爬坡G14033力G13007数G712此处G24740G170G27；IF同G990FTG321G27G21G21G27G130G170150G170G270G321G2631G17G25G25NMTCF6159219013080661731故算锥齿轮最大应力时G712计算G17728矩MNTTTCSCEC22203,MIN计当计算锥齿轮疲劳寿命时G712MNTTCFC61592主减速器主动齿轮的平均计算G17728矩ZTGCZITT0G5347G1025G主G1186动锥齿轮G19400的G1268动G6940率G712对于G2464齿G19766齿轮副G712当06IG27G283G49/MM；但G11013于齿轮材G17148G1209及制作工艺的G6564高G712许G11004应力可G6564高G210G97G215G712所G1209单位齿长G990的G3290周力G12538G2524许G11004值的要G8726G15校核G17902过。G6365最大附着力矩计算时G712PG31G27G283G49/MM；校核G17902过。G69G17采G11004轮齿弯曲强度进行计算G2464曲G19766齿轮轮齿的齿G7693弯曲应力G103830102WSVMSCWJDBMKKKKTG5347G1025CTG252G252齿轮G990的计算G17728矩G1186动齿轮G6365最大弯曲应力算时MNTC222032G6365疲劳弯曲应力算时MNTC615922主动齿轮G6365最大弯曲应力算时MNTC6121G6365疲劳弯曲应力算时MNTC6116410KG252G252过载G13007数G7120KG7291SKG252G252G4622G4556G13007数G712G3252G1038MMMS614244所G1209650425250SSMKMKG252G252齿G19766载G14667分配G13007数主动齿轮G1038G5760G14230G5347G71225111MKG712G247421MKG1186动齿轮G1038G5760G14230G5347G712111MKMG712G2474051MK9VKG252G252G17148G18339G13007数G712VKG7291BG252G252齿G19766宽G712主动齿轮MMB321G712G1186动齿轮MMB292DG252G252分度G3290直径G712主动齿轮MMD451G1186动齿MMD1852WJG252G252G13520G2524G13007数G712主动齿轮G45G320G17G21G260G712G1186动齿轮G45G320G17G21G214对于G1186动齿轮G6365最大弯曲应力计MPAW75651022401852942441051650122203232G6365疲劳弯曲应力计算MPAW21521022401852942441051650161592232对于主动齿轮G6365最大弯曲应力计算MPAW1555102700453242441216501612231G6365疲劳弯曲应力计算MPAW3149102700453242441216501614164231G6365CSCECTTT,MIN计算的最大弯曲应力不超过MPAW700G6365CFCTT计算的疲劳弯曲应力不应超过MPAW210G11013G990G17860计算G13479G7536可G117051WWG7122WWG7121WWG7122WWG712所G1209最大弯曲应力G12538G2524设计要G8726G70G17采G11004轮齿接触强度进行计算G2464曲G19766齿轮轮齿的齿G19766接触应力JVFMSZPJJBKKKKKTDC012G5347G1025PCG252G252G13520G2524G5389G5627G13007数G712G19062对G19062的齿轮MMNCP212341DG252G252主动齿轮大端分度G3290直径MMD451ZTG252G252主动齿轮计算G17728矩G712MNTZ612G712MNTZ614164SKG252G252G4622G4556G13007数G712SKG32110FKG252G252G15932G19766G2709G17148G13007数G7121FKBG252G2521B和2BG1025较小的齿G19766宽G712MMBB292JG252G252齿G19766接触强度的G13520G2524G13007数G7122350JG6365最大弯曲应力算MPAJ122582350291100005111612245234G6365疲劳接触应力算MPAJ151171235029110000511614164245234G6365CSCEZTTT,MIN计算的最大接触应力不应超过MPAJ2800G6365CFZTT计算的疲劳接触应力不应超过MPAJ1750G11013G990G17860计算G13479G7536可G11705G712,JJJJ所G1209主减速器锥齿轮的接触应力G12538G2524要G87264主减速器齿轮的材料及G9921处理汽车G20549动桥主减速器的工作G11468当G13333重G712G4439具G7389载G14667大、作G11004时G19400长、载G14667G2476G2282G3822、G5114G1926G1999等G1260G9869G712G1866G6451G3363G5430G5347主要G7389齿G7693弯曲G6252G7041、齿G19766疲劳G9869G15444、磨G6451和G6842G1272等。对G20549动桥齿轮材料及G9921处理应G7389G1209G991要G87261具G7389高的弯曲疲劳强度和G15932G19766接触疲劳强度及G3921的齿G19766G13796磨G5627G712故齿G15932G19766应G7389高的G11840度；G21齿轮G14467部应G7389适当的G19899G5627G1209适应G1926G1999载G14667G712避免在G1926G1999载G14667G991轮齿G7693部G6252G7041；3G19062材的G19215G17908、G2011G2078与G9921处理等G2164工G5627G14033G14403G3921G712G9921处理G2476G5430小或G2476G5430G16280G5471G5627G7143G6523制G712G1209G6564高G1147G2709G17148G18339G712减少制G17908G6116G7424并G19489G1314G5235G2709率；4选择齿轮材料的G2524G18341G1815G13044时要适应G6117G3281的情况。汽车主减速器和差速器G3290锥齿轮与G2464曲G19766齿轮G11458前均采G11004G9195G11911G2524G18341G19062制G17908。G7424G8437设计采G11004G19062号G1038G210CRG48NG55I的G19062材制G17908。G11004G9195G11911G2524G18341G19062制G17908的齿轮经G9195G11911、G9152G9791、G3250G9791G2530G712齿轮G15932G19766G11840度可高G17810G43G53C5G27G97G254G15G13792G14467部G11840度较G1314G712G43G53C3G21G9745。对于G9195G11911G4630G9157度G712端G19766模数少于5时G712G10380G17G28G971G173MMG712G6117G1216G4570此G9157度设定G10381G173MM。G11013于G7044齿轮G9082G9381不G14403G712G2464曲G19766齿轮副在G9921处理和G12946G2164工G2530均应G1209G2414度G10380G17005G970G17010G970G170G210MM的G11979G2282处理G712G1055G2530对齿G19766进行G2955G1036处理G712G17837G7691G7389可G14033G6564高寿命G17810G215。5主减速器轴G6227的计算G6365扭G17728强度G1284算主减速器主动轴的最小直径G1038MMNPCD6433623286611033MIN材料选择45G16855G17148G19062G2474最小直径DG3233G174G25G1313G3234G174MMG973G25MMDMING323G25MM参G13783资料G1025G42G37/G55G21G28G26G16G284G15G6117G1216G7693G6466主减速器的G13479G7512G4622G4556初G8505选定轴G6227的G3423号G1038G3290锥滚子轴G62273G21G280G27和3G21010G712G1866轴G6227G1881径分G2047G103840MM和50MM。G3252G1038主动锥齿轮G1038G17882时G19036G7053G2533旋G17728G712螺旋G7053G2533G1038左旋G712G11013资料G1025查G5483公G5347可G11705主动锥齿轮G990总的轴G2533力G103811NFFAZ9011416713COS35SIN6713SIN19TAN35COS91963COSSINSINTANCOS总的径G2533力G1038NFFRZ1211276713SIN35SIN6713COS19TAN35COS91963SINSINCOSTANCOSG5347G1025G712FG252G252齿G19766宽G1025G9869处的G3290周力G712NBDTDTFM9196310003376SIN27917314523376SIN2222G5760G14230G5347G6915G6227主动锥齿轮的轴G6227A、G37径G2533载G14667的计算（参G11487图3G712G2474G68G3235MMG30G69G32G265MMG709G32G32G25G26G27G27G1710G49G32G32453G27G170G49G7693G6466G53及A计算所G5483的G51值G7171G16825轴G6227的总当G18339动载G14667DPG712可直接G11004于G10711轴G6227的G20081定寿命G4710G25G17728G709221096123418903/10QFCFLPTG5347G1025G712CG252G252轴G6227的G20081定动载G14667G712G11013轴G6227手G1888查G5483G280G17G27G252G252G9213度G13007数G712查G5483G321G166G252G252寿命G6363数G712对G3290锥滚子轴G6227G2474G166G3210/3；G252G252载G14667G13007数G712G2474G729G717G720G52G252G252轴G6227的当G18339动载G14667G712G32G756G711G757G729G729G717在实际计算G1025G712常G1209工作小时数G15932G12046轴G6227的G20081定寿命G712HNLLH97845352623286010221096123601066G5347G1025G712NG252G252轴G6227的计算G17728速（R/MING709G15可G6466汽车平均行驶车速计算G712G778G7294G171。DMIN36MML10961232212G1186动齿轮轴G6227的计算G17728矩G10389271529750806626622RAMRVNR/MING712G89G68MG2474G1038G270G78M/G75G712HNLLH119155224927158010221096123601066G25G709主减速器的G9082G9381主减速器及差速器的齿轮、轴G6227G1209及G1866G1194G6717G6842G15932G19766均G20047G9082G9381G712G17902常在G1186动齿轮的前端近主动齿轮处的主减速G3783的G1881G3733G990设一G999G19388的G19610G8845G8145G712G4570G20146G9305G2052G3783G1319G1881G3733G990的部分G9082G9381G8845G6922G19610来G1889经过进G8845孔引至前轴G6227G3290锥滚子的小端处G712G11013于G3290锥滚子轴G6227在旋G17728时的泵G8845作G11004G712使G9082G9381G8845G11013G3290锥滚子的小端G17902G2533大端G712并经前轴G6227前端的G3250G8845孔流G3250G20549动桥G1025G19400的G8845盆G1025G712使G9082G9381G8845G5483G2052循环。G17837G7691不G7041可使轴G6227G5483G2052G14403G3921的G9082G9381、散G9921和清洗G712G13792且可G1209保护前端的G8845封不被破G3363G712G1038了保证G7389足够的G9082G9381G8845G14033流进差速器G712G7389的采G11004G999G19388的导G8845匙。G1038了防止G3252G9213度升高G13792使主减速器G3783和桥G3783G1881部压力升高所引起的漏G8845G712应在主减速器G3783G990或桥G3783G990装置G17902气塞G712G2530者应避开G8845G9305所及G1055处。G2164G8845孔应设置在G2164G8845G7053便G1055处G712G8845孔位置也决定了G8845G19766位置。放G8845孔应设在桥G3783最G1314处G712但也应G13783虑G2052汽车在G17902过障碍时放G8845塞不G7143被撞掉。差速器的设计计算差速器的作G11004G7171G1038了消除G11013于左、右G20549动轮在运动G4410G990的不协G16855G13792G1147G10995的弊病G712保证汽车G20549动桥两侧车轮在行程不等时具G7389G1209不同速度旋G17728的特征G712G1186G13792G9397足了汽车行驶运动G4410的要G8726。I差速器运动G4410及G1881G6717G68421G709工作G2419理及运动特G5627G7424G8437设计采G11004对称G5347G3290锥行星齿轮差速器G712G1866工作G2419理如G991W0G1038主减速器G1186动齿轮或差速器G3783的角速度；1G7122W分G2047G1038左、右G20549动车轮或差速器半轴齿轮的角速度；3G1038行星齿轮绕G1866轴的自G17728角速度。当差速器开G3999工作时G712行星齿轮不仅G7389绕半轴齿轮G1025心的“公G17728”G712G13792且还G7389绕行星齿轮轴G1209角速度3的自G17728。G17837时外侧车轮及G1866半轴齿轮的G17728速G4570增高G712外侧半轴齿轮的角速度G103813301ZZG30HL7845352913G1881侧半轴齿轮的角速度G103813302ZZG30G11013此可G117050212G21G709差速器技术参数差速器的G1881G6717G6842使G20549动桥左右半轴的G17728矩分配改G2476G712G17837G7389利于改G2476汽车的G17902过G5627。例如当汽车的一G1022G20549动轮G11013于附着力G2476G3363G13792开G3999G9381G17728时G712G1268给G4439的G17728矩就减小G712G13792G1268G2052不G9381G17728车轮的G17728矩却G11468应增大了G712G13479G7536在汽车左右G20549动车轮G990的总牵引力可G14033G17810G2052的最大数值G1038RFTRTFFMINMAX2G712G11013此可见G712G11013于差速器的G1881G6717G6842使汽车总牵引力增大了RFRT。G17902常采G11004锁紧G13007数12TTKG15932G12046两侧G20549动轮的G17728矩可G14033G11468差的最大倍数G712G4439也说明了迫使差速器工作所需的力矩大小；采G11004G17728矩分配G13007数02TTG15932G12046差速器的G17728矩分配特G5627。参照资料1推荐数G6466G712G6117G1216G2474锁紧G13007数G46G321G175；G17728矩分配G13007数60。II差速器的G13479G7512组G6116和参数选择对称G5347G3290锥行星齿轮差速器G11013差速器左、右G3783G712G21G1022半轴齿轮和G21G1022行星齿轮G712行星齿轮轴G712半轴齿轮及行星齿轮垫片等组G6116。行星齿轮的背G19766和差速器G3783G11468应位置的G1881G15932G19766均做G6116G10711G19766G712保证行星齿轮对正G1025心G712G1209利于和两G1022半轴齿轮正确的啮G2524。1G709差速器齿轮的G3534G7424参数选择G29G68G17行星齿轮数G11458的选择G17747车常G11004G21G1022行星齿轮G69G17行星齿轮G10711G19766半径G53G37MM的确定可G6466经验公G5347MMTKRJBB043922203333G5347G1025BKG252G252行星齿轮G10711G19766半径G13007数G712推荐选择3BKG712BR确定G2530G712可G6466BRA9909800来预选G1866节锥距。0AG323G27G175MMG70G17行星齿轮与半轴齿轮齿数的选择G1038了G5483G2052较大的模数G1186G13792使齿轮G7389较高强度G712应使行星齿轮的齿数尽G18339少G712但一般不应小于10。半轴齿轮的齿数采G1100414G97G215。半轴齿轮与行星齿轮的齿数G8616G3822在1G175G97G21范围。G1038G9397足安装要G8726G712左、右两半轴齿轮的齿数G1055和G712必G20047G14033被行星齿轮的数G11458整除G712RB372MMA037MMD22MM14即NZZRL22整数G712G1038G9397足G1209G990要G8726G712G6117G1216G2474111ZG151822RLZZDG17差速器G3290锥齿轮模数及半轴齿轮节G3290直径的初G8505确定先初G8505G8726G1998G3290锥齿轮的节锥角1GG7122G42311811ARCTANARCTAN211ZZ57581118ARCTANARCTAN122ZZG1866G10251Z和2ZG1038行星齿轮和半轴齿轮齿数G1889G7693G6466G991G5347确定G3290锥齿轮大端模数MMZAZAM6535758SIN185382SIN2SIN2220110MG324G170MM则节G3290直径G1038MMMZD440411111DG3244MMMMMZD0720418222DG32G26G21G170MMG72G17压力角G68G11458前汽车差速器齿轮大都采G110040322的压力角G712齿高G13007数G10380G17G27G712最少齿数G103810G712并且在校齿轮齿顶不G2476尖的条件G991G712还可G1209G7389G2011G2533修正G2164大半轴齿轮齿G2414G712G1186G13792使行星齿轮与半轴齿轮趋于等强度。FG17行星齿轮安装孔直径D及G1866G9157度G47的确定（见图G709行星齿轮安装孔与行星齿轮轴名义直径G11468同G712MMRNTDDC841882829811100022203111030G5347G1025G7120TG252G252差速器G1268递的G17728矩G712G2474CSCETT,MIN（MNG709；NG252G252行星齿轮数G712NG32G21；G252G252行星齿轮G6915G6227G19766G1025G9869G2052锥顶的距G12175G712240DRDG320G174G26G21G32G21G27G17G27MMG30Z111,Z2LZ2R22D133MMD2660MM30MMA2230D1828MML20MM15CG252G252G6915G6227G19766的许G11004挤压应力G712G2474G1038G28G27G48G51G68。A124A2A0A3A4A5A6A7A8A9A10A6A11A12A0A3A4A5A7A8A9A10A6A115A13A14A15A16A17A18A19A20A21A221A23A24A25A26A25A27Z1,10A28A29A30A31A32A33112A34A35A36A37A36A38Z21425183A39A38M44A36A40A41F025030A0F10M115A36A42A43A44HG16M646A36A45A44H1788M005172037A46A47A48A49A50A51A52A3022OA53A54A55A56A57A51A52A58A25O2258A35A59A4890O90O9A60A61A62A63D1MZ1D2MZ244A5372010A60A64A48211ARCTANZZA53122ARCTANZZA65290O13142O5857O11A60A64A66AO2211SIN2SIN2DD422012A67A60T31416M12566413A36A68A44MZZHHHHG21222137004300472732272714A36A69A442“21178817881HMHHMH239474879315A63A70A71A7205101880MHHCG080316A36A69A48OOAHAH“22“11ARCTANARCTAN63917O65954O17A40A64A4812022101380154O16649617O18A73A74A75122211RR2482460521783019A76A77A78A792220211101COS2COS2HDDHDD52068274370220A80A81A82A83A84A85A86A76A87A88A892210211201SIN2SIN2HDHD29535620060721A90A91A92A85A93MAHHTSSTSTAN22122126215A940520122A85A95A96A97A98A99A100A101A102A103A104A105A106A107014323A108A85A932626223222131121BDSSSBDSSS25481A940448624A108A85A10022222112114COS4COS21DSHHDSHH42889A94219192）差速器齿轮的强度计算差速器齿轮主要进行弯曲强度计算，而对于疲劳寿命则不考虑，这是由于行星齿轮在差速器的工作中经常只起等臂推力杆的作用，仅在左、右驱动车轮有转速差时兴行星齿轮和半轴齿轮之间才有相对滚动的缘故。汽车差速器齿轮的弯曲应力为JNDMBKKTKVMSW223102式中，T半轴齿轮计算转矩，MN，060TTSK尺寸系数，反映材料性质的不均匀性，SK0629MK载荷分配系数，取MK10；VK质量系数，取VK1；D26MM172B半轴齿轮齿宽；2D大端分度圆直径JN4,J选取0257N差速器行星齿轮数，N2；按上式计算的汽车差速器齿轮的弯曲应力，应不大于980MPA，由49327MPA980MPA,故校G7692G17902G17819。车轮G1268动G16025G13634G16786计计算驱动车轮的G1268动G16025G13634G1313于汽车G1268动系的G7423端，G1866G2163用是G4570转矩由差速器半轴齿轮G1268G13485驱动车轮。在G7041G5332式驱动G7737上，驱动车轮的G1268动G16025G13634G2265G6336半轴和等速G987G2533G14422，这时半轴和等速G987G2533G14422G4570差速器半轴齿轮G994轮G8598G17842G6521起G7481。G44G714半轴的G5430式G1852G9026式半轴的G3818端G994轮G8598相G17842，而轮G8598G2460由G980对轴G6227G6915G6227于G7737G3783的半轴G3883G12661上，G3822G18331用G980对圆G19193滚G4388轴G6227G6915G6227轮G8598，G1000G1016轴G6227的圆G19193滚G4388G4579端相G2533G4445G16025G5194有G980G4462的G20056G13051，G16855G3921G2530由G19157G13051G15758G8609G1116G1209G19157G13051。由于车轮G6164G6227G2475的G3414G2533力G612、G13449G2533力G592和G1403G2533力G602G1209G2462由G1194G1216G5353起的弯矩G18129经G17819轮G8598、轮G8598轴G6227G1268G13485G7737G3783，故G1852G9026式半轴在G10714G16782上只G6227G2475转矩而不G6227G2475弯矩。G44G44G714半轴的G16786计G994计算1）半轴的计算载荷半轴的主要尺寸是G4439的直径，G16786计G994计算时G20330G1820应G2524G10714G3332G11842G4462G1866计算载荷。半轴的计算应考虑G2052G1209G991G989G12193G2499G14033的载荷工G19291G13449G2533力G592G708驱动力G6122G2058动力）G7380大时G11G592G612G73G12，G19480G11540系数取08，G8821有G1403G2533力作用；2G1403G2533力G602G7380大时，G1866G7380大G1552G2469G10995于G1403G9381时，为G612G731，G1403G9381时轮G13986G994G3332G19766的G1403G2533G19480G11540系数在计算中取10，G8821有G13449G2533力作用；3G3414G2533力G7380大时，这G2469G10995在汽车G1209G2499G14033的G20652速G17902G17819不G5191G17347G19766时，G1866G1552为G11G612G16G74G90G12G78G71,G78G71是动载荷系数，这时G8821有G13449G2533力和G1403G2533力的作用。由于车轮G6227G2475的G13449G2533力G592、G1403G2533力G602G1552的大G4579G2475车轮G994G3332G19766G7380大G19480G11540力的G19492G2058，G2375有22222YXZ故G13449G2533力G592G7380大时不G1262有G1403G2533力作用，而G1403G2533力G602G7380大时G1075不G1262有G13449G2533力作用。2）半G9026式半轴的G16786计计算G7081）G2058动时强度计算汽车G9397载G19757G8502于G3332G19766上时驱动G7737G13485G3332G19766载荷KGM8552NG837989855218汽车G18337量转G12239系数9507502M取08G19480G11540系数98070取08G13449G2533力按G7380大G19480G11540力算NGMFXX25147508379280222222A109滚动半径MM29750KRMNRXMK927472A110A111半轴G6227G2475的G6209转应力233337216102616297471016MMNDMPIPIA112500G49G18G80杆G18108直径G2033选G71G300G11205218G12G11253270G80G80G12取G7126G80G80G7082）G2475G7380大牵G5353力时强度计算对于驱动车轮G7481说，当G2469动机G7380大转矩G2462G1268动系G7380低档G1268动比计算G6164得的G13449G2533力G708见G991式）G4579于按G7380大G19480G11540力G6164决G4462的G13449G2533力时，则应按G991式计算，G2375RTTLERITXXMAX22A113A114或差速器的转矩分配系数，对于普G17902圆G19193齿轮差速器取06MAXETG2469动机G7380大转矩G708MN）；TLIG1268动系G7380低档G1268动比，G2375为变速器G980档G1268动比、副变速器G6122分动器低档G1268动比G994主减速比之乘积；T汽车G1268动系效率，计算时G2499忽略不记G6122取09；RR轮G13986的滚动半径G708G80）。AG714G2469动机G7380大G6209矩MAXEM，G1268动系G7380低档数比G1268G2052半轴上G6209矩1901MAXIIMMGEAA1151114545314560MN91267由技术资料得60；5453GI；11140I。BG714取412M80NGMX46928083792412222A116MNRXMKB913952975046922A117A118式中2GG9397载G19757G8502汽车的驱动G7737对水G5191G3332G19766的载荷，G49；M汽车加速和减速时的质量系数，对于前驱动G7737G2499取1M1417，对于G2530驱动G7