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外啮合渐开线园柱齿轮传动iso9085外啮合图号：2020/2/1423:56几何参数1精度等级66传动比u2模数Mn18分度圆直径d1369.469几何直径12805603齿数Z120分度圆直径d21200.776几何直径2100016004Z265齿顶圆直径da1420.235几何模数16255齿形角an20齿顶圆直径da21249.863几何齿宽2504006齿顶高系数ha1*1齿根圆直径df1335.737齿距极限偏差±fpt17.51914920.17781617齿顶高系数ha2*1齿根圆直径df21165.365基节极限偏差±fpb16.46261518.96094498齿顶根高系数hf1*1.4公法线长度Wn1197.115齿距累积总偏差Fp53.56199781.25644789齿顶根高系数hf2*1.4公法线长度Wn2474.449齿廓总偏差Fa27.41971732.293940710螺旋角β13全齿高h142.24858747螺旋线总偏差Fβ24.59753626.813091911中心距A800全齿高h242.2485875螺旋倾斜极限偏差±fHβ17.52946619.080355212变位系数X10.4630跨齿数K14齿廓形状偏差ffα21.30259725.069042413X20.4164跨齿数K29齿条啮合齿廓始点De1&2353.941551181.1053814顶隙系数系数C*0.4端面重合度εα1.4135齿轮啮合齿廓始点DAE1&2356.310551190.9251215总变位系数Xn0.8794纵向重合度εβ1.5116滑动率η0.98053710.9803269316取变位系数Xn10.4630啮合线长度gα76.8462205齿顶厚度Sa10.39011413.036994417齿宽B380齿顶高ha25.38258724.5433575修形起始点405.834651233.66252修形起始点长度dtlxa13.20960419.1329152强度计算参数1输入功率P(Kw)3500输入扭矩T1（Nm）70624.453282输入转速n1(转/分）473.278输出转速n2(转/分）145.6243使用系数KA2.5传动比u3.254设计寿命N（年）15输出扭矩T2(Nm)229529.47325工作制h（小时）24分圆圆周力Ft(N)382301.96183.25第1页外啮合6工作制t（天）360径向力Fr142806.65987啮合刚度cγ17.70448088轴向力Fa88261.362278支点距离l1035刀具齿顶高hao25.29齿宽重点位置s115.5刀具齿顶圆角半径ρao7.210小轮材料疲劳极限σHlim1500动载系数KV1.02111大轮材料疲劳极限σHlim1500齿向载荷系数KHβ(不大于2)1.11312小轮材料弯曲极限σFlim500齿向载荷系数KFβ(不大于2)1.10013大轮材料弯曲极限σFlim500齿间载荷系数KFα0.95014齿轮内腔直径di10接触应力σH11114.56115齿轮内腔直径di20接触应力σH21114.56116单对齿刚度C'13.514齿形系数YF11.41917系数K'-0.6齿形系数YF21.44518寿命N13.6802E+09应力修正系数YS12.01919寿命N21.1324E+09应力修正系数YS22.07720寿命系数ZNT10.866246528齿根应力σF1380.64721寿命系数ZNT20.885968904齿根应力σF2399.07822润滑系数ZLZVZR1接强安全系数SH11.16623齿面工作硬化系数ZW11接强安全系数SH21.19224齿面工作硬化系数ZW21弯强安全系数SF11.95025材料滑移层厚度ρ’0.003弯强安全系数SF21.90926相对齿根表面YRrelT0.93027弯曲强度尺寸系数Yx0.922寿命系数YNT10.867411097寿命系数YNT20.888101576齿数Z120齿数Z265法向模数mn18中心距a800齿面宽b380分度圆柱上的螺旋角β0.22689280313第2页外啮合齿高系数ha1*1齿高系数ha2*1法面压力角αn0.3490658520齿顶系数cn*0.41分度圆直径d1d1=Mn*Z1/COSΒ369.4694788369.4695分度圆直径d2d2=Mn*Z2/COSΒ1200.7758061200.77582未变位时中心距AdAd=Mn*(Z1+Z2)/2COSΒ785.1226425785.12263中心距变动系数YnYn=(A-Ad)/Mn0.8265198630.82654啮合角awttgat=tgan/COSβ0.3735441470.3735at=arctgat0.35749369520.4829COSαwt=Ad/A*COSat0.9193558360.9194awt=arccosawt0.40435630223.1679齿顶压力角αat1αat=arccos(db/da)0.60304526234.55194838齿顶压力角αat20.45105868325.843758845总变位系数Xninvawt=tgawt-awt0.0235814330.0236invat=tgat-at0.0160504510.0161Xn=(Z1+Z2)*(invawt-invat)/(2*tgan)0.8793761150.87946变位系数分配Xn1Xn2Xn1取值0.4630.4630Xn2=Xn-Xn10.4160.41647齿顶高变动系数ΔYnΔYn＝Xn-Yn0.0530.05298齿顶高ha1ha2ha1=(ha1*+Xn1-ΔYn)*Mn25.3825874625.3826ha2=(ha2*+Xn2-ΔYn)*Mn24.5433575424.54349齿根高hf1hf2hf1=(ha*+cn*-Xn1)*Mn16.86616.8660hf2=(ha*+cn*-Xn2)*Mn17.7052299217.705210齿高h1h2h1=ha1+hf142.24942.2486h2=ha2+hf242.24942.248611齿顶圆直径da1da2da1=d1+2*ha1420.2346537420.2347da2=d2+2*ha21249.8625211249.862512齿根圆直径df1df2df1=d1-2*hf1335.7374788335.7375df2=d2-2*hf21165.3653461165.3653第3页外啮合基圆直径db1db2db1=d1*cosαt346.1104323346.1104db2=d2*cosαt1124.8589051124.8589端面模数mtmt=mn/cosβ18.4734739418.4735基圆螺旋角βbsinβb=sinβ*cosαn0.21299160612.2035啮合线长度gαgα=1/2*((da1^2-db1^2)^0.5+(da2^2-db2^2)^0.5)-a*sinαwt76.846220576.8462端面基节pbtpbt=mt*π*cosαt54.3668995254.3669端面重合度εαεα=gα/pbt1.4134743971.4135纵向重合度εβεβ=bH*sinβ/π/mn1.5116430521.511613公法线计算Wn1Wn2当量齿数Zn1Zn2Zn1=Z1/(cosβb)^2/cosβ21.4861601321.4862Zn2=Z2/(cosβb)^3/cosβ69.8300204369.8300z'=z*invαt/invαn21.5378932821.537969.9981531869.9982跨测齿数K1K2k=z'/π*(1/cosαn*((1+2*xn/z')^2-(cosαn)^2)^0.5-2*xn*tanαn/z'-invαn)+0.53.5923137083.59238.9721771398.97220.00000.00000.0000K13.5923137084K28.9721771399W*1W*2W*=COS(PI(K-0.5)+Z**INVan)10.6341098210.634126.0734790326.0735Wn1Wn1=(W*1+2*Xn1*SINan)*Mn197.1147685197.1148Wn2Wn1=(W*2+2*Xn2*SINan)*Mn474.4493473474.44931支点距离l1035.0000齿宽中点位置s115.5000齿距极限偏差fpt1/fpt2(μm)17.5191488320.178基节极限偏差fpb1/fpb2(μm)16.4626148818.961螺旋线倾斜极限偏差fHβ1/fHβ217.5294659219.080螺旋线倾斜极限偏差fHβ512.3952042213.492第4页外啮合螺旋线公差Fβ1、Fβ224.5975358426.813齿廓公差Fa1/Fa227.4197173932.294齿距累积公差Fp1、Fp253.5619971781.256齿面粗糙度Ra101/Ra1020.80.800齿根表面粗糙度Rz101/Rz1026.36.300齿廓形状偏差fta1/fta221.3025971225.069强度计算名义切向载荷Ft(N)Ft=2000/d1*(9550*P/n1)382301.9618382301.962使用系数KA2.5小轮材料疲劳极限σHlim1500大轮材料疲劳极限σHlim1500小轮材料弯曲极限σFlim500大轮材料弯曲极限σFlim500齿高中部直径dm1/dm2dm=(da+df)/2377.98606631207.613934齿轮内腔直径di1/di200轮缘内腔直径比qq=di/dm00材料密度ρ（kg/mm^3）0.0000079单位齿宽转动惯量J*J*=π/32*ρ*(1-q^4)*dm^415831.794391649451.08齿轮副诱导质量mred(kg/mm)mred=J1**J2*/(J1**rb2^2+J2**rba^2)0.479979948啮合刚度cγ(N/(mm.μm)cγ=17.70448088临界转速nE1nE1=30*10^3/π/z1*(cγ/mred)^0.52899.822655临界转速比N（共振区0.2~0.5）N=n1/nE10.163209291总重合的εγεγ=εα+εβ2.925117449系数Cv1/Cv2/Cv30.320.2171331420.070齿廓偏差跑合量yp1/yp2yp=ya=0.075*fpb1.2346961161.422有效基节偏差fpbeHfpbeH=fpb-yp15.2279187617.539齿距偏差跑合量yfyf=0.075*fta1.5976947841.880有效齿廓形状偏差ffeHffeH=fta-yf19.7049023323.189单对齿刚度C'13.514跑合齿顶磨合量Cay（μm）Cay=1/18(σHlim/97-18.45)^2+1.51.995第5页外啮合系数BpBp=C'*fpbeH/(Ft*KA/b)0.0818190520.094系数BfBf=C'*ffeH/(Ft*KA/b)0.1058737210.125系数BkBk=|1-c'*Ca/((Ft*Ka)/b)|0.989动载系数KVKV=N(Cv1*Bp+Cv2*Bf+Cv3*Bk)+11.021单位载荷Fm/b(小于100时=100)Fm/b=Ft*KA*Kv)/b2567.186弯曲强度计算名义轴颈dshdsh=109*(p/n)^(1/4)179.748d1/dsh(大于1.15为刚性）2.055系数K'(右表)-0.600当量啮合齿向误差fshfsh=Fm/b*0.023*(|1+K'*l*s/d1^2*(d1/dsh)^4