二级圆柱齿轮减速器(1)-学位论文.doc

XX学院设计说明书课 题： 二级圆柱斜齿齿轮减速器 子课题: 同课题学生姓名: 专 业 学生姓名 班 级 学 号 指导教师 完成日期 二级圆柱斜齿齿轮减速器摘要 减速器是各类机械设备中广泛应用的传动装置。减速器设计的优劣直接影响机械设备的传动性能。 减速器是原动机和工作机之间的独立的闭式传动装置，用来降低转速和增大转矩，以满足工作需要，在某些场合也用来增速，称为增速器。选用减速器时应根据工作机的选用条件，技术参数，动力机的性能，经济性等因素，比较不同类型、品种减速器的外廓尺寸，传动效率，承载能力，质量，价格等，选择最适合的减速器。 减速器的类别、品种、型式很多，目前已制定为行（国）标的减速器有40余种。减速器的类别是根据所采用的齿轮齿形、齿廓曲线划分；减速器的品种是根据使用的需要而设计的不同结构的减速器；减速器的型式是在基本结构的基础上根据齿面硬度、传动级数、出轴型式、装配型式、安装型式、联接型式等因素而设计的不同特性的减速器。 与减速器联接的工作机载荷状态比较复杂，对减速器的影响很大，是减速器选用及计算的重要因素，减速器的载荷状态即工作机（从动机）的载荷状态，通常分为三类：均匀载荷;中等冲击载荷;强冲击载荷。由于编者水平有限，设计中有错误与不当之处在所难免，希望大家批评指正。关键字：减速器、齿轮、轴承、联接目 录摘要························································································2一、设计任务书······································································6 一、设计题目········································································6 二、原始数据········································································6 三、设计内容和要求······························································6二、传动方案的拟定·····························································7三、电动机的选择··································································7 1.选择电动机的类型·······························································7 2.选择电动机功率···································································7 3.确定电动机转速···································································8四、传动比的计算 1. 总传动比·········································································8 2. 分配传动比······································································8五、传动装置运动、动力参数的计算1.各轴的转速············································································82.各轴功率计············································································83.各轴转矩················································································9六、 传动件的设计计算一、高速级齿轮传动的设计计算················································91.选择材料、热处理方式和公差等级·············································92.初步计算传动的主要尺寸··························································93.确定传动尺寸·········································································104.校核齿根弯曲疲劳强度·····························································115.计算齿轮传动其他几何尺寸····················································12二、低速级圆柱齿轮的设计计算1.选择材料、热处理方式和公差等级··············································122.初步计算传动的主要尺寸···························································133.确定传动尺寸···········································································154.校核齿根弯曲疲劳强度······························································165.计算齿轮传动其他几何尺寸·····················································17七、齿轮上作用力的计算·························································171.高速级齿轮传动的作用力····························································172.低速级齿轮传动的作用力····························································18八、减速器装配草图的设计······················································19九、轴的设计计算···································································19 一、高速轴的设计与计算····························································19 1.已知条件············································································19 2.选择轴的材料······································································19 3.初算轴径············································································19 4.结构设计············································································20 5.键连接················································································21 6.轴的受力分析·······································································22 7.校核轴的强度·······································································23 8.校核键连接的强度·································································23二、中间轴的设计与计算································································24 1.已知条件···············································································24 2.选择轴的材料········································································24 3.初算轴径···············································································24 4.结构设计················································································24 5.键连接···················································································25 6.轴的受力分析·········································································25 7.校核轴的强度·········································································28 8.校核键连接的强度···································································28三、低速轴的设计与计算·································································29 1.已知条件·················································································29 2.选择轴的材料···········································································29 3.初算轴径·················································································29 4.结构设计·················································································30 5.键连接····················································································31 6.轴的受力分析···········································································31 7.校核轴的强度···········································································32 8.校核键连接的强度·····································································33十、减速器箱体的结构尺寸··························································33十一、润滑油的选择与计算························································34十二、装配图和零件图································································35致谢·······························································································36参考文献························································································37一、设计任务书一、设计题目：设计二级圆柱斜齿齿轮减速器设计热处理车间零件清洗用传送设备。该传送设备的传动系统由电动机减速器运输带组成。每日二班制工作，工作期限为8年。运输带允许最大误差为。传送见图如图1所示。 （图1）二、原始数据：转矩T()传送带速度V(m/s)滚筒直径D（mm）使用年限（年）10000.6330010三、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；（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。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）零件工作图二张（输出轴及该轴上的齿轮），图号自定，比例11。（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）1-带传动 2-电动机 3-减速器 4-联轴器 5-输送带 6-输送带 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。减速器为展开式圆柱齿轮的二级传动，轴承初步选用深沟球轴承。三、电动机的选择电动机的选择见表1计算项目计算及说明计算结果1.选择电动机的类型根据用途选用Y系列三相异步电动机 2.选择电动机功率 输送带所需拉力为 输送带功率为 查表2-1取，带传动效率带=0.96，一对轴承效率轴承=0.99，斜齿齿轮传动效率直齿=0.97，联轴器效率联=0.99，得电动机到工作机间的总效率为总=带4轴承2直齿联=0.96*0.994*0.972*0.99=0.859 电动机所需工作效率为 P0= Pw/总=4.2/0.859 Kw=4.89Kw 根据表8-2选取电动机的额定工作功率为Ped=5.5KwF=6667NPw=4.2Kw总=0.859 P0=4.89KwPed=5.5Kw 3.确定电动机转速输送带带轮的工作转速为 由表2-2可知带传动传动比i带=24，两级减速器传动比i齿=840，则总传动比范围为 i总=i锥i齿=（24）*（840）=16160电动机的转速范围为n0=nwi总=40.13*(16160)r/min=642.16421r/min 由表8-2知，符合这一要求的电动机同步转速有1000r/min、1500r/min和3000r/min，考虑到3000r/min的电动机转速太高，但1000r/min的电动机体积大且价格贵，所以本例选用1500r/min的电动机，其满载转速为1440r/min,其型号为Y132S-4nw=40.13r/minnm=1440r/min四、传动比的计算及分配传动比的计算及分配见表2计算项目计算及说明计算结果1.总传动比i总=nm/nw=1440/40.13=35.88i总=35.882.分配传动比根据传动比范围，取带传动的传动比i带=2.5，则减速器传动比为 高速级传动比为，取低速级传动比为 i2=i/i1=14.35/4.4=3.26i=14.35i1=4.4i2=3.26五、传动装置运动、动力参数的计算传动装置运动、动力参数的计算见表3计算项目计算及说明计算结果1.各轴转速n0=nm=1440r/minn1=n0/i带=1440/2.5=576r/minn2=n1/i1=576/4.4r/min=130.9r/minn3=n2/i2=130.9/3.26r/min=40.15r/minnw=n3=40.15r/minn0=1440r/minn1=576r/minn2=130.9r/minnw=n3=40.15r/min2.各轴功率p1=p0带=4.89*0.96kw=4.69kwP2=p11-2=p1轴承齿=4.69*0.99*0.97kw=4.50kwP3=p22-3=p2轴承齿=4.50*0.99*0.97kw4.32kwPw=p33-w=p3轴承联=4.32*0.99*0.99kw=4.23kwp1=4.69kwP2=4.50kwP3=4.32kwPw=4.23kw3.各轴转矩T0=9550p0/n0=9550*4.89/1440N·mm=32.43N·mT1=9550p1/n1=9550*4.69/576N·mm=77.76N·m T2=9550p2/n2=9550*4.50/130.9N·mm=328.30N·mT3=9550p3/n3=9550*4.32/40.15N·mm=1027.55N·mTw=9550pw/nw=9550*4.23/40.15N·mm=1006.14N·mT0=32.43N·mT1=77.76N·mT2=328.30N·mT3=1027.55N·mTw=1006.14N·m六、 传动件的设计计算一、减速器外传动件的设计减速器外传动只有带传动，故只需对待传动进行设计。带传动的设计计算见表4计算项目计算及说明计算结果1.确定设计功率 由表8-6，查得工作情况系数，则 2. 选择带型n0=1440r/min，由图8-2选择A型V带选择A型V带3.确定带轮基准直径根据表8-7，选小带轮直径为，则大带轮直径为4.验算带的速度带速符合要求5.确定中心距和V带长度根据，初步确定中心距，即为使结构紧凑，取偏低值，V带计算基准长度为由表8-8选V带基准长度，则实际中心距为6.计算小带轮包角合格7.确定V带根数V带的根数可用下式计算：由表8-9查取单根V带所能传递的功率P0=1.3kw,功率增量 由表8-10查得，由表8-11查得，则由表8-12查得，由表8-8查得,则带的根数为取5根Z=58.计算初拉力由表8-13查得V带质量，则初拉力为9.计算作用在轴上的压力10.带轮结构设计（1）小带轮结构 采用实心式，由表8-14查电动机轴径，由表8-15查得轮毂宽：其最终宽度结合安装带轮的轴段确定轮缘宽：（2）大带轮结构 采用孔板式结构，轮缘宽可与小带轮相同，轮毂宽可与轴的结构设计同步进行二、减速器内传动的设计计算高速级斜齿圆柱齿轮的设计计算见表5 计算项目计算及说明计算结果1.选择材料、热处理方式和公差等级 考虑到带式运输机为一般机械，大、小锥齿轮均选用45钢，小齿轮调质处理，大齿轮正火处理，由表8-17得齿面硬度HBW1=217255，HBW2=162217.平均硬度HBW1=236，HBW2=190.HBW1-HBW2=46.在3050HBW之间。选用8级精度。45钢小齿轮调质处理大齿轮正火处理8级精度2.初步计算传动的主要尺寸因为是软齿面闭式传动，故按齿面接触疲劳强度进行设计。其设计公式为d11) 小齿轮传递转矩为T1=77760·2) 因v值未知，Kv值不能确定，可初步选载荷系数Kt=1.43) 由表8-19，查得弹性系数ZE=189.84) 直齿轮，由图9-2查得节点区域系数ZH=2.465) 齿数比=i1=4.46) 取齿宽系数=1.17) 初选Z1=23,则Z2=23*4.4=101.2，取Z2=101，则端面重合度为轴向重合度为由图8-3查得重合度系数8) 由图11-2查得螺旋角系数9) 许用接触应力可用下式公式 由图8-4e、a查得接触疲劳极限应力为 小齿轮与大齿轮的应力循环次数分别为N1=60n1aLh=60*576*1*2*8*250*8=1.106*109N2=N1/i1=1.106*109/4.4=2.51*108由图8-5查得寿命系数ZN1=1，ZN2=1.14；由表8-20取安全系数SH=1，则有取 初算小齿轮的分度圆直径d1t,有d1tmm=53.99mm d1t53.99mm3.确定传动尺寸（1）计算载荷系数 由表8-1查得使用系数KA=1.0 因， 由图8-6降低1级精度，按9级精度查得动载荷系数Kv=1.15，由图8-7查得齿向载荷分配系数Kß=1.12，由表8-22查得齿间载荷分配系数，则载荷系数(2） 对d1t进行修正 因K与Kt有较大的差异，故需对Kt计算出的d1t进行修正 ，即 d1=53.99=55.85mm（3） 大端模数m ，查表8-23，取标准模数m=2.5mm（4） 计算传动尺寸 中心距为 取整，则螺旋角为因值与初选值相差较大，故对与有关的参数进行修正由图9-2查的节点区域系数，则端面重合度为 轴向重合度为 由图8-3查得重合度系数，由图11-2查得螺旋角系数 d1t =55.22mm精计算圆周速度为 由图8-6查得动载荷系数Kv=1.15，K值不变 按表8-23，取,则高速级中心距为则螺旋角修正为修正完毕（5） 大端分度圆直径为 （6）齿宽为 b=1.1*59.355mm=65.29mm 取b2=66mm，取b1=75mmK=1.55 d1=55.85mm m=2.5mmd1=59.355mmd2=260.545mmb2=66mmb1=75mm4.校核齿根弯曲疲劳强度 齿根弯曲疲劳强度条件为 （1） K、T1、mn和d1同前 （2） 齿宽（3） 齿形系数YF和应力修正系数YS 即当量齿数为 由图8-8查得YF1=2.61,YF2=2.22由图8-9查得YS1=1.59，YS2=1.81（4） 由图8-10查得重合度系数（5） 由图11-3查得螺旋角系数（6） 许用弯曲应力 由图8-11查得寿命系数YN1=YN2=1,由表8-20查得安全系数SF=1.25，故 =满足齿根弯曲强度5.计算锥齿轮传动其他几何尺寸端面模数 m1=齿顶高 ha=mn=2.5mm齿根高 hf=1.25mn=1.25*2.5mm=3.125mm顶隙 C=0.25m=0.25*2.5mm=0.625mm全齿高 h=ha+hf=2.5+3.125mm=5.625mm齿顶圆直径为da1=d1+2ha=59.355+2*2.5mm=61.355mmda2=d2+2ha=260.645+2*2.5mm=265.645mm齿根圆直径为df1=d1-2hf=59.355-2*3.125mm=53.105mmdf2=d2-2hf=260.645-2*3.125mm=254.395mmm1=2.58mmha=2.5mmhf=3.125mmC=0.625mmh=5.625mmda1=61.355mmda2=265.645mmdf1=53.105mmdf2=254.395mm 二、低速级斜齿圆柱齿轮的设计计算 低速级斜齿圆柱齿轮的设计计算见表6计算项目计算及说明计算结果1.选择材料、热处理方式和公差等级 考虑到带式运输机为一般机械，大、小锥齿轮均选用45钢，小齿轮调质处理，大齿轮正火处理，由表8-17得齿面硬度HBW1=217255，HBW2=162217.平均硬度HBW1=236，HBW2=190.HBW1-HBW2=46.在3050HBW之间。选用8级精度。45钢小齿轮调质处理大齿轮正火处理8级精度2.初步计算传动的主要尺寸因为是软齿面闭式传动，故按齿面接触疲劳强度进行设计。其设计公式为d11) 小齿轮传递转矩为T2=328300·2) 因v值未知，Kv值不能确定，可初步选载荷系数Kt=1.43)由表8-19，查得弹性系数ZE=189.84)初选螺旋角，由图9-2查得节点区域系数ZH=2.465)齿数比=i2=3.266)取齿宽系数=1.17)初选Z3=25,则Z4=25*3.26=81.5，取Z4=82，则端面重合度为轴向重合度为8)由图8-3查得重合度系数9)由图11-2查得螺旋角系数10) 许用接触应力可用下式公式 由图8-4e、a查得接触疲劳极限应力为 小齿轮与大齿轮的应力循环次数分别为N3=60n2aLh=60*130.9*1*2*8*250*8=2.513*108N4=N1/i2=2.513*108/3.26=7.71*107由图8-5查得寿命系数ZN3=1.14，ZN2=1.2；由表8-20取安全系数SH=1，则有取 初算小齿轮的分度圆直径d1t,有d3tmm=89.62mm d3t89.62mm3.确定传动尺寸（1）计算载荷系数 由表8-1查得使用系数KA=1.0 因， 由图8-6降低1级精度，按9级精度查得动载荷系数Kv=1.07，由图8-7查得齿向载荷分配系数Kß=1.11，由表8-22查得齿间载荷分配系数，则载荷系数（5)大端模数m ，查表8-23，取标准模数m=3.5mm（6） 计算传动尺寸 中心距为 取整，则螺旋角为因值与初选值相差大，故对与有关的参数不用进行修正（7） 大端分度圆直径为 （6）齿宽为 b=1.1*88.785mm=97.67mm 取b4=98mm，取b1=105mmK=1.43 m=3.5mmd3=88.785mmd4=291.215mmb4=98mmb3=105mm4.校核齿根弯曲疲劳强度 齿根弯曲疲劳强度条件为 （1）K、T1、mn和d3同前 （2）齿宽（3）齿形系数YF和应力修正系数YS 即当量齿数为 由图8-8查得YF3=2.6,YF4=2.25,由图8-9查得YS3=1.58，YS4=1.79（4）由图8-10查得重合度系数（5）由图11-3查得螺旋角系数（6）许用弯曲应力 由图8-11查得寿命系数YN1=YN2=1,由表8-20查得安全系数SF=1.25，故 =满足齿根弯曲强度5.计算齿轮传动其他几何尺寸端面模数 m1=齿顶高 ha=mn=3.5mm齿根高 hf=1.25mn=1.25*3.5mm=4.375mm顶隙 C=0.25m=0.25*3.5mm=0.875m全齿高 h=ha+hf=3.5+4.375mm=7.875mm齿顶圆直径为da3=d3+2ha=88.785+2*3.5mm=95.785mmda4=d4+2ha=291.215+2*3.5mm=298.215mm齿根圆直径为df3=d3-2hf=88.785-2*4.375mm=80.035mmdf4=d4-2hf=291.215-2*4.375mm=282.465mmm1=3.55mmha=3.5mmhf=4.375mmC=0.875mmh=7.875mmda3=95.785mmda4=298.215mmdf3=80.035mmdf4=282.465mm七、齿轮上作用力的计算齿轮上作用力的计算为后续轴的设计和校核、键的选择和验算及轴承的选择和校核提供数据，其计算过程见表6计算项目计算及说明计算结果1.高速级齿轮传动的作用力（1）已知条件 高速轴传递的转矩T1=77760Nmm，转速n1=576r/min，高速级齿轮的螺旋角，