DSZP2HA+行星减速机设计说明书.doc

DSZP2HA 行星减速机设计说明书一、 用途： 捞渣输送机主传动装置是用于2X330MW电力机组除渣设备主传动设备，该设备集机电液为一体，传动设备的主要功能是通过传动装置带动链条，链条带动刮板，当接渣斗装满后，传动装置启动，托出刮板，带出煤渣，并运到高处，把煤渣倾倒出去。二、设计输入参数：1. 工作扭矩：14000Nm；2. 最大扭矩：55000Nm；3. 转速范围：0.2-2.5rpm；4. 减速机速比：37.92：1；三、方案设计一）传动型式选择： 按最大扭矩55000Nm，总传动比37.92，选用两级NGW行星齿轮减速机。两级行星轮个数均选np=3，高速级采用行星架浮动而太阳轮和内齿轮固定的结构；低速级采用太阳轮浮动的结构。二）材料、性能选者、热处理及齿形要求1. 材料：a 太阳轮和行星轮的材料为20CrNi2MoA，渗碳淬火处理，表面硬度57+4HRC，齿面接触疲劳极限： Hlim=1450N/mm2 ， 齿根弯曲疲劳极限：太阳轮Flim=400N/mm2 ，行星轮Flim=280N/mm2 ， b 内齿轮的材料为42CrMo，调质处理，硬度为HB262293， 齿面接触疲劳极限Hlim=750N/mm2 ， 齿根弯曲疲劳极限Flim=255N/mm2 ， 2齿形齿形为渐开线直齿，外啮合最终加工为磨齿，6级精度；内啮合最终加工为插齿，7级精度。 为提高齿轮承载能力，两极均采用变位齿轮传动。三）.传动比的分配 按高速级（I）和低速级（II）齿面接触等强度的原则进行传动比的分配。取系数=1.2（低速级内齿轮分度圆直径与高速级内齿轮分度圆直径之比,一般=11.3），齿宽系数aI=0.4， aII=0.7，HlimI=HlimII，其余见下表代 号名 称说 明取 值KA使用系数按中等冲击1.5KHPI行星轮间载荷分配系数按齿轮手册表7.3-71.1KHPII1.05KHI综合系数按齿轮手册表7.3-41.8KHII由齿轮手册可知，q值为由此查齿轮手册图7.2-9，得PI=5.75 ，则 四）、配齿计算a 高速级 太阳轮齿数Za 取C=45（整数） 内齿圈齿数Zb 行星轮齿数Zc 取Zc=47b 同理可求出低速级齿数c 按齿面接触强度，计算太阳轮分度圆直径高速级太阳轮传递扭矩为：T=55000/37.68=1560N。m一对啮合副传动转矩： 则说明：KA，KHP，KH 同前，KP不均载系数，U=Zc/Za则模数 取m=4.5取a=153mm同理求出其他参数列于下表实际总传动比37.68（速比误差0.63）级别第一级第二级中心距153mm170mm模数4.57速比6.755.647齿轮太阳轮行星轮内齿轮太阳轮行星轮内齿轮齿数2047115173079齿宽62120五）、齿轮几何计算- 渐开线圆柱齿轮几何参数计算 -a 高速级外啮合 小 齿 轮 大 齿 轮 法向模数 mn = 4.50000 齿 数 z1 = 20 z2 = 47 法向变位系数 xn1 = .2270 xn2 = .3000 齿 宽 (mm) b1 = 62.0000 b2 = 62.0000 螺 旋 角 () = .00000 中 心 距 (mm) a = 153.0008 齿 数 比 u = 2.3500 端面模数 mt = 4.5000 齿顶高系数 ha1 = 1.0000 ha2 = 1.0000 顶隙系数 cn1 = .4000 cn2 = .4000 分度圆直径 (mm) d1 = 90.0000 d2 = 211.5000 节圆直径 (mm) dp1 = 91.3438 dp2 = 214.6578 齿顶圆直径 (mm) da1 = 100.8016 da2 = 222.9586 齿根圆直径 (mm) df1 = 79.4430 df2 = 201.6000 基圆直径 (mm) db1 = 84.5723 db2 = 198.7450 齿 顶 高 (mm) ha1 = 5.4008 ha2 = 5.7293 齿 根 高 (mm) hf1 = 5.2785 hf2 = 4.9500 全 齿 高 (mm) h1 = 10.6793 h2 = 10.6793 节 距 (mm) pn = 14.1372 法面的基圆齿距 pbn = 13.2846 端面的基圆齿距 pbt = 13.2846 法面压力角 () n = 20.0000 端面压力角 () t = 20.0000 端面啮合角 () tp= 22.2003 基圆螺旋角 () b = .0000 法向齿厚 (mm) sn = 7.069 分度圆弦齿厚 (mm) Sn1 = 7.8024 Sn2 = 8.0494 分度圆弦齿高 (mm) hn1 = 5.5702 hn2 = 5.8059 公法线长度 (mm) Wnk1= 35.1707 Wnk2= 76.9509 跨 齿 数 K1 = 3 K2 = 6 固定弦齿厚 (mm) sc1 = 6.8983 sc2 = 7.1095 固定弦齿高 (mm) hc1 = 4.1454 hc2 = 4.4355 圆棒(球)直径 (mm) dp1 = 7.5600 dp2 = 7.5600 跨棒(球)距 (mm) M1 = 101.6690 M2 = 223.9130 齿 顶 厚 (mm) sa1 = 2.8739 sa2 = 3.3242 最大滑动系数 1 = 1.9509 2 = 1.1210 端面重合度 epa = 1.5160 纵向重合度 epb = .0000- 渐开线圆柱齿轮精度 - 小齿轮 - IQ1=6 IQ2=6 IQ3=6 FP = .0320 ff = .0100 FBT= .0190Fr = .0280 fpt= .0130 Fb = .0190Fi= .0420 fi= .0138 Fpx= .0190Fpk= .0220 fpb= .0110Fi= .0400 fi= .0180Fw = .0200 ffB= .0138 a = 153.001 fa = .0200 6-6-6-G J GB 10095-88Wnk1= 35.171 Ews= -.0802 Ewi= -.1153K1 = 3 Ess= -.0780 Esi= -.1300- 大齿轮 -IQ1=6 IQ2=6 IQ3=6 FP = .0630 ff = .0110 FBT= .0190Fr = .0400 fpt= .0140 Fb = .0190Fi= .0740 fi= .0150 Fpx= .0190Fpk= .0320 fpb= .0130Fi= .0560 fi= .0200Fw = .0250 ffB= .0150a = 153.001 fa = .02006-6-6-G J GB 10095-88Wnk2= 76.951 Ews= -.0888 Ewi= -.1217K2 = 6 Ess= -.0840 Esi= -.1400b 高速级内啮合- 渐开线圆柱齿轮几何参数计算 - 小 齿 轮 内 齿 圈 法向模数 mn = 4.50000 齿 数 z1 = 47 z2 = 115 法向变位系数 xn1 = .3000 xn2 = .3000 齿 宽 (mm) b1 = 62.0000 b2 = 62.0000 螺 旋 角 () = .00000 中 心 距 (mm) a = 153.0000 齿 数 比 u = 2.4468 端面模数 mt = 4.5000 齿顶高系数 ha1 = 1.0000 ha2 = 0.8000 顶隙系数 cn1 = .4000 cn2 = .2500 分度圆直径 (mm) d1 = 211.5000 d2 = 517.5000 齿顶圆直径 (mm) da1 = 223.2000 da2 = 513.1125 齿根圆直径 (mm) df1 = 201.6000 df2 = 531.4500 基圆直径 (mm) db1 = 198.7450 db2 = 486.2909 齿 顶 高 (mm) ha1 = 5.8500 ha2 = 2.1938 齿 根 高 (mm) hf1 = 4.9500 hf2 = 6.9750 全 齿 高 (mm) h1 = 10.8000 h2 = 9.1688 节 距 (mm) pn = 14.1372 法面的基圆齿距 pbn = 13.2846 端面的基圆齿距 pbt = 13.2846 法面压力角 () n = 20.0000 端面压力角 () t = 20.0000 端面啮合角 () tp= 20.0000 基圆螺旋角 () b = .0000 法向齿厚 (mm) sn = 7.069 分度圆弦齿厚 (mm) Sn1 = 8.0494 Sn2 = 6.0857 分度圆弦齿高 (mm) hn1 = 5.9266 hn2 = 2.1857 公法线长度 (mm) Wnk1= 76.9509 Wnk2= 187.5133 跨 齿 数 K1 = 6 K2 = 14 固定弦齿厚 (mm) sc1 = 7.1095 sc2 = 5.3740 固定弦齿高 (mm) hc1 = 4.5562 hc2 = 1.2257 圆棒(球)直径 (mm) dp1 = 7.5600 dp2 = 7.5600 跨棒(球)距 (mm) M1 = 223.9130 M2 = 509.9085 齿 顶 厚 (mm) sa1 = 3.2047 sa2 = 4.5031 最大滑动系数 1 = -.2184 2 = .6822 端面重合度 epa = 1.6002 纵向重合度 epb = .0000- 渐开线圆柱齿轮精度 - 小齿轮 - IQ1=6 IQ2=6 IQ3=6 FP = .0630 ff = .0110 FBT= .0120 Fr = .0400 fpt= .0140 Fb = .0120 Fi= .0740 fi= .0150 Fpx= .0120 Fpk= .0320 fpb= .0130 Fi= .0560 fi= .0200 Fw = .0250 ffB= .0150 a = 153.000 fa = .02006-6-6-G J GB 10095-88 Wnk1= 76.951 Ews= -.0888 Ewi= -.1217 K1 = 6 Ess= -.0840 Esi= -.1400 M1 = 223.9130 dltlM = .2239 dltuM = .3069- 内齿圈 - IQ1=7 IQ2=7 IQ3=7 FP = .1120 ff = .0200 FBT= .0160 Fr = .0710 fpt= .0200 Fb = .0160 Fi= .1320 fi= .0240 Fpx= .0160 Fpk= .0630 fpb= .0180 Fi= .1000 fi= .0280 Fw = .0450 ffB= .0240 a = 153.000 fa = .03157-7-7-F K GB 10095-88 Wnk2= 187.513 Ews= .2080 Ewi= .0927 K2 =14 Ess= -.0800 Esi= -.2400 M2 = 509.9085 dltlM = .2708 dltuM = .6081c 低速级外啮合- 渐开线圆柱齿轮几何参数计算 - 小 齿 轮 大 齿 轮法向模数 mn = 7.00000齿 数 z1 = 17 z2 = 30法向变位系数 xn1 = .4750 xn2 = .4000齿 宽 (mm) b1 = 120.0000 b2 = 120.0000螺 旋 角 () = .00000中 心 距 (mm) a = 169.9997齿 数 比 u = 1.7647端面模数 mt = 7.0000齿顶高系数 ha1 = 1.0000 ha2 = 1.0000顶隙系数 cn1 = .4000 cn2 = .4000分度圆直径 (mm) d1 = 119.0000 d2 = 210.0000节圆直径 (mm) dp1 = 122.9785 dp2 = 217.0209齿顶圆直径 (mm) da1 = 138.3994 da2 = 228.3494齿根圆直径 (mm) df1 = 106.0500 df2 = 196.0000基圆直径 (mm) db1 = 111.8234 db2 = 197.3354齿 顶 高 (mm) ha1 = 9.6997 ha2 = 9.1747齿 根 高 (mm) hf1 = 6.4750 hf2 = 7.0000全 齿 高 (mm) h1 = 16.1747 h2 = 16.1747 节 距 (mm) pn = 21.9911法面的基圆齿距 pbn = 20.6649端面的基圆齿距 pbt = 20.6649法面压力角 () n = 20.0000端面压力角 () t = 20.0000端面啮合角 () tp= 24.5923基圆螺旋角 () b = .0000法向齿厚 (mm) sn = 10.996 分度圆弦齿厚 (mm) Sn1 = 13.3876 Sn2 = 13.0254 分度圆弦齿高 (mm) hn1 = 10.0774 hn2 = 9.3769 公法线长度 (mm) Wnk1= 55.6034 Wnk2= 77.1837 跨 齿 数 K1 = 3 K2 = 4 固定弦齿厚 (mm) sc1 = 11.8466 sc2 = 11.5091 固定弦齿高 (mm) hc1 = 7.5438 hc2 = 7.0802 圆棒(球)直径 (mm) dp1 = 11.7600 dp2 = 11.7600 跨棒(球)距 (mm) M1 = 139.0331 M2 = 230.3604 齿 顶 厚 (mm) sa1 = 3.9420 sa2 = 5.0198 最大滑动系数 1 = 1.4484 2 = 1.4006 端面重合度 epa = 1.3297 纵向重合度 epb = .0000- 渐开线圆柱齿轮精度 - 小齿轮 -IQ1=6 IQ2=6 IQ3=6FP = .0450 ff = .0120 FBT= .0160Fr = .0320 fpt= .0140 Fb = .0160Fi= .0570 fi= .0156 Fpx= .0160Fpk= .0220 fpb= .0130Fi= .0450 fi= .0200Fw = .0200 ffB= .0156a = 170.000 fa = .02006-6-6-G J GB 10095-88Wnk1= 55.603 Ews= -.0868 Ewi= -.1237K1 = 3 Ess= -.0840 Esi= -.1400- 大齿轮 -IQ1=6 IQ2=6 IQ3=6FP = .0630 ff = .0130 FBT= .0160Fr = .0450 fpt= .0160 Fb = .0160Fi= .0760 fi= .0174 Fpx= .0160Fpk= .0320 fpb= .0140Fi= .0630 fi= .0220Fw = .0250 ffB= .0174a = 170.000 fa = .02006-6-6-F J GB 10095-88Wnk2= 77.184 Ews= -.0712 Ewi= -.1393K2 = 4 Ess= -.0640 Esi= -.1600d 低速级内啮合 - 渐开线圆柱齿轮几何参数计算 -小 齿 轮 内 齿 圈法向模数 mn = 7.00000齿 数 z1 = 30 z2 = 79法向变位系数 xn1 = .4000 xn2 = .1930齿 宽 (mm) b1 = 120.0000 b2 = 120.0000螺 旋 角 () = .00000中 心 距 (mm) a = 169.9999齿 数 比 u = 2.6333端面模数 mt = 7.0000齿顶高系数 ha1 = 1.0000 ha2 = .8000顶隙系数 cn1 = .4000 cn2 = .2500 分度圆直径 (mm) d1 = 210.0000 d2 = 553.0000齿顶圆直径 (mm) da1 = 229.7023 da2 = 547.5620齿根圆直径 (mm) df1 = 196.0000 df2 = 570.4020基圆直径 (mm) db1 = 197.3354 db2 = 519.6500齿 顶 高 (mm) ha1 = 9.8511 ha2 = 2.7190齿 根 高 (mm) hf1 = 7.0000 hf2 = 8.7010全 齿 高 (mm) h1 = 16.8511 h2 = 11.4200节 距 (mm) pn = 21.9911法面的基圆齿距 pbn = 20.6649端面的基圆齿距 pbt = 20.6649法面压力角 () n = 20.0000端面压力角 () t = 20.0000端面啮合角 () tp= 18.5611基圆螺旋角 () b = .0000法向齿厚 (mm) sn = 10.996分度圆弦齿厚 (mm) Sn1 = 13.0254 Sn2 = 10.0116分度圆弦齿高 (mm) hn1 = 10.0533 hn2 = 2.7031公法线长度 (mm) Wnk1= 77.1837 Wnk2= 204.9859跨 齿 数 K1 = 4 K2 = 10固定弦齿厚 (mm) sc1 = 11.5091 sc2 = 8.8409固定弦齿高 (mm) hc1 = 7.7566 hc2 = 1.1395圆棒(球)直径 (mm) dp1 = 11.7600 dp2 = 11.7600跨棒(球)距 (mm) M1 = 230.3604 M2 = 539.6439齿 顶 厚 (mm) sa1 = 4.2504 sa2 = 8.0293最大滑动系数 1 = -.0384 2 = 1.5132端面重合度 epa = 1.2872纵向重合度 epb = .0000- 渐开线圆柱齿轮精度 - 小齿轮 - IQ1=6 IQ2=6 IQ3=6 FP = .0630 ff = .0130 FBT= .0160 Fr = .0450 fpt= .0160 Fb = .0160 Fi= .0760 fi= .0174 Fpx= .0160 Fpk= .0320 fpb= .0140 Fi= .0630 fi= .0220 Fw = .0250 ffB= .0174 a = 170.000 fa = .0200 6-6-6-F J GB 10095-88 Wnk1= 77.184 Ews= -.0712 Ewi= -.1393 K1 = 4 Ess= -.0640 Esi= -.1600 M1 = 230.3604 dltlM = .1655 dltuM = .3237 - 内齿圈 - IQ1=7 IQ2=7 IQ3=7 FP = .1120 ff = .0240 FBT= .0200 Fr = .0800 fpt= .0250 Fb = .0200 Fi= .1360 fi= .0294 Fpx= .0200 Fpk= .0630 fpb= .0220 Fi= .1120 fi= .0320 Fw = .0450 ffB= .0294 a = 170.000 fa = .0315 7-7-7-F J GB 10095-88 Wnk2= 204.986 Ews= .2152 Ewi= .1137 K2 =10 Ess= -.1000 Esi= -.2500 M2 = 539.6439 dltlM = .3393 dltuM = .6424-六）、齿面疲劳强度校核T=55000N.m KA=1高速级外啮合接触疲劳极限应力(MPa)Hlim = 1450.00 1450.00许用接触疲劳应力(MPa)HP = 1450.80 1450.80计算接触应力(MPa)H = 971.38 971.38接触强度安全系数SH = 1.49 1.49弯曲疲劳极限应力(MPa)Flim = 400.00 280.00许用弯曲疲劳应力(MPa)FP = 800.00 560.00计算齿根弯曲应力(MPa)F = 245.20 229.75弯曲强度安全系数SF = 3.26 2.44高速级内啮合接触疲劳极限应力(MPa)Hlim = 1450.00 750.00许用接触疲劳应力(MPa)HP = 1381.72 794.56计算接触应力(MPa)H = 414.44 414.44接触强度安全系数SH = 3.33 1.92弯曲疲劳极限应力(MPa)Flim = 280.00 255.00许用弯曲疲劳应力(MPa)FP = 560.00 510.00计算齿根弯曲应力(MPa)F = 213.26 209.17弯曲强度安全系数SF = 2.63 2.44低速级外啮合接触疲劳极限应力(MPa) Hlim = 1450.00 1450.00许用接触疲劳应力(MPa)HP = 1508.94 1508.94计算接触应力(MPa)H = 1097.35 1107.80接触强度安全系数SH = 1.38 1.36弯曲疲劳极限应力(MPa)Flim = 400.00 280.00许用弯曲疲劳应力(MPa)FP = 857.60 600.3