减速齿轮箱设计

0目录一、传动装配的总体设计1.1电机的选择················································11.2求传动比··················································21.3计算各轴的转速、功率、转矩·······························2二、齿轮的设计2.1原始数据··················································32.2齿轮的主要参数············································32.3确定中心距················································42.4齿轮弯曲强度的校核·······································52.5齿轮的结构设计············································7三、轴的设计计算3.1轴的材料的选择和最小直径的初定····························83.2轴的结构设计··············································83.3轴的强度校核··············································10四、滚动轴承的选择与计算4.1滚动轴承的选择············································144.2滚动轴承的校核············································14五、键连接的选择与计算5.1键连接的选择··············································155.2键的校核··················································15六、联轴器的选择6.1联轴器的选择··············································166.2联轴器的校核··············································16七、润滑方式、润滑油型号及密封方式的选择7.1润滑方式的选择············································167.2密封方式的选择············································17八、箱体及附件的结构设计和选择8.1箱体的结构尺寸············································178.2附件的选择················································18九、设计小结···········································19十、参考资料·············································201机械设计课程设计计算说明书已知条件：项目运输带拉力F（N）运输带速v（m/s）卷筒直径D(mm)参数48002.5210结构简图1传动装配的总体设计1.1电机的选择1.1.1类型：Y系列三项异步电动机1.1.2电动机功率的选择假设：wp—工作机所需功率,kw;ep—电动机的额定功率,kw；dp—电动机所需功率,kw；电动机到工作机的总效率为，1234、、、分别为弹性连轴器、闭式齿轮传动（齿轮精度为8级）、滚动轴承和共同的效率。2则：48002.51210001000wFVpKw/dewppp32卷筒轴承齿轮联轴器查表可得：0.990.970.980.96卷筒轴承齿轮联轴器、、、所以：3220.99*0.97*0.99*0.960.89轴承齿轮联轴器卷筒/12/0.8913.48ewdpppKw1.1.3电动机转速的选择以及型号的确定方案号电动机型号额定功率（kw）同步转速（r/min）满载转速（r/min）总传动比1Y180L-61510009704.26辅助计算：16010006010002.5227.48/min3.142109704.26227.48wmwvnrDnin因为本设计为单级斜齿圆柱齿轮减速器的设计，总传动比应在3-5左右，所以应按方案二选择电动机。查表可得：外伸轴长度80mm,直径38mm，额定功率和满载转速见上表。1.2求传动比6010006010002.5227.48/min3.14210wvnrD9704.26227.48mwniin齿1.3计算各轴的转速n、功率p、转矩T1.3.1各轴的转速12970/min227.48/minmwnnrnnr31.3.2各轴的输入功率11212313.480.9913.3513.350.980.9912.95dppKwppKw1.3.3各轴的输入转矩11113.3595509550131.44970pTNmn22212.9595509550543.66227.48pTNmn2齿轮的设计2.1原始数据材料牌号热处理方法强度极限/BMpa屈服极限/CMpa硬度HBS45正火560200169~217调质580220229~286其中小齿轮45号钢调质，大齿轮45号钢正火2.2齿轮的主要参数由上述硬度可知，该齿轮传动为闭式软尺面传动，软尺面硬度350HBS，所以齿轮的相关参数按接触强度设计，弯曲强度校核。limH式中：—试验齿轮的接触疲劳强度极限应力；limHS—lim1.5HS接触强度的最小安全系数，取；NZ—1.02NZ接触疲劳强度计算的寿命系数，取；WZ—1WZ工作硬化系数，取。由教材图5—29查得：小齿轮lim1580HMpa；大齿轮lim2560HMpa。limlimHHPNWHZZS4所以：lim11limlim22lim3801.021258.41.55751.021391.01.5HNWHPHHNWHPHZZMpaSZZMpaS21311754HPdzKTudu式中：z—重合度系数，对于斜齿轮传动z=0.75~0.88，取z=0.80；K—载荷系数，一般近视取k=1.3~1.7,因是斜齿轮传动，故k取小K=1.5；d—齿宽系数，对于软尺面（350HBS），齿轮相对于轴承对称布置时，d=0.8~1.4,取d=1；u—齿数比，对于斜齿轮5~65uu，取。所以：213111754HPdzKTudu230.851.325.8651754258.40.9516.08mm2.3确定中心距121212a=222cosvnmZZmZZdd式中：1Z—小齿轮的齿数；2Z—大齿轮的齿数；—齿轮的螺旋角；5nm—斜齿轮的模数。对于软尺面的闭式传动，在满足齿轮弯曲强度下，选取1Z=36，则21525125ZiZ；螺旋角，一般情况下在8~15，当制造精度较高或对振动、噪音有要求的齿轮，可取10~20，或者更大值。本设计为一般要求，所以初选16斜齿轮的模数11cos59.72cos161.5936ndmZ，由渐开线圆柱齿轮第一系列，取nm=2所以：12236154a=197.652cos2cos16nmZZmm取中心距a=200mm,122.225125cos0.97522140nmZZa所以'''181141，符合其条件10~20。2.4齿轮弯曲疲劳强度的校核limminFSTFPNXFYYYS式中：STY—试验齿轮的应力修正系数，取STY=2；limF—试验齿轮的齿根的弯曲强度极限应力，lim1lim2220200FFMpaMpa、；minFS—弯曲强度的最小安全系数，取minFS=1.3；NY—弯曲疲劳强度寿命系数，取NY=1；6XY—弯曲疲劳强度的计算尺寸系数，取XY=1.所以：lim11minlim22min2202115801.3200211307.691.3FSTFPNXFFSTFPNXFYYYMpaSYYYMpaS又因为11221120002000FFSFSFpnnKTKTYYYYYbmZbmZ式中：FSY—外齿轮的符合齿形系数；Y—螺旋角系数。（其他字符的意义同前。）13233642cos154180cosvvZZ由教材图5—25可得：14.03FSY、23.94FSY12111.883.2cosZZ+1.76121'''12236175.80coscos(181141)(5~10)84nddmZbdbb由教材图5—40可得，螺旋角系数0.58Y。所以：111212000FFSnKTYYbmZ1220001.5131.444.030.5876.2084236FPMpa72222222000FFSnKTYYbmZ2220001.5543.663.940.5879.61762154FPMpa综上所述，两齿轮符合强度条件。2.5齿轮结构设计2.5.1计算齿轮分度圆直径小齿轮：11'''23675.80coscos(181141)nmZdmm大齿轮：22'''2154324.21coscos(181141)nmZdmm2.5.2齿轮宽度按强度计算要求，取齿宽系数d=1，则齿轮的宽度为2176dbdmm圆整后小齿轮的宽度为184bmm，大齿轮的宽度为276bmm2.5.3齿轮的圆周速度1113.1475.89703.8510/601000601000dnvms（满足精度要求）2.5.4齿轮的相关参数如下表名称代号单位小齿轮大齿轮中心距amm200传动比i4.26模数nmmm2螺旋角·'''cos(181141)'''192736变位系数X0齿数Z361548分度圆直径dmm75.80324.21齿顶圆直径daadmm79.80328.21齿根圆直径dfmm70.80319.21齿宽bmm84763轴的设计计算3.1轴的材料选择和最小直径估算3.1.1轴的材料选用45号钢，调质处理。3.1.2高速轴和低速轴直径初算直径时，若最小直径段开于键槽，应考虑键槽对轴强度的影响，当该段截面上有一个键槽时，d增加5%~7%，两个键槽时，d增加10%~15%，有教材表12-2，高速轴1110C，低速轴2110C。同时要考虑电动机的外伸直径d=38mm。所以13311113.351.051101.0526.36970PdCmmn23322212.951.051101.0542.32227.48PdCmmn结合电动机的外伸直径d=48mm，初选LT8联轴器48845843864884JGBJ,所以初确定1248ddmm3.2轴的结构设计3.2.1高速轴的结构设计3.2.1.1各轴段径向尺寸的初定13311113.351.051101.0526.36970PdCmmn结合电动机的外伸直径d=48mm，初选LT6联轴器48845843864884JGBJ所以取148dmm；253dmm；9355dmm由此