2023年二级圆锥斜齿圆柱齿轮减速器.doc

设计阐明书课 题： 二级圆锥-圆柱齿轮减速器 子课题： 同课题学生姓名： 专 业 机电一体化 学生姓名 黄友金 班 级 学 号 指引教师 完毕日期 3月 二级圆锥-圆柱齿轮减速器摘要 减速器是各类机械设备中广泛应用传动装置。减速器设计优劣直接影响机械设备传动性能。 减速器是原动机和工作机之间独立闭式传动装置，用来减少转速和增大转矩，以满足工作需要，在某些场合也用来增速，称为增速器。选用减速器时应依照工作机选用条件，技术参数，动力机性能，经济性等因素，比较不同类型、品种减速器外廓尺寸，传动效率，承载能力，质量，价格等，选取最适合减速器。 减速器类别、品种、型式诸多，当前已制定为行（国）标减速器有40余种。减速器类别是依照所采用齿轮齿形、齿廓曲线划分；减速器品种是依照使用需要而设计不同构造减速器；减速器型式是在基本构造基本上依照齿面硬度、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不同特性减速器。 与减速器联接工作机载荷状态比较复杂，对减速器影响很大，是减速器选用及计算重要因素，减速器载荷状态即工作机（从动机）载荷状态，普通分为三类：均匀载荷;中档冲击载荷;强冲击载荷。 本文重要二级圆锥-圆柱齿轮减速器设计，设计中存在局限性请人们予以意见和建议。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、设计内容和规定······························································6二、传动方案拟定·····························································7三、电动机选取··································································7 1.选取电动机类型·······························································7 2.选取电动机功率···································································7 3.拟定电动机转速···································································8四、传动比计算 1. 总传动比·········································································8 2. 分派传动比······································································8五、传动装置运动、动力参数计算1.各轴转速············································································82.各轴功率计············································································83.各轴转矩················································································9六、传动件设计计算一、高速级锥齿轮传动设计计算················································91.选取材料、热解决方式和公差级别·············································92.初步计算传动重要尺寸··························································93.拟定传动尺寸·········································································104.校核齿根弯曲疲劳强度·····························································115.计算锥齿轮传动其她几何尺寸····················································12二、低速级斜齿圆柱齿轮设计计算1.选取材料、热解决方式和公差级别··············································122.初步计算传动重要尺寸···························································133.拟定传动尺寸···········································································154.校核齿根弯曲疲劳强度······························································165.计算锥齿轮传动其她几何尺寸·····················································17七、齿轮上作用力计算·························································171.高速级齿轮传动作用力····························································172.低速级齿轮传动作用力····························································18八、减速器装配草图设计······················································19九、轴设计计算···································································19 一、高速轴设计与计算····························································19 1.已知条件············································································19 2.选取轴材料······································································19 3.初算轴径············································································19 4.构造设计············································································20 5.键连接················································································21 6.轴受力分析·······································································22 7.校核轴强度·······································································23 8.校核键连接强度·································································23二、中间轴设计与计算································································24 1.已知条件···············································································24 2.选取轴材料········································································24 3.初算轴径···············································································24 4.构造设计················································································24 5.键连接···················································································25 6.轴受力分析·········································································25 7.校核轴强度·········································································28 8.校核键连接强度···································································28三、低速轴设计与计算·································································29 1.已知条件·················································································29 2.选取轴材料···········································································29 3.初算轴径·················································································29 4.构造设计·················································································30 5.键连接····················································································31 6.轴受力分析···········································································31 7.校核轴强度···········································································32 8.校核键连接强度·····································································33十、润滑油选取与计算························································33十一、装配图和零件图································································34参照文献························································································35一、设计任务书一、设计题目：设计圆锥圆柱齿轮减速器设计铸工车间型砂运送设备。该传送设备传动系统由电动机减速器运送带构成。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）60000.930010三、设计内容和规定：1. 编写设计计算阐明书一份，其内容普通涉及下列几种方面：（1）传动系统方案分析和拟定以及减速器类型选取；（2）电动机选取与传动装置运动和动力参数计算；（3）传动零件设计计算（如除了传动，蜗杆传动，带传动等）；（4）轴设计计算；（5）轴承及其组合部件设计；（6）键联接和联轴器选取及校核；（7）减速器箱体，润滑及附件设计；（8）装配图和零件图设计；（9）校核；（10）轴承寿命校核；（11）设计小结；（12）参照文献；（13）道谢。2. 规定每个学生完毕如下工作：（1）减速器装配图一张（0号或一号图纸）（2）零件工作图三张（输出轴及该轴上大齿轮），图号自定，比例11。（3）设计计算阐明书一份。二、传动方案拟定运动简图如下：（图2）由图可知，该设备原动机为电动机，传动装置为减速器，工作机为型砂运送设备。减速器为展开式圆锥圆柱齿轮二级传动，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。三、电动机选取电动机选取见表1计算项目计算及阐明计算成果1.选取电动机类型依照用途选用Y系列三相异步电动机 2.选取电动机功率 输送带功率为 Pw=Fv/1000=6000*0.9/1000 Kw=5.4Kw 查表2-1，取一对轴承效率轴承=0.99，锥齿轮传动效率锥齿轮=0.96，斜齿圆柱齿轮传动效率齿轮=0.97，联轴器效率联=0.99，得电动机到工作机间总效率为总=4轴承锥齿轮齿轮2联=0.994*0.96*0.97*0.992=0.88 电动机所需工作效率为 P0= Pw/总=5.4/0.88 Kw=6.1Kw 依照表8-2选用电动机额定工作功率为Ped=7.5KwPw=5.4Kw总=0.88 P0=6.1KwPed=7.5Kw 3.拟定电动机转速输送带带轮工作转速为 nw=(1000*60V)/d=1000*60*0.9/*300r/min=57.32r/min由表2-2可知锥齿轮传动传动比i锥=23，圆柱齿轮传动传动比i齿=36，则总传动比范畴为 I总=i锥i齿=23*(36)=618电动机转速范畴为n0=nwI总57.32*(618)r/min=343.921031.76r/min 由表8-2知，符合这一规定电动机同步转速有750r/min和1000r/min，考虑到1000r/min接近其上限，因此本例选用750r/min电动机，其满载转速为720r/min,其型号为Y160L-8nw=57.32r/minnm=720r/min四、传动比计算及分派传动比计算及分派见表2计算项目计算及阐明计算成果1.总传动比i=nm/nw=720/57.32=12.56i=12.562.分派传动比高速级传动比为 i1=0.25i=0.25*12.56=3.14为使大锥齿轮不致过大，锥齿轮传动比尽量不大于3，取i1=2.95低速级传动比为 i2=i/i1=12.56/2.95=4.26i1=2.95i2=4.26五、传动装置运动、动力参数计算传动装置运动、动力参数计算见表3计算项目计算及阐明计算成果1.各轴转速n0=720r/minn1=n0=720r/minn2=n1/i1=720/2.95r/min=244.07r/minn3=n2/i2=244.07/4.26r/min=57.29r/minnw=n3=57.29r/minn1=n0=720r/minn2=244.07r/minnw=n3=57.29r/min2.各轴功率p1=p0联=6.1*0.99kw=6.04kwP2=p11-2=p1轴承锥齿=3.28*0.99*0.96kw=5.74kwP3=p22-3=p2轴承直齿=5.74*0.99*0.97kw=5.51kwPw=p33-w=p3轴承联=5.51*0.99*0.99kw=5.4kwp1=6.04kwP2=5.74kwP3=5.51kwPw=5.4kw3.各轴转矩T0=9550p0/n0=9550*6.1/720N·mm=80.91N·mmT1=9550p1/n1=9550*6.04/720N·mm=80.11N·mmT2=9550p2/n2=9550*5.74/244.07N·mm=224.6N·mmT3=9550p3/n3=9550*5.51/57.29N·mm=918.41N·mmTw=9550pw/nw=9550*54/57.29N·mm=900.16N·mmT0=80.91N·mmT1=80.11N·mmT2=224.6N·mmT3=918.41N·mmTw=900.16N·mm六、 传动件设计计算 一、高速级锥齿轮传动设计计算锥齿轮传动设计计算见表4 计算项目计算及阐明计算成果1.选取材料、热解决方式和公差级别 考虑到带式运送机为普通机械，大、小锥齿轮均选用45钢，小齿轮调质解决，大齿轮正火解决，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钢小齿轮调质解决大齿轮正火解决8级精度2.初步计算传动重要尺寸由于是软齿面闭式传动，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=80110·2) 因v值未知，Kv值不能拟定，可初步选载荷系数Kt=1.33) 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=2.55) 齿数比=i=2.956) 取齿宽系数=0.37) 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 小齿轮与大齿轮应力循环次数分别为N1=60n1aLh=60*720*1*2*8*250*10=1.728*109N2=N1/i1=1.728*109/2.95=5.858*108由图8-5查得寿命系数ZN1=1，ZN2=1.05；由表8-20取安全系数SH=1，则有取 初算小齿轮分度圆直径d1t,有 d1t=d1t100.96mm3.拟定传动尺寸（1）计算载荷系数 由表8-1查得使用系数KA=1.0，齿宽中点分度圆直径为 Dm1t=d1t(1-0.5)=100.96*(1-0.5*0.3)mm=85.82mm故vm1=dm1tn1/60*100=*85.82*720/60*100m/s=3.23m/s由图8-6减少1级精度，按9级精度查得动载荷系数Kv=1.24，由图8-7查得齿向载荷分派系数Kß=1.13，则载荷系数K=KAKvKß=1.0*1.24*1.13=1.4(2） 对d1t进行修正 因K与Kt有较大差别，故需对Kt计算出d1t进行修正 ，即 d1=100.96=103.49mm（3） 拟定齿数 选齿数Z1=23，Z2=uZ1=2.95*23=67.85，取Z2=68,则u´=68/63=2.96,在允许范畴内（4） 大端模数m ，查表8-23，取原则模数m=5mm（5） 大端分度圆直径为 d1=mZ1=5*23mm=115mm>103.49 d2=mZ2=5*68mm=340mm(6) 锥齿距为 R=（7） 齿宽为 b=0.3*179.65mm=53.895mm取b=55mm d1=103.49mm Z1=23 Z2=68m=5mmd1=115mmd2=340mm R=179.65mmb=55mm4.校核齿根弯曲疲劳强度 齿根弯曲疲劳强度条件为 （1） K、b、m和同前（2） 圆周力为 Ft=（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=2.65,YF2=2.13，由图8-9查得YS1=1.58，YS2=1.88（4） 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 满满足齿根弯曲强度5.计算锥齿轮传动其她几何尺寸ha=m=5mmhf=1.2m=1.2*5mm=6mmC=0.2m=0.2*5mm=1mmda1=d1+2mcos=115+2*5*0.9474mm=124.474mmda2=d2+2mcos=340+2*5*0.3201mm=343.201mmdf1=d1-2.4mcos=115-2.4*5*0.9474mm=103.631mmdf2=d2-2.4mcos=340-2.4*5*0.3201mm=336.159mmha=5mmhf=6mmC=1mda1=124.474mmda2=343.201mmdf1=103.631mmdf2=336.159mm 二、低速级斜齿圆柱齿轮设计计算 斜齿圆柱齿轮设计计算见表5计算项目计算及阐明计算成果1.选取材料、热解决方式和公差等 大、小锥齿轮均选用45钢，小齿轮调质解决，大齿轮正火解决，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钢小齿轮调质解决大齿轮正火解决8级精度2.初步计算传动重要尺寸由于是软齿面闭式传动，故按齿面接触疲劳强度进行设计。其设计公式为1) 小齿轮传递转矩为T3=224600·2) 因v值未知，Kv值不能拟定，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=i=4.266) 查表8-18，取齿宽系数=1.17) 初选Z3=23，则Z4=uZ3=4.28*23=97.98，取Z4=98，则端面重叠度为 = =1.67轴向重叠度为由图8-13查得重叠度系数8） 由图11-2查得螺旋角系数Z=0.999） 许用接触应力可用下式计算 由图8-4e、a查得接触疲劳极限应力为 小齿轮与大齿轮应力循环次数分别为N3=60n2aLh=60*244.07*1*2*8*250*10=5.86*109N4=N3/i2=5.86*109/4.26=1.38*108由图8-5查得寿命系数ZN3=1.05，ZN4=1.13；由表8-20取安全系数SH=1.0，则有 取初算小齿轮分度圆直径d3t，得 =77.553mmZ3=23Z4=98d3t77.553mm3.拟定传动尺寸（1）计算载荷系数 由表8-21查得使用系数KA=1.0因=0.99m/s，由图8-6查得动载荷系数Kv=1.1，由图8-7查得齿向载荷分派系数K=1.11，由表8-22查得齿向载荷分派系数K=1.2，则载荷系数为 K=KAKvKK=1.0*1.1*1.11*1.2=1.45（2） 对d3t进行修正 因K与Kt有较大差别，故需对Kt计算出d3t进行修正，即 =78.465mm(3) 拟定模数mn mn=按表8-23，取mn=4mm（4） 计算传动尺寸 中心距为 =247.4mm取整，螺旋角为 因值与初选值相差较大，故对与关于参数进行修正 由图9-2查得节点区域系数ZH=2.43，端面重叠度为 = =1.65轴向重叠度为由图8-3查得重叠度系数，由图11-2查得螺旋角系数Z=0.984 =77.845mm因=0.99m/s，由 图8-6查得动载荷系数Kv=1.1，载荷系数K值不变 mn=按表8-23，取mn=4mm，则中心距为 螺旋角为修正完毕，故 b4=105mm b3=110mm K=1.45d3t77.845mmmn=4mma=250mmd3=95.041mmd4=404.959mmb4=105mmb3=110mm4.校核齿根弯曲疲劳强度 齿根弯曲疲劳强度条件为 1） K、T3、mn和d3同前2） 齿宽b=b3=105mm3） 齿形系数YF和应力修正系数YS。当量齿数为 由图8-8查得YFS=2.61，YF4=2.23；由图8-9查得YS3=1.59，YS4=1.814） 由图8-1查得重叠度系数5） 由图11-23查得螺旋角系数6） 许用弯曲应力为 由图8-4f、b查得弯曲疲劳极限应力由图8-11查得寿命系数YN3=YN4=1，由表8-20查得安全系数SF=1.25，故=42.66Mpa<满足齿根弯曲疲劳强度5.计算齿轮传动其她几何尺寸端面模数齿顶高 ha=ha*mn=1*4mm=4mm齿根高 hf=(ha*+c*）mn=（1+0.25）*4mm=5mm全齿高 h=ha+hf=3.5+4.375mm=7.875mm顶隙 c=c*mn=0.25*4mm=1mm齿顶圆直径为 da3=d3+2ha=95.041+2*4mm=103.041mm da4=d4+2ha=404.959+2*4mm=412.959mm齿根圆直径为 df3=d3-2hf=95.041-2*5mm=85.041mm df4=d4-2hf=404.959-2*5mm=394.959mmm1=4.132mmha=4mm hf=5mmh=7.875mmc=1mmda3=103.041mmda4=412.959mm df3=85.041mmdf4=394.959mm七、 齿轮上作用力计算齿轮上作用力计算为后续轴设计和校核、键选取和验算及轴承选取和校核提供数据，其计算过程见表6计算项目计算及阐明计算成果1.高速级齿轮传动作用力（1）已知条件 高速轴传递转矩T1=80110Nmm，转速n1=720r/min，小齿轮大端分度圆直径d1=115mm，cos1=0.9474，sin=0.3201，（2）锥齿轮1作用力 圆周力为其方向与力作用点圆周速度方向相反径向力为其方向为由力作用点指向轮1转动中心轴向力为其方向沿轴向从小锥齿轮小端指向大端法向力为 Ft1=1639.1NFr1=565.2NFa1=191NFN1=1744.3N 2.低速级齿轮传动作用力（1）已知条件 中间轴传递转矩T2=224600Nmm，转速n2=244.07r/min，低速级斜齿圆柱齿轮螺旋角。为使斜齿圆柱齿轮3轴向力与锥齿轮2轴向力互相抵消一某些，低速级小齿轮右旋，大齿轮左旋，小齿轮分度圆直径为 d3=95.041mm（2） 齿轮3作用力 圆周力为其方向与力作用点圆周速度方向相反径向力为 其方向为由力作用点指向轮3转动中心轴向力为 其方向可用右手法则来拟定，即用右手握住轮3轴线，并使四指方向顺着轮转动方向，此时拇指指向即为该力方向法向力为（3） 齿轮4作用力 从动齿轮4各个力与积极齿轮3上相应力大小相等，作用方向相反Ft3=4726.4NFr3=1777.1NFa3=1225.3NFn3=5196N八、 减速器装配草图设计一、 合理布置图面该减速器装配图一张A0或A1图纸上，本文选取A0图纸绘制装配图。依照图纸幅面大小与减速器两级齿轮传动中心距，绘图比例定位1：1，采用三视图表达装配构造。二、 绘出齿轮轮廓尺寸在俯视图上绘出锥齿轮和圆柱齿轮传动轮廓尺寸