二级展开式圆柱齿轮减速器——斜齿轮(南京林业大学课程设计)

机械设计课程设计计算说明书题目：二级展开式圆柱齿轮减速器学院：机械电子工程学院专业：机械设计制造及其自动化设计者：刘＊＊指导老师：涂桥安2013年7月4日南京林业大学目录一、已知条件························································11、原始数据···································································12、工作制及寿命·······························································1二、传递方案的分析与拟定············································1三、电动机的选择计算················································11、选择电动机的类型和结构形式················································12、选择电动机的容量··························································13、确定电动机的转速··························································24、确定电动机的型号··························································2四、传动装置的运动及动力参数的选择与计算····························21、传动装置总传动比的确定和分配··············································22、传动装置运动及动力参数计算················································3五、传动零件的设计计算··············································41、带传动····································································42、圆柱齿轮传动······························································6六、轴的设计·······················································141、材料选择·································································142、确定轴的最小直径·························································143、轴的结构设计·····························································164、齿轮受力计算·····························································185、高速轴（Ⅰ轴）的强度校核·················································196、中间轴（Ⅱ轴）的强度校核·················································217、低速轴（Ⅲ轴）的强度校核·················································228、精确校核低速轴的疲劳强度·················································24七、滚动轴承的选择及校核···········································271、轴承的选择·······························································273、30206轴承计算····························································284、30207轴承计算····························································295、7210C轴承计算····························································306、轴承的润滑方式···························································32八、键的选择和强度校核·············································321、类型选择·································································322、材料选择·································································323、键型号的选择·····························································324、强度校核·································································33九、参考文献·······················································33机械设计课程设计计算说明书第1页共33页计算及说明计算结果一、已知条件1、原始数据：鼓轮直径D：300mm传送速度v：0.63/sm传送带从动轴所需的扭矩T：600Nm2、工作制及寿命：每日两班制工作，使用期限8年二、传递方案的分析与拟定为满足工作机的工作要求，且综合考虑其在结构简单、尺寸紧凑、加工方便、高传动效率、使用维护方便等方面的要求，本设计采用二级展开式圆柱齿轮减速器。传动方案简图如下：传动方案简图中各符号意义如下：1-电动机；2-带传动；3-减速器；4-联轴器；5-鼓轮；6-传送带三、电动机的选择计算1、选择电动机的类型和结构形式按工作要求和条件，选用三项笼型异步电动机，密封式结构，电压380V，Y型。2、选择电动机的容量（1）工作机所需的功率：210001000wFvTvPD（2）传动装置的总效率：2.94wPkW机械设计课程设计计算说明书第2页共33页4212345a取带传动效率：10.95；取滚动轴承效率：20.98；取齿轮传动效率：30.97；取联轴器效率：40.99；取鼓轮效率：50.96。（3）电动机容量：ddaPP3、确定电动机的转速鼓轮轴工作转速601000vnD按文献1推荐的传动比合理范围，取V带传动比1'2~4i，二级圆柱齿轮减速器传动比2'8~40i，则总传动比的范围为'16~160ai。电动机所需转速''danin4、确定电动机的型号符合'641.76~6417.6/mindnr这一范围的同步转速有1000/minr1500/minr、3000/minr三种。方案对比如下：方案电动机型号额定功率PkWed电动机转速/minnr同步转速满载转速1Y132M1-6410009602Y112M-44150014403Y132S2-2430002920由于电动机转速越高，极数越少，尺寸和重量越小，价格也越低，故应使得同步转速尽可能大。但电动机选用时，一般选用同步转速为1000/minr或1500/minr的两类，因此方案2较合理。0.78a3.77dPkW40.11/minnr'641.76~6417.6/mindnr选择Y112M-4型四、传动装置的运动及动力参数的选择与计算1、传动装置总传动比的确定和分配机械设计课程设计计算说明书第3页共33页（1）传动装置总传动比namin，nm为选定电动机的满载转速。（2）分配传动装置各级传动比0aiii，0i、i分别为带传动和减速器的传动比。为使V带传动外廓尺寸不致过大，初步取03i，则减速器的传动比为：0aiii。（3）分配减速器的各级传动比考虑润滑条件，为使两级大齿轮直径相近，由文献1图12展开式曲线查得14.1i，则21iii。2、传动装置运动及动力参数计算（1）各轴转速电机轴0mnnⅠ轴10mnniⅡ轴121nniⅢ轴232nni鼓轮轴43nn（2）各轴输入功率电机轴0edPP（edP查机械手册可得）Ⅰ轴101PPⅡ轴2123PPⅢ轴3223PP35.9ai11.97i124.1,2.92ii01440/minnr1480/minnr2117.07/minnr340.09/minnr440.09/minnr04PkW13.8PkW23.61PkW33.43PkW机械设计课程设计计算说明书第4页共33页鼓轮轴4324PP（3）各轴输入转矩电动机输出转矩：09550mnPTmⅠ轴101mTTiⅡ轴21123TTiⅢ轴32223TTi鼓轮轴4324TT（4）运动和动力参数表轴的输出功率分别为轴的输入功率乘轴承效率20.98，轴的输出转矩分别为轴的输入转矩乘轴承效率20.98，运动和动力参数列表如下：轴功率P(kW)转矩T(N·m)转速nr/min传动比i效率η输入输出输入输出电机轴426.5314403.000.95Ⅰ轴3.83.7275.6174.104804.10.95Ⅱ轴3.613.54294.69288.80117.072.920.95Ⅲ轴3.433.36817.99801.6340.091.000.97鼓轮轴3.333.26793.61777.7440.0943.33PkW26.53mTNm175.61TNm2294.69TNm3817.99TNm4793.61TNm五、传动零件的设计计算1、带传动（1）确定计算功率caP由文献2表8-7查得工作情况系数1.1aK，则0caaPKP。（2）选择V带类型4.4caPkW机械设计课程设计计算说明书第5页共33页根据caP、0n由文献2图8-10选用A型号。（3）确定带轮的基准直径dd并验算带速v①初选小带轮的基准直径dd查文献2表8-6和表8-8，取小带轮的基准直径190ddmm。②验算带速10601000ddnv，并满足5/s30/mvms③计算大带轮的基准直径201dddid，圆整后根据文献2表8-8取标准值。（4）确定V带中心距a和基准长度L①初定中心距120120.72ddddddadd0500amm②计算带所需的基准长度21200120224dddddddLadda，圆整后根据文献2表8-2取标准值。③计算实际中心距a002ddLLaa变动范围：minmax0.015,0.03ddaaLaaL（5）验算小带轮的包角112157.3180dddda（6）计算带的根数z①单根普通V带的基本额定功率0P由190ddmm和01440/minnr查文献2表8-4a可得01.064PkW。②单根普通V带额定功率的增量0P选用A型号190ddmm6.78/svm取2280ddmm00259740500mmammamm取1600dLmm5