锥齿轮设计参数111

计算项目符号单位一.已知条件传递最大功率Pkw电机的额定功率小齿轮最大转速n1rpm额定转速电动机最大扭矩Tnm最高车速Vmaxkm/h滚动半径rmm总最大传动比i总max变速器一挡传动比变速器三挡传动比轴交角∑°齿轮精度齿线形状小齿轮材料及热处理40Cr大齿轮材料及热处理40Cr材料及热处理质量等级原动机特性工作机特性齿轮支撑形式1.齿形制　齿形角α°　齿顶高系数ha*　顶隙系数c*2.初选传动比i0主动齿轮的最大扭矩Tjenm主动齿轮齿数Z1节圆直径d2直径系数Kd2二.几何计算锥齿轮传动设计计算大端端面模数mmm模数系数Kmz1z24.齿数比ux1x2xt1xt2δ1°δ2°d1mmd2mmdm1mmdm2mmRRmmm9.齿宽系数φR齿宽bmm10.螺旋角β°11.齿宽中点的螺旋角βm°12.齿宽中点法向模数mnmmmha１mmha２mmhf１mmhf２mmh１mmh２mmda1mmda2mmθf1°θf2°θa1°θa2°δa1°δa2°16.齿顶圆直径17.齿根角18.齿顶角19.顶锥角3.齿数5.变位系数6.节锥角7.分度圆直径8.锥距13.齿顶高14.齿根高15.齿高12/zzu=3/14/1～=RfRbRf=)5.01(RmRRf-=)sin2/(11ddR=mxhhaa)(2,1*2,1+=2,12,12,1fahhh+=2,12,12,12,1cos2daahdd+=bq22,12,1cosarctanRhff=δf1°δf2°Ak1mmAk2mm22.安装距Amm23.支撑端距Hmms1mms2mmmmmmmmmmzv1zv226.端面重合度εα°radrad27.轴向重合度εβ28.法向重合度εαnA.计算接触应力σHN/mm21.节点区域系数ZH当量齿轮端面齿形角αvt2.弹性系数ZE3.重合度系数Zε当量齿轮纵向重合度εVβ当量齿轮端面重合度εVα当量齿轮啮合线长度gVαmmdvb1mmdvb2mmdva1mmdva2mm22.分度圆弧齿厚23.分度圆弦齿厚24.分度圆弦齿高25.当量齿数当量齿轮基圆直径当量齿轮齿顶圆直径20.根锥角21.外锥高三.接触强度校核计算2,12,12,1ffqdd-=2,12,11,22,1sin2/dakhdA-=___1ns___2ns___2nh___1nh1vat2vatt2/mmN-+-=tvattvatzzddtantancostantancos21222111当量齿轮中心距avmmdv1mmdv2mm4.螺旋角系数Zβ5.锥齿轮系数ZK6.使用系数KA7.动载系数KV临界转速比N中点圆周速度vmtm/s系数K齿距极限偏差fptμm跑合量yaμm单对齿刚度c'N/mm·μm系数cV12系数cV3齿宽中点切向力FmtN8.齿向载荷分布系数KHβ轴承系数KHβbe9.齿间载荷分布系数KHα10.有效齿宽beHmm11.当量圆柱齿轮齿数比uvB许用接触应力σHPN/mm21.接触疲劳极限σHlimN/mm22.润滑剂系数ZL3.速度系数ZV4.粗糙度系数ZR5.尺寸系数ZX6.最小安全系数SHlimC.强度条件A.计算齿根应力σFN/mm21.齿向载荷分布系数KFβ2.齿间载荷分布系数KFα当量齿轮分度园直径四.弯曲强度校核计算21cos/cosdduuv=XRVLHHHPZZZZSlimlimss=3.齿形系数YFa4.应力修正系数Ysa5.重合度系数Yε6.螺旋角系数Yβ7.锥齿轮系数YKB.许用齿根应力σFPN/mm21.弯曲疲劳极限σFlimN/mm22.试验齿应力修正系数YST3.相对齿根圆角敏感系数YδrelT4.齿根表面状况系数YRrelT5.尺寸系数YX6.最小安全系数SFlimC.强度条件1.轴的材料和热处理方式40Cr调质抗拉强度极限σB屈服强度极限σS弯曲疲劳极限σ-1剪切疲劳极限τ-1许用弯曲应力[σ-1]2.轴直径的最小值最小直径dminmm系数A0轮体最小厚度χmm小齿轮大端直径d0锥齿轮的结构设计小齿轮结构-=120/1mVYbbb切向分力Ft1N·m径向分力Fr1N·m轴向分力Fa1N·m法相分力FbnN·m小齿轮受力公式及数据来源结果备注47%的功率和扭矩280131.613061.18000最大转数8000400040007003292802803443443.757.52.52.51.131.13正交传动90906级直齿淬火HRC52HRC52淬火HRC52HRC52GB12369-902020110.20.21.51.5001.5Tje=T·i总max·ηT/n2.8最低挡时；ηT传动效率，取0.9；n为驱动轮个数。2220.75281318.323169.60713取13～1613两轮都是悬臂支撑二.几何计算GB12369-90MQ均匀平稳均匀平稳锥齿轮传动设计计算32d2TKdje=ghi=amaxp0Vnr377.0i1.50.4234.50.3取0.3～0.40.328134242411.5003.154查表13-3-800.52高变位：x2=-x10-0.52查表13-3-900.08高变位：xt2=-xt10-0.0833.69017.59256.31072.4084258.563184.535.70048.75053.550153.75037.85896.77632.18080.6470.3000.33311.35732.25900001.2753.7501.56.841.52.161.83.061.87.743.39.93.39.944.49671.54064.664185.8062.7221.8112.7224.5732.7221.8112.7224.57336.41219.40359.03276.980埃尼姆斯齿制12/zzu=211arctan时，90当zz==δ12δδ-=2,12,1mzd=)5.01(2,121Rmddf-=，3/14/1～=RfRbRf=)5.01(RmRRf-=)sin2/(11ddR=mxhhaa)(2,1*2,1+=mxchf)h(2,1*a2,1-+=2,12,12,1fahhh+=2,12,12,12,1cos2daahdd+=bq22,12,1cosarctanRhff=RbmbR)(tan-?b2，12，1:顶隙收缩齿faqq=等2，1a212，1qdd+=，等顶顶隙收缩齿：：：a)/sinarcsin(mmRRbb=mRnmmmbfcos)5.01(-=30.96815.78153.58867.83530.66890.18319.75227.191按结构确定3.44810.7041.2643.4333.44510.6501.2643.4331.5597.3071.5042.16533.65213.63875.717135.65233.42843.58020201.1291.1801.1701.1400033.42843.5803518.241778995.7932.4952.4952020查表13-1-105189.8189.80.8770.943001.6931.3326.37114.74940.31948.05890.717478.01745.36663.80298.999510.435三.接触强度校核计算2,12,12,1ffqdd-=2,12,11,22,1sin2/dakhdA-=2,1K2,1AAH-=12111)cos/tan22/(smsxxmst-=++=bbdbcos6cos42sin122,12,1232,12,12,1____2,1???--=dssRssn??????+?????????-=2,12,122,12,12,1____2,1cos442sin1dbdshRshabd32,12,12,1coscoszzv=2,12,1*2,12,12,1cos2cosarccosdxhzzatvat++=,cos/tanarctanb=t)/(sinbbnmmmb=))cos(sincos(arcsin/b=mnvveHvmtHHVAKEHHuubdFKKKKZZZZZ11+?=bbsvtmHZb2sin/cos2=)cos/arctan(tanmvtb=)1(/11(134时时）　　?=+--=bbbbVVVVVVVZZ2,12,12,12,1tan5.02aavvabhddq-+=vtvvbddcos2,12,1=vtvvbvavbvavaddddgsin5.022222121--+-=]cos)5.0(/[vtvvbRmRg-=)]5.0(/[tan85.0bRmbRmv-=bb-+-=tvattvatzzddtantancostantancos21222111av=(dv1+dv2)/269.722279.91942.90651.14296.539508.69511配对齿轮的齿顶和齿根不进行修形0.85给定0.85查表13-1-8111KV=N·K+11.0871.1700.2930.213vmt=πdm1n1/6000014.95420.4200.2980.802查表13-3-4313131.7481.748给定14给定140.660.660.230.23Fmt=2000×9550P/(n1d1)14779.7624987.222KHβ=1.5KHβbe1.8751.875查表13-3-341.251.25查表13-3-35精度等级11beH=0.85b9.65427.4202.2509.947996.53575996.536查图13-1-24（b）11901190查图13-1-271.0251.025查图13-1-281.0751.075查图13-1-290.950.95查表13-1-10911查表13-1-1101.251.25σH≤σHP不满足满足7099.754472366.186KFβ=KHβ=1.5KHβbe1.8751.875查表13-3-35精度等级11εVα+εVβ查表13-3-33四.弯曲强度校核计算2,12,12,1cos5.0dRbRdvd-=mZbbcos=1100084.0221+=uuvzNmt31285.0/'VVmtAaptccbFKcyfK+-=HLMpt/f160sbFmt85.0/KA21cos/cosdduuv=XRVLHHHPZZZZSlimlimss=KsaFamnmtFFVAFYYYYYbmFKKKKbbs85.0=bFmt85.0/KA查图13-3-282.252.3查图13-3-291.861.840.6930.813111给定1447.125447.125查图13-1-53（b）3653652给定2查图13-1-570.980.98查表13-1-12211查图13-1-5611查表13-1-1101.6较高可靠度1.6σF≤σFP不满足满足241～286HBS毛胚直径≤1007355403552007038.192116.75730查表取值6.77选择齿轮轴结构55.54d0≤500锥齿轮的结构设计小齿轮结构bFmt85.0/KAbVmoYcossinarcsincos75.25.02+=-=120/1mVYbbbXRrelTrelTFSTFFPYYYSYdsslimlim=310mindnPA=30][2.09550000TA=][Tnmm6.1156.86347.50531.670166.930小齿轮受力11t1/2000FmdT=11r1costanFdtF=11a1sintanFdtF=cos/F1bntF=可改条件选择公式不可改查表1.5003.91419.545正火至：45调质至：45表面淬火至：35SiMn