减速器减速器锥柱二级传动

机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器-1-目录一、设计任务书·········································································2二、电机的选择计算一、择电机的转速································································2二、工作机的有效功率···························································2三、选择电动机的型号···························································3三、运动和动力参数的计算一、分配传动比·····································································3二、各轴的转速·····································································3三、各轴的功率·····································································4四、各轴的转矩·····································································4四、传动零件的设计计算1.闭式直齿轮圆锥齿轮传动的设计计算········································42.闭式直齿轮圆柱齿轮传动的设计计算········································6五、轴的设计计算1.减速器高速轴I的设计······················································92.减速器低速轴II的设计·················································113.减速器低速轴III的设计·······················································14六、滚动轴承的选择与寿命计算1.减速器高速I轴滚动轴承的选择与寿命计算·······························162.减速器低速II轴滚动轴承的选择与寿命计算······························173.减速器低速III轴滚动轴承的选择与寿命计算···························18七、键联接的选择和验算1.联轴器与高速轴轴伸的键联接··········································192.大圆锥齿轮与低速轴II的的键联接·········································193.大圆柱齿轮与低速轴III的的键联接·····························20机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器-2-八、润滑油的选择与热平衡计算1.减速器的热平衡计算·····························································212.润滑油的选择·····································································22九、参考文献····························································23机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器-3-计算及说明结果一、设计任务书班级机械0402学号200406010219姓名郑利江一、设计题目：设计圆锥—圆柱齿轮减速器设计铸工车间的型砂运输设备。该传送设备的传动系统由电动机—减速器—运输带组成。每日二班工作。（图1）1—电动机；2联轴器；3—减速器；4—鼓轮；5—传送带二、原始数据：传送带拉力F(KN)传送带速度V(m/s)鼓轮直径D（mm）使用年限（年）1.7701.3922357三、设计内容和要求：1.编写设计计算说明书一份，其内容通常包括下列几个方面：（1）传动系统方案的分析和拟定以及减速器类型的选择；（2）电动机的选择与传动装置运动和动力参数的计算；（3）传动零件的设计计算（如除了传动，蜗杆传动，带传动等）；（4）轴的设计计算；（5）轴承及其组合部件设计；（6）键联接和联轴器的选择及校核；（7）减速器箱体，润滑及附件的设计；（8）装配图和零件图的设计；（9）校核；（10）轴承寿命校核；（11）设计小结；（12）参考文献；（13）致谢。机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器-4-计算及说明结果2.要求每个学生完成以下工作：（1）减速器装配图一张（0号或一号图纸）（2）零件工作图两张（输出轴及该轴上的大齿轮），图号自定，比例1︰1。（3）设计计算说明书一份。二、传动方案的拟定运动简图如下：（图2）由图可知，该设备原动机为电动机，传动装置为减速器，工作机为型砂运输设备。减速器为展开式圆锥—圆柱齿轮的二级传动，轴承初步选用深沟球轴承。联轴器2选用凸缘联轴器，8选用齿形联轴器。机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器-5-计算及说明结果三、电动机的选择及传动装置的运动和动力参数计算一、选择电动机的类型和结构形式按工作要求和条件，选用三相笼型异步电动机，Y系列，封闭式结构，电压380V，频率50Hz。二、选择电动机容量工作机主动轴功率：w1.7701.3922.464wPFVK传动装置的总效率：24a12345（式中1、2、3、4、5分别为联轴器、滚动轴承、原锥齿轮传动、圆柱齿轮传动和卷筒的传动效率。）取1=0.99（联轴器），2=0.985（滚动轴承），3=0.96（齿轮精度为8级，不包括轴承效率），4=0.97（齿轮精度为8级，不包括轴承效率），5=0.96（卷筒效率，不包括轴承）则24a0.990.9850.960.970.960.825电动机所需功率：wda2.464ww2.987w0.825PPKKK三、确定电动机的转速卷筒州的工作转速为：6010006010001.392rr113.2minmin235VnD按课程设计指导书P7—表1查得圆锥—圆柱齿轮的传动比一般范围为：ai=10~25，故电动机转速机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器-6-计算及说明结果''(10~25)113.21132~2830mindarnin根据额定功率edP≥dP，且转速满足1132minmindrrn，选电动机型号为：Y100L2-4。其主要性能如下表：型号额定功率Kw满载时起动电流额定电流起动转矩额定转矩最大转矩额定转矩转速rmin电流（380V）A效率%功率因数Y100L2-4314206.882.50.817.02.22.3电动机的外形尺寸：中心高H外形尺寸L×(AC/2+AD)×HD底角安装尺寸A×B地脚螺栓孔直径K轴伸尺寸D×E装键部位尺寸F×GD100380×288×245160×1401228×608×31四、确定传动装置的总传动比和分配传动比1.总传动比总传动比142012.544113.2manin2.分配减速器的各级传动比直齿轮圆锥齿轮传动比按直齿轮圆柱齿轮传动比0.250.2512.5443.136aii锥，又锥齿轮的传动比一般不大于3，故取i锥=3则12.5444.183i柱实际总传动比34.1812.54iii锥柱实0.004i，满足要求。机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器-7-计算及说明结果五、计算传动装置的运动和动力参数1.各轴的转速（各轴的标号均已在图2中标出）1420minmrnn1420473.333minnrni锥473.33113.24.18minnrni柱113.2minrnn卷筒轴2.各轴的输出、输入功率12.9870.992.957132.957dPPKw入22.9570.9852.9126452.913PPKw入出32.9130.962.796482.796PPKw入出22.7960.9852.754062.754PPKw入出42.7540.972.671382.671PPKw入出22.6710.9852.6309352.631PPKw入出12.6310.992.604692.605PPKw出卷筒轴入252.6050.9850.96PP卷筒轴出卷筒轴入2.6432882.643KwKw3.各轴输入、输出转矩955095502.98720.091420ddmPTNmn机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器-8-计算及说明结果955095502.95719.891420955095502.91319.591420955095502.79656.41473.33955095502.75455.57473.33955095502.671225.34113.2PTNmnPTNmnPTNmnPTNmnPTn入入出出入入出出入入955095502.631221.96113.2955095502.605219.77113.2955095502.463207.79113.2NmPTNmnPTNmnPTNmn出出卷筒轴入卷筒轴入卷筒轴卷筒轴出卷筒轴出卷筒轴运动和动力参数计算结果整理于下表：轴名效率P(Kw)转矩（Nm）转速nr/min传动比i效率输入输出输入输出电动机轴2.98720.0914201.00.99Ⅰ轴2.9572.91319.8919.5914203.00.95Ⅱ轴2.7962.75456.4155.57473.334.20.96Ⅲ轴2.6712.631225.34221.96113.21.00.97卷筒轴2.6052.463219.77207.79113.2机械设计课程设计计算说明书——圆锥—圆柱齿轮减速器-9-计算及说明结果四、传动零件的设计计算一、圆锥齿轮传动的设计计算已知输入功率12.957PKw（略大于小齿轮的实际功率），小齿轮的转速为：11720minrn，大齿轮的转速为2437.33minrn，传动比3i，由电动机驱动，工作寿命（设每年工作300天），两班制，带式输送，平稳，转向不变。1.选定齿轮类型、精度等级、材料及齿数（1）按传动方案，选用直齿圆锥齿轮传动，齿形制11060JB,齿形角20，齿顶高系数*1ah，顶隙系数*0.2c，螺旋角0m，不变位。（2）、运输机为一般工作机器，速度不高，故选用8级精度。（3）、材料选择，小齿轮材料为40Cr（调质），硬度为280HBS，大齿轮材料为45刚（调质），硬度为240HBS，二者材料硬度相差40HBS。（4）、选小齿轮齿数12123,32369zzuz则2.按齿面接触疲劳强度设计公式：1td≥32122.92(10.5)EFRRZKTu（1）、确定公式内的各计算值1）查得材料弹性影响系数12189.8EZMPa。2）按齿面的硬度查得小齿轮的接触疲劳强度极限lim1600