链轮设计-实例

第一级传动主传动及二级传动链第二级传动一、链轮Z1的设计计算：1）材料选择：采用45#调质处理表面硬度40-50HRC2）分度圆直径：d=p/(sina180°/z)=19.05/(sina180°/25)=151.995(mm)3）齿顶圆直径：dadamax=d+1.25p-d1=151.995+1.25×19.05-11.91=163.8975(mm)(查表：d1=11.91)damin=d+(1-1.6/z1)p-d1=151.995+(1-1.6/25)×19.05-11.91=157.9158(mm)取da=1600-0.03(mm)4）齿根圆直径df:df=d-d1=151.995-11.91=140.085(mm)5）分度圆弦齿高：hahamax=(0.625+0.8/z1)p-0.5d1=(0.625+0.8/25)×19.05-0.5×11.91=6.561(mm)hamin=0.5(p-d1)=0.5×(19.05-11.91)=3.570(mm)取ha=4.5(mm)6）最大齿根距离：LxLx=dcos(90°/z1)-d1=151.995×cos(90°/25)-11.91=139.785(mm)7）齿侧凸缘直径：dg（查表：h为链的内连扳高度；h=18.08）dg=pcot(180°/z1)-1.04h-0.76=19.05×cot(180°/25)-1.04×18.08-0.76=131.233(mm);取dg=131mm8）齿侧圆弧半径：reremax=0.008d1(180+z12)=0.008×11.91×(180+252)=76.7004(mm)remin=0.12d1(2+z1)=0.12×11.91×(2+25)=38.5884(mm)9）滚子定位圆弧半径：ririmax=0.505d1+0.06931d=0.505×11.91+0.069×3√11.91=6.172(mm)rimin=0.505d1=0.505×11.91=6.015(mm)10）滚子定位角：ααmax=140°-90°/z1=140°-90°/25=136.4°αmin=120°-90°/z1=120°-90°/25=116.4°11）齿宽：bf1（b1内链节内宽）bf1=0.95b1=0.95×12.57=11.9415(mm)12）齿侧倒角：baba=0.13p=0.13×19.05=2.4765(mm)13）齿侧半径：rxrx=p=19.05(mm)14）齿全宽:bfm(m排数)bfm=(m-1)pt+bf1=(1-1)pt+11.9415=11.9415(mm)15）轴毂厚度：h（假设轴孔为50mm,152mm范围内取值）h=K+dk/6+0.01d=9.5+dk/6+0.01×151.995=19.353(mm)16）轮毂长度：llmax=3.3h=3.3×19.353=63.866(mm)lmin=2.6h=2.6×19.353=50.319(mm)17）轮毂直径：dhdh=dk+2h=50+2×19.353=88.706(mm)二、Z1对应轴的设计计算1)材料选45#，30Mp(空心轴)2)按需用应力计算轴的直径:d(T=9550P/n=9550×0.24/30=76.4(Nm),M=考虑链传动在轴上产生的弯矩)3][5Td3411v=2.648×1.3=3.5(mm)3411v查表得1.3。取轴颈直径40mm，空心孔内径do=40×0.85=34(mm)3)按弯扭矩合成强度计算轴径：3431221168.21pTMd=47.430×1.279=60.66（mm）,显然采用合成算法更准确。4)若采用实心轴则：312268.21pTMd=47.430(mm),取d=50mm5)根据以上计算结果采用空心轴，又轴上有键槽，则d=60.66×1.1=66.728,取值为d=70则do=70×0.85=59.56)对一反求链轮轴孔dk=70mm，则轴毂厚度h：h=K+dk/6+0.01d=9.5+70/6+0.01×151.995=22.687(mm)轮毂长度l：lmax=3.3h=3.3×22.687=74.867(mm);lmin=2.6h=2.6×22.687=58.986(mm)；取中间值l=65mm轮毂直径dh：dh=dk+2h=70+2×22.687=115.347(mm)三、链轮Z2的设计计算：1）材料选择：采用45#调质处理表面硬度40-50HRC2）分度圆直径：d=p/(sina180°/z)=19.05/(sina180°/62)=376.117(mm)3）齿顶圆直径：dadamax=d+1.25p-d1=376.117+1.25×19.05-11.91=388.020(mm)(查表：d1=11.91)damin=d+(1-1.6/z2)p-d1=376.117+(1-1.6/62)×19.05-11.91=382.765(mm)取da=385(mm)公差h114）齿根圆直径df:df=d-d1=388.020-11.91=376.110(mm)5）分度圆弦齿高：hahamax=(0.625+0.8/z2)p-0.5d1=(0.625+0.8/62)×19.05-0.5×11.91=6.197(mm)hamin=0.5(p-d1)=0.5×(19.05-11.91)=3.570(mm)取ha=5(mm)6）最大齿根距离：LxLx=dcos(90°/z2)-d1=388.020×cos(90°/62)-11.91=375.985(mm)7）齿侧凸缘直径：dg（查表：h为链的内连扳高度；h=18.08）dg=pcot(180°/z2)-1.04h-0.76=19.05×cot(180°/62)-1.04×18.08-0.76=356.071(mm)8）齿侧圆弧半径：reremax=0.008d1(180+z22)=0.008×11.91×(180+622)=383.407(mm)remin=0.12d1(2+z2)=0.12×11.91×(2+62)=91.469(mm)9）滚子定位圆弧半径：ririmax=0.505d1+0.06931d=0.505×11.91+0.069×3√11.91=6.172(mm)rimin=0.505d1=0.505×11.91=6.015(mm)10）滚子定位角：ααmax=140°-90°/z2=140°-90°/62=138.548°αmin=120°-90°/z2=120°-90°/25=118.548°11）齿宽：bf1（b1内链节内宽）bf1=0.95b1=0.95×12.57=11.9415(mm)12）齿侧倒角：baba=0.13p=0.13×19.05=2.4765(mm)13）齿侧半径：rxrx=p=19.05(mm)14）齿全宽:bfm(m排数)bfm=(m-1)pt+bf1=(1-1)pt+11.9415=11.9415(mm)15）轴毂厚度：h（假设轴孔为50mm,152mm范围内取值）h=K+dk/6+0.01d=9.5+dk/6+0.01×388.020=19.353(mm)16）轮毂长度：llmax=3.3h=3.3×19.353=63.866(mm)lmin=2.6h=2.6×19.353=50.319(mm)17）轮毂直径：dhdh=dk+2h=50+2×19.353=88.706(mm)四、Z2对应轴的设计计算7)材料选45#，30Mp(空心轴)8)按需用应力计算轴的直径:d(T=9550P/n=9550×0.24/30=76.4(Nm),M=考虑链传动在轴上产生的弯矩)3][5Td3411v=2.648×1.3=3.5(mm)3411v查表得1.3。取轴颈直径40mm，空心孔内径do=40×0.85=34(mm)9)按弯扭矩合成强度计算轴径：3431221168.21pTMd=47.430×1.279=60.66（mm）,显然采用合成算法更准确。10)若采用实心轴则：312268.21pTMd=47.430(mm),取d=50mm11)根据以上计算结果采用空心轴，又轴上有键槽，则d=60.66×1.1=66.728,取值为d=70则do=70×0.85=59.512)对一反求链轮轴孔dk=70mm，则轴毂厚度h：h=K+dk/6+0.01d=9.5+70/6+0.01×388.020=22.687(mm)轮毂长度l：lmax=3.3h=3.3×22.687=74.867(mm);lmin=2.6h=2.6×22.687=58.986(mm)；取中间值l=65mm轮毂直径dh：dh=dk+2h=70+2×22.687=115.347(mm)