[优秀毕业设计精品]带式输送机传动装置设计

学生课程设计（论文）题目机械设计课程设计学生姓名学号所在院系机电工程学院专业机械设计制造及其自动化班级指导教师二一零年一月A1A2A3A4A5A6A3A4A7A8A91目录任务书2成绩评定表5摘要6第一部分传动装置的总体设计7第二部分传动零件的设计计算9第三部分轴的设计18第四部分润滑油及润滑方式的选择36第五部分密封及密封的选择36第六部分主要尺寸及数据36总结38参考文献38A1A2A3A4A5A6A3A4A7A8A92本科学生课程设计任务书题目4带式输送机传动装置设计1、课程设计的目的本课程设计为学生提供了一个既动手又动脑，自学，查资料，独立实践的机会。将本学期课本上的理论知识和实际有机的结合起来，锻炼学生实际分析问题和解决问题的能力，提高学生综合运用所学知识的能力，装配图、零件图的设计绘图能力。2、课程设计的内容和要求传动装置简图1、己知条件1机器功用由输送带运送物料2工作情况电动机连续单向运转，载荷较平稳，空载启动，室内工作，环境温度不超过40度。3运转要求输送带运动速度误差不超过5。4使用寿命10年，G8611年300G3837，G1016G10689G2058。5G7828G1474G2620期一年G4579G1474，G989年G3835G1474。G25生G1147G2390G3423G1025G4579G3423机G7812G2058G17908G2390。2设计G2419G3999G6980G6466G16277G991G15932A0A10A11A12A13A14A15A16A17A15A18A19A20A21A22A23A0A10A11A24A25A26A27A28A15A29A30A31A21A32A33A34A35A36A37A15A17A17A31A20A203要求1G4448G6116传动装置的设计计G12651。2G4448G6116G2520G12879零件的设计、G17885G6333计G12651。3G16760G11507计G12651和G2058图，G1457G16789计G12651G8503G11842和图G13452G17148G18339。4G6365G20056G4462计G2022G5502G5219G4448G6116G1231G2165。5G6365学G7669G16280G4462G7696式G1082G1901G16840G7138G1082，G1144电G4388和G13452G17148G7003G7735。A1A2A3A4A5A6A3A4A7A8A933、主要参考文献G621G64所学G11468G1863课程的G6957G7460G622G64G457机G7812设计课程设计G458G623G64G457机G7812设计手G1888G458G624G64G457电动机手G1888G4584、课程设计工作进度计划1G1946G3803G19466G8585G7081G3837G7092设计计G12651G19466G8585G7083G3837G7093G1955速器的装配图一G5364G7084G3837G7094绘零件图G989G5364G7083G3837G7095G13546G1901设计G16840G7138G1082G7083G3837G709G25G12584G17789G6122G13783G4531G19466G8585。1G3837指导教师G708G12626G4395G709日期年G7388G7097教研室意见年G7388G7097学生G708G12626G4395G709G6521G2475G1231G2165G7114G19400年G7388G7097注G1231G2165G1082由G6363G4560G6957G5084G3647G1901。A1A2A3A4A5A6A3A4A7A8A94课程设计（论文）指导教师成绩评定表A38A39A40A41A40A41A42A43A44A45A43A44A43A46A47A43A42A48A49A50A48A49A51A52A53A542001A55A56A57A58A59A60A61A62A63A64A65A66A67A68A69A70A71A72A66A73A74A75A76A77A78A79A67A68A80A81A8202A83A84A85A86A87A88A89A90A91A92A93A94A95A96A94A95A97A98A99A100A95A101A102A103A104A93A105A106A107A108A109A110A111A112A113A114A115A74A116A77A117A118A8203A119A120A121A122A123A90A124A125A126A127A128A129A130A131A77A132A133A66A67A68A134A135A127A82A136A137A138A1393504A140A141A142A143A144A145A146A136A137A147A148A147A148A149A150A151A152A79A153A154A155A156A149A157A158A159A111A160A161A93A162A163A164A66A149A165A166A167A168A93A94A169A170A66A149A171A112A164A172A173A168A174A175A176A66A177A178A74A179A180A77A181A174A8205A182A143A183A184A146A136A137A185A149A186A187A97A98A188A116A99A100A155A189A190A191A192A193A194A195A149A196A178A197A198A76A199A174A200A112A164A77A93A201A202A203A195A74A204A205A95A206A67A62A207A208A209A210A109A110A211A153A154A77A149A72A8206A212A213A214A85A215A216A136A137A217A218A219A146A212A213A136A137A185A149A165A166A114A115A93A94A202A203A66A186A187A172A173A220A221A222A220A95A193A96A95A223A68A106A93A94A67A68A66A169A170A165A166A95A224A225A195A194A226A227A228A229A230A95A128A231A8207A213A232A233A213A232A234A182A143A136A137A185A73A74A198A235A77A169A170A150A236A111A167A168A149A72A195A149A150A151A115A236A237A172A173A238A118A239A205A95A206A67A95A167A168A155A240A241A114A115A106A8208A242A213A232A243A85A215A244A245A146A246A247A136A137A214A140A141A246A247A136A137A87A248A249A250A251A246A247A136A137A216A147A148A147A148A73A74A198A235A77A169A170A204A205A95A175A176A95A167A168A95A252A253A77A149A72A82A254A245A255A1234509A80A0A214A243A0A69A216A255A123A87A83A84A87A212A213A214A85A183A216A86A1A2A89A3A185A148A253A4A5A6A188A116A130A152A7A130A131A8A9A195A130A152A63A148A253A4A99A41A10A11A12A8A9A8210A212A213A57A13A14A214A85A183A216A255A123A19A148A252A200A146A15A128A231A66A74A24A160A195A187A174A165A166A66A174A200A94A175A66A181A174A101A16A253A168A195A93A94A165A166A66A175A176A167A168A78A79A8211A93A17A147A148A147A148A171A91A18A67A68A74A20A172A7A21A22A66A7A74A186A153A24A160A82A23A25A23A25A26A27A28A29A30A31A95A32A33A34A35A36A37A102A103A104A38A39A40A42A43A44A40A42A45A46A475摘要机械设计课程设计是在完成机械设计课程学习后，一次重要的实践性教学环节。是高等工科院校大多数专业学生第一次较全面的设计能力训练，也是对机械设计课程的全面复习和实践。其目的是培养理论联系实际的设计思想，训练综合运用机械设计和有关选修课程的理论，结合生产实际分析和解决工程实际问题的能力，巩固、加深和扩展有关机械设计方面的知识。本次设计的题目是带式运输机的减速传动装置设计。根据题目要求和机械设计的特点作者做了以下几个方面的工作决定传动装置的总体设计方案，选择电动机，计算传动装置的运动和动力参数，传动零件以及轴的设计计算，轴G6227、联G6521件、G9082G9381G4506G4565和联轴G3132的选择及校G20576计算，G314机体结G7512及其G19480件的设计和参数的G11842定，G315G13484G2058装G18209G3282及零件G3282，G13546G1901计算G16840G7138G1082。关G19202G16801减速G3132带式运输机机械设计G11142G2183G5390G5242A38A39A40A42A43A44A40A42A45A46A476计算及说明结G7536第一部分传动装置的总体设计一、传动G7053G77081、设计要求G2379G12582G11464G5464G39G32300G80G80，G10313G5353力G41G323400G49G15G13459速度G57G320G17G265G80G18G86，连续单向运转，载荷平G15925，空载启动，使用年G1949210年，G6221G18339生G1147，G1016G10689G2058工作，运输带的速度误差G1813G167805G8。2、电动机G11464G6521由G13864G17736器G994G1955速器连G6521，G1955速器由G13864G17736器G994G2379G12582连G65213、G1955速器G18331用G1120G13435圆柱齿轮G1955速器4、G7053G7708简图如G991轴1轴2轴3G1120、电动机的G17885G63331、G17885G6333电动机的G12879G3423G6365工作要求和条件，G17885用G989G11468笼G3423异步电动机，封闭式结构，电压380G57，YG34232、G17885G6333电动机的容G18339由电动机至运输带的传动总效率为4234221AG7084321、分别是G13864G17736器、G17736承、齿轮传动和G2379G12582的传动效率G709分别取1G320G1799、2G320G1798、3G320G179G26、4G320G179G258330960970980990232AG11842G4462传动G7053G7708G1955速器的G12879G3423为G1120G13435展开式斜齿圆柱齿轮G1955速器AG320G17833A48A49A50A51A52A53A50A51A54A55A567所以KWVFD0638330100075034001000KWVFW55210007503410003、G11842G4462电动机的转速G2379G12582G17736的工作转速为MIN7747300750100060100060RDVNG6365G6363G4560G1082G15932一，查G1120G13435圆柱齿轮G1955速器的传动比408I，故电动机转速的可G17885范围MIN819101638277474082RNIND，符合这一范围的同步转速有G2650、1000、1500RG18G80ING17根G6466容G18339和转速，由G6363G4560G1082P145取电动机G3423号Y132M1G25G989、G11842G4462传动装置的总传动比和分配传动比电动机G3423号为Y132M1G25MIN960RNM1、总传动比10207747960NNIMA2、分配传动装置传动比由公式21IIIA21I4131I求得3151I、7932I四、计G12651传动装置的运动和动力参G69801、计G12651G2520G17736转速G177361MIN9601RNG177362MIN79180MIN315960112RRINNG177363MIN7747MIN79379180223RRINN2、计G12651G2520G17736输入功率G177361KWKWPPD03399006311G177362KWKWPP8829709800333212G177363KWKWPP7429709808823223G2379G12582G17736KWKWPP66299098074212343、计G12651G2520G17736输入转矩KWKWWD552063NG324G26G17G26G26RG18G80IN电动机G3423号Y132M1G25MIN/9601RNMIN/791802RNMIN/77473RNKWP0331KWP8822KWP7423KWP6624A58A59A60A61A62A64A60A61A65A66A678电动机输出转矩MNMNNPTMDD44309600639550955013G17736的输入转矩G177361MNMNTTD1430990443011G177362MNMNITT01159315970980143013212G177363MNMNITT185477939709800115923223G2379G12582G17736输入转矩MNMNTT8753099098018547123413G17736的输出转矩则分别为G2520G17736的输入转矩乘G17736承效率0G1798运动和动力参G6980计G12651结果整理G994G991效率PKW转矩TMN转速NG708RG18G80ING709传动比I效率输入输出输入输出电机G177363G170G2530G17449G2501G1700G1799G1773613G17032G179930G171429G17549G2505G17310G1795G1773622G17882G1782159G1701155G1783180G17G2693G17G2690G1795G1773632G17G2642G17G25954G26G171853G25G17244G26G17G26G261G1700G179G26G2379G12582G177362G17G25G252G17G251530G178G26520G17254G26G17G26G26第二部分传动零件的设计计算一、高速级减速齿轮设计1、G17885G4462齿轮G12879G3423、精度等G13435、G7460料及齿G69801G17885用斜齿圆柱齿轮传动2运输机为一般工作机器，速度不高，由有机设G1082G15932108知，G17885用G26G13435精度G708GB1009588G7093G7460料G17885G6333有机设G1082G15932101G17885G6333G4579齿轮G7460料为40CR钢G708调G17148G709，硬度为280HBS，G3835齿轮G7460料为45钢G708调G17148G709，硬度为240HBS。G1120者G7460料硬度差为40HBS。4G17885G4579齿轮齿G6980为231Z，G3835齿轮齿G69801223152312IZZ5G709初G17885螺旋角G32142、G6365齿面G6521触强度设计由设计计G12651公式G7081021G709进行试G12651，即MNTD4430MNT14301MNT011592MNT185473MNT875304G17885用斜齿圆柱齿轮传动A68A70A71A72A73A74A71A72A75A76A779321112HEHDTTZZUUTKD1G11842G4462公式内的G2520计G12651G6980值1试G17885载荷系G698061TK2计G12651G4579齿轮传递的转矩MMNT3311054291098014303由G1593210G26G17885取齿宽系G69801D4由G1593210G25查得G7460料的弹性影响系G6980218189MPAZE5由图1021DG6365齿面硬度查得G4579齿轮的G6521触疲劳强度极G19492MPAH6001LIM；G3835齿轮的G6521触疲劳强度极G19492MPAH5502LIM；G25由式1013计G12651应力G5502环次G6980HJLNNH9111076482103008219606060HINN891121098243151076482G26由图1019查得G6521触疲劳寿命系G69809301HNK9802HNK8计G12651G6521触疲劳G16780用应力取失效概率为1G8，安全系G6980SG321，得SKKHHNHHNHHH222LIM21LIM121G32MPAMPA5548125509806009309由图1030G17885取区域系G6980432HZ10由图102G25查得7650188502则651212G709计G126511试G12651G4579齿轮分度圆G11464G5464TD1，代入G6980值321112HEHDTTZZUUTKDG32MMMM5385548818943231513156511101430612323HN911076482HN82109824MPAH5548MMDT5381A78A79A81A82A87A88A81A82A90A92A96102计G12651圆G2620速度VSMSMNDVT9316000096053810006011PIPI3计G12651尺宽BMMMMDBTD538538114计G12651尺宽G994齿高比BG18H模G6980MMMMZDMTNT6212314COS538COS11齿高MMMMMHNT645362125225256106453538/HB5计G12651纵向重合度83114TAN2313180TAN31801ZDG25计G12651载荷系G6980根G6466SMV/931，G26G13435精度，由图108G708机设G1082G709查得动载系G6980081VK由G15932102查得使用系G69801AK因斜齿轮，假设MMNBFKTA/100/，G6937可G11705G1866安全（8）、G17736承寿命的G7669核1已G11705G17736承的预计寿命L283001048000G75由所G17885G17736承系列7007AG38，查指导G1082P122表G11705额定G2172载荷G38190KN2G8726两G17736承受G2052的径向载荷NFFFNFFFNHNVRNHNVR33112541106838353975606731085167222222222212113G8726两G17736承的计算G17736向力对于70000AG38G3423G17736承，按表137，G17736承派生G17736向力RDFF680，G2029有NNFFNNFFRDRD2276533112568068046381975606806802211于是G17736向力为NFFNNFFFDADAEA2276528764463818238522114当量G2172载荷PG32523619756028764111RAFFE68033112522765222RAFFE由表135得径向载荷系数和G17736向载荷系数为G17736承14101X8701YG17736承212X02YG3252G17736承G17828G17728G1025有轻G5506G1926G1999载荷，G6937按表136取21PF，G2029NNFYFXFPNNFYFXFPARPARP40135022765033112512191107328764870975604102122222111115G20576算G17736承寿命G325221PP，所以按G17736承2的受力大小来G20576算，G2029HHHPCNLH48000483564013501900096060106010366所以所G17885G17736承寿命G12538合要G8726，G11842定角接触球G17736承7007AG38（9）、键的G7669核联G17736G3132与G177361G17885用键的系列50810LHBNT54292键、G17736和联G17736G3132的G7460G7021G18129是G19062，由表62查得许用G6392G2399应力1729CASHL48000NFR975601NFR33112524800048356HL50810LHBA214A215A216A217A218A219A216A217A220A221A22223MPAP120100，取MPAP100，键的工作长度MMBLL40，键的接触高度MMHK450，由式61得MPAMPAMPAKLDTP110311230404105429210233故可知其安全（G27）、轴承G4563G2641的校核1已知轴承的G20056计G4563G2641G472G104G27G104300G104104G27000G75由G6164选轴承G13007G2027720G27G36C，查G6363G4560书P123表知G20081定动载荷C352G46G492G8726两轴承受G2052的G5464向载荷NFFFNFFFNHNVRNHNVR2425331924999241348392928347713183022222222223231HL24000A1A2A3A4A0A10A3A4A11A12A13283G8726两轴承的计算轴向力G4557G112270000G36CG3423轴承，按表137，轴承G8978G10995轴向力RDFF680，G2029G7389NNFFNNFFRDRD6017222425336806800526724839296806802211G1122G7171轴向力为NNFFFNFFADADA711944347270526726017221221其中NNFFFAAA3472767391011119234G5415G18339动载荷P因440483929601722111RAFFE780242533711944222RAFFE由表135得G5464向载荷G13007数和轴向载荷G13007数为轴承111X01Y轴承24102X8702Y因轴承G17828转中G7389G17743G5506G1926G1999载荷，故按表136取21PF，G2029NNFYFXFPNNFYFXFPARPARP63327671194487024253341021384715601722048392912122222111115G20576算轴承G4563G2641因21PP，G6164以按轴承1的受力大G4579G7481G20576算，G2029HHHPCNLH2400048348384715352007918060106010366G6164以G6164选轴承G4563G2641G12538合G16213G8726，确定G16294G6521G16314G10711轴承720G27G36C（G28）、G19202的校核G4579齿轮1选G11004G19202的G13007G202763812LHBNT011592G19202、轴和G13864轴G3132的材料G18129G7171钢，由表62查得G16780G11004G6392G2399应力MPAP120100，取MPAP110，G19202的G5049G1328G19283度MMBLL51，G19202的G6521G16314G20652度MMHK450，由式61得MPAMPAMPAKLDTP1101237425141001159210233HLG4579齿轮63812LHBA14A15A16A17A18A19A16A17A20A21A22291选G11004G19202的G13007G2027MMMMMMLHB40812NT011592G19202、轴和G13864轴G3132的材料G18129G7171钢，由表62查得G16780G11004G6392G2399应力MPAP120100，取MPAP110，G19202的G5049G1328G19283度MMBLL28，G19202的G6521G16314G20652度MMHK450，由式61得MPAMPAMPAKLDTP1106167422841001159210233所以所选轴承寿命G12538合G16213求，G11842定G16294G6521G16314G10711轴承7212AC（8）G19202的校核G21843G17730G994轴1）选G11004G19202的系列MMMMMMLHB6311182）G19202G451轴和G17730G8598的材料G18129G7171钢，由G6957材查得G16780G11004应力MPAP120100，取MPAP110，G19202的G5049G1328G19283度MMBLL45，G19202G994G17730G8598G451G19202G8145的G6521G16314G20652度MMHK5550，G2029G7389MPAMPAMPAKLDTP11032716245551018547210233G21843G17730G994轴的G192021118LHBMPAMPAP1103271G13864轴G3132上G192021016LHBA84A85A86A87A88A89A86A87A90A91A9234MPAMPAKLDTP1100681505451018547210233，所以合G17878第四部分润滑油及润滑方式的选择G1268动G1226的G9082G9381G4557G1122此G1120G13435G7024G21843G3290G7621G21843G17730G1955G17907G3132，由G1268动G19658G1226设计G18108G2010G2499知G1268动G1226的G3290G2620G17907度G17840G17840G4579G112212G80G18G86，所以G18331G11004G9036G8845G9082G9381，为此G12677G1319G1881G19668G7389G17287G3827的G9082G9381G8845，G11004以G9082G9381和G6967G9921。G2528时为G1114G18003G1825G8845G6617动时G8797G9207G8879G17227，G21843G20042到G8845G8756G5225面的G17329G12175G993G4579G112230G79450G80G80,此G1955G17907G3132为40G80G80。选G11004G7643G1946G2507为G54H0357G282的G7234通G5049G1006G21843G17730G8845G9082G9381，G16025G14279G20652G17907G13435大G21843G17730G21843根G3290以上G451G1314G17907G13435大G21843G17730G989G2010G1055G980G2334G5464G53以G991。轴承的G9082G9381由前面G1268动G1226设计G18108G2010知G17959G21843G17730G3290G2620G17907度G4579G11222G80G18G86,故G4557轴承G18331G11004G9082G9381G14038G9082G9381，为此G3324轴承G7061G16025G7389G6389G8845环以G19462G8502G9082G9381G14038G8981G3845。G18331G11004G10272G2507为2的G19053G3534G9082G9381G14038（G42G374G28187）。第五部分密封及密封的选择轴承G12483G11434G1122轴G19400的G4506封由G1122G1268动G1226的G3290G2620G17907度G4579G11223G80G18G86,故G2499由指导书P58选择G4506封形式为粗羊毛毡封G8845圈G4506封。机G11434G994机座G13864G6521处的G4506封为G1114保证机G11434G994机座G13864G6521处G4506封的G2499靠性，G13864G6521凸缘应G7389G17287G3827的宽度，G13864G6521表面应精刨，其表面粗糙度应G993大G112263。第六部分主要尺寸及数据G12677G1319尺寸机座壁厚MM10机G11434壁厚MM101机座凸缘厚度MMB15机G11434凸缘厚度MMB151MPAMPAP1100681MM10MM101MMB15MMB151A93A94A95A96A97A98A95A96A99A100A10135机座G5225凸缘厚度MMB252地脚螺钉直G5464MMDF18地脚螺钉数目6N轴承G7061G13864G6521螺栓直G5464MMD161机G11434G994机座G17842G6521螺栓直G5464MMD122轴承G12483G11434螺钉直G5464MMD83窥视孔G11434螺钉直G5464MMD64定位销直G5464MMD10大G21843G17730G20042园G994G1881机壁G17329G12175MM121G21843G17730G12483面G994G1881机壁G17329G12175MM102G21843G177302G12483面和G21843G177303G12483面的G17329G12175MM114所G7389轴承G18129G11004G8845G14038G9082G9381轴承G12483G11434和G21843G177303G12483面的G17329G12175MM143轴承G12483G11434凸缘厚度MMT69MMB252M