[机械设计精品] 毕业设计 单级圆柱齿轮减速器传动装置

毕业设计论文论文题目单级圆柱齿轮减速器传动装置作者姓名指导教师所在院系专业班级数控技术应用提交日期2010年6月I单级齿轮减速器输送机传动装置摘要带式输送机是现代最重要的散状物料输送设备，被广泛使用于电力、冶金、化工、煤炭、矿山和港口等领域。随着带式输送向着高带速、长距离、大运量的大型发展，拓展运人、运料和双向运输等功能，做到一机多用，使其发挥最大的经济效益，从而大大的提高了生产效率，降低劳动力。本次课程设计为带式输送机传动系统的设计，首先分析了带式输送机的发展前景，根据所设计的工作条件分析和确定传动方案，接着通过计算对带式输送机有关零部件进行合理选择、校核以及对重要零部件选择合理经济的G9082G9381方式。根据工作的G19668G8726，选择合理经济的方案G5224G1457G16789工作G2499G19764G1000G13479G7512G12628G2345、G4622G4556G13051G1957、G2164工方G1427、G6116本低G5277、传动效率高和使用G13512G6264G1427G2045。G3通过带式输送机传动系统的设计，进一G8505G5053G3278和所G4410G3534本G11705G16794G5194使所G4410G11705G16794G5483到G13520合运用，G5194为G3324G1182G2530G4410G1076本G999G1006和进行G8504G12879设计G6183G991了G3374G4466的G3534G11796，对G14270G5061G4570G7481工作G1025有G5468大的G5122G2173。G3G3关键词带式输送机，带传动，G21843G17730传动II目录A1A2IA31A4A5A0111A6A7A8A91111A10A11A12A131112A10A11A14A15A14A16A17A18112A19A20A21A221121A23A24A25A261A271A28A29A30A31A32A29A30311A33A34A35A36A37312A34A38A39A40A41A34A38A42A434121A44A45A46A47A48A494A502A51A52A53A54A55A56A52A53A55A5651A57A58A59A60A61A62A63A64A65A66A67A68A6952A57A58A59A60A70A71A67A68A6953A57A72A73A58A59A60A74A75521A76A77A78A79A80A81A82A83A78A79A84A85A86A87A88A78A79A84A89622A78A79A80A81A82A90A79A85A79A91A92A937221A94A95A96A97A98A95A99A96A97A100A101A1027A1033A104VA105A106A107A108A105A1069A1094A104A110A111A112A113A106A107A108A108A114A110A111A113A10611A1095A104A115A106A107A108A115A1061551A116A117A118A119A120A1211552A122A123A118A119A120A121A121A12418A1096A104A125A126A127A128A107A108A125A126A128A10722A1097A104A129A130A131A132A133A129A130A132A1332471A134A135A136A137A138A139A140A141A142A143A144A145A146A141A14224III72A134A135A136A137A147A1401A141A142A143A144A145A146A141A1422473A134A148A136A137A147A140A149A141A142A144A145A146A141A14224A1508A151A152A153A154A155A132A133A152A153A132A1332581A156A157A158A159A158A160A161A162A162A1632582A156A164A158A159A158A160A161A162A162A16326A1659A166A167A168A169A170A171A172A173A174A167A168A170A171A172A1732691A175A1762692A177A178A17927A16510A166A180A181A182A183A172A173A174A172A17327A16511A166A184A185A186A187A184A18527A188A189A190A191A192A193A194A195A196A192A193A194A195A196A197A19730A198A199A200A201A199A20031A202A2031IA202A2032IIA204A205A206A207A208A209A210A211A212A2131第1章绪论11设计题目A214A215A216A217A218A219A220A221A222A223A224A222A225A219A226A227A228A229111设计思路A2301A231A232A233A234A235A236A237A218A238A239A240A241A236A237A242A243A244A239A240A241A2302A231A232A233A239A240A241A245A246A247A228A248A234A235A241A247A228A242A243A244A249A240A250A251A252A249A240A253A2303A231A232A233A252A249A240A253A254A255A84A0A254A254A249A240A253A2304A231A232A233A254A249A240A253A243A244A84A1A247A228A15A236A237A2305A231A232A233A84A1A247A228A243A244A2A3A227A228A229A4A5A2306A231A97A6A7A8A9A10A11A12A13A827A83A103A14A828A83A105A16112设计的目的和要求A17A11A18A19A20A21A22A23A24A25A26A21A22A27A111A19A20A21A22A23A24A112A25A28A29A30A31A32A11A33A34A35A36A37A31A38A39A90A122A17A11A27A18A821A83A123A40A41A42A19A20A21A22A23A24A25A26A43A122A44A8A45A25A26A11A29A30A46A47A48A49A50A51A52A53A54A19A20A21A22A55A56A90A137A29A30A46A47A48A49A57A51A52A58A59A11A60A40A61A62A90A142A63A137A64A65A51A52A66A67A53A33A68A11A69A70A71A72A46A73A74A155A822A83A31A32A46A75A76A77A42A19A20A9A10A90A19A20A78A79A80A81A85A86A87A19A20A11A33A88A21A22A89A91A90A165A92A31A47A93A26A21A22A94A95A46A96A98A99A100A101A102A99A100A11A94A95A155A823A83A172A31A47A104A22A6A106A174A14A106A41A42A21A22A107A108A82A177A109A110A113A106A181A114A46A115A116A117A83A186A43A118A97A119A6A106A189A120A191A121A102A124A106A19A20CADA191A121A117A19A20A21A22A89A125A11A23A126A191A94A53A54A33A127A55A56A90A186A128A129A64A65A191A94A11A130A131A155A132A133A181A134A135A136A80A138A14A33A139A2A2012A9A10A93A140A14A141A143A139A82A78A79A9A10A106A144A106A204A145A117A833A21A22A22A6A146A147A148A33A149A82A4A201A8312设计内容121内容安排A1501A151A152A153A154A156A157A158A159A160A161A162A1502A151A163A153A164A157A166A167A160A152A153A168A169A170A153A171A153A173A175A176A157A178A179A1503A151A152A153A180A150A210A182A183A152A153A184A185A152A153A157A187A178A151A1504A151A188A157A187A178A1505A151A188A190A192A193A194A195A196A180A157A187A178A1506A151A197A198A199A171A198A188A200A157A166A167A192A202A203A205A206A207A208A209A211A187A178A212A2132A1507A151A214A215A192A216A180A157A187A178A1508A151A217A218A219A220A221A222A219A223A224A225A226A227A228A2299A230A224A225A225A231A232A233A234A223A235A236A237A238A239A240A241A242A224A225A243A2443第1章设计步骤11设计课题设计一用于带式运输上的单级直齿圆柱齿轮减速器。运输机连续工作，单向运转，工作中有轻微震动，经常满载，空载启动。减速器小批量生产，使用期限8年（每年以300天计），两班制工作，卷筒不包括其轴承效率为97，运输带允许速度误差为5。原始数据题号3运输带拉力F（KN）45运输带速度V（M/S）12卷筒直径D（MM）900设计人员对应学号46151125设计任务要求1减速器装配图纸一张（2号图纸）2轴、齿轮零件图纸各一张（3号或4号图纸）3设计说明书一分A245A246A247A248A249A250A251A252A253A254412计算过程及计算说明121传动方案拟定第三组设计单级圆柱齿轮减速器和一级带传动、工作条件使用年限8年，工作为两班工作制，有轻微震动，环境清洁。、原始数据滚筒圆周力F4500N；带速V12M/S；滚筒直径D900MM；方案拟定采用带传动与齿轮传动的组合，即可满足传动比要求，同时由于带传动具有良好的缓冲，吸振性能，适应大起动转矩工况要求，结构简单，成本低，使用维护方便。A255A217A16A0A1A57A217A2A50A3A0A220A217A78A4A5A6A7A8A94A221A10A95A222A116A40A12A50A49A13A14A15A17A18A19A20A21A225第2章电动机选择1、电动机类型和结构的选择A25A23YA224A24A26A27A28A29A30A31A32A90A229A224A24A30A31A32A33A34A35A162A36A37A38A39A41A42A43A44A45A30A31A32A90A122A46A47A48A51A90A86A52A53A54A90A240A55A56A58A90A244A59A60A61A90A247A36A34A62A249A250A90A62A249A248A90A252A63A64A65A66A205A67A252A68A69A73A70A71A72A74A1552、电动机容量选择电动机所需工作功率为式（1）/KWPPAWD由式21000/VFPWKW因此1000/KWVFPAD由电动机至运输带的传动总效率为总543321式中1、2、3、4、5分别为带传动、轴承、齿轮传动、联轴器和卷筒的传动效率。由机械G6175G1888G7609G5483G3926G991数据G24741096，2G729099，3G729093，4G729099，5095G2029总096G1040993G104093G104099G104095081所G1209电机所需的工作功率ZDVFP1000/8101000/214500（513KW3、确定电动机转速卷筒工作转速为A75A76N/100060DVPIA77A79A80A81A82A83A84A85A87A886900/21100060PI80MIN/RG7693据G6175G1888G748G723G15932G6524G14628的传动比合G10714G14551G3272，G2474圆柱齿轮传动一级减速器传动比G14551G3272G741G2553G7945。G2474带传动比G741G255G794G720。G2029总传动比G10714G16782G14551G3272为G741AG255G729G722G7940。G6937电动机转速的可G17885G14551为NG255DIAG104N卷筒16G79420G10480480G7941600R/MING2029G12538合G17837一G14551G3272的同G8505转速有750、1000和1500R/MING7693据G4493G18339和转速，由G11468G1863G6175G1888G7609G1998三G12193适用的电动机G3423G2507（G3926G159321）G13520合G13783G15397电动机和传动G16025G13634G4622G4556G18337G18339G1227G7696和带传动、减速器传动比，比G17751两G12193方案可G16277第2方案比G17751适合。G6937G17885定电动机G3423G2507为Y132M26，G1866G1039要性能G20081定功率为55KW满G17745转速为960R/MIN，G20081定转矩为221确定传动装置的总传动比和分配级传动比由G17885定的电动机满G17745转速NM和工作机G1039动轴转速N1、可G5483传动G16025G13634总传动比为IANM/NNM/N卷筒960/8012总传动比G12573于G2520传动比的G1068G12227分G18209传动G16025G13634传动比A89A91A92A93A94A95A96A97A98A997IAI0G104I（式中I0A100I分别为带传动和减速器的传动比）2、分G18209G2520级传动G16025G13634传动比G7693据机械设计G3534G11796G7609G5483G2474（普通V带I24）因为IAG729I0G104I所G1209IG729IAG715I0G72912/3G729422传动装置的运动和动力设计G4570传动G16025G13634G2520轴由G20652速至低速G1393G8437定为G265轴，G266轴，G1209G2462I0,I1，为G11468G18063两轴G19400的传动比01A10112A101为G11468G18063两轴的传动效率PA102A103PA104A103为G2520轴的输G1849功率KWTA102A103TA104A103为G2520轴的输G1849转矩（NG103M）NA102,NA104,为G2520轴的输G1849转矩（R/MIN）可G6365电动机轴至工作运动传G17894G17347G13459G6524G12651，G5483G2052G2520轴的运动和动力G2454数221运动参数及动力参数的计算A105A106A107A108A109（1）计G12651G2520轴的转数G265轴NA110NM/I0960/3320（R/MIN）G266轴NA111NA110/I1320/480R/MINA112A113A114A115A116A117A118A119A120A1218卷筒轴NA123NA11180R/MIN（2）计G12651G2520轴的功率G265轴PA110PDG10401PDG1041513G104096492KWG266轴PA124PA125G10412PA125G1042G1043492G104093G104099453KW卷筒轴PA126PA124A12723PA124A1272A1274453G104093G104099417KW（3）计G12651G2520轴的输G1849转矩电动机轴输G1998转矩为TD9550G103PD/NM9550G104513/9605103NG103MG265轴TA125TDG103I0G10301TDG103I0G10315103G1043G10409614697NG103MG266轴TA124TA125G103I1G10312TA125G103I1G1032A127414697G1044G104099G1040955529NG103M卷筒轴输G1849轴转矩TA126TA124A1272A1274520NG103M（4）计G12651G2520轴的输G1998功率由于G265G794G266轴的输G1998功率分别为输G1849功率G1068G1209轴承效率G6937PA125PA125G104A128A129492G104099487KWPA124PA124G104A128A129453G104099448KWA130A131A132A133A134A135A136A137A138A1399（5）计G12651G2520轴的输G1998转矩由于G265G794G266轴的输G1998功率分别为输G1849功率G1068G1209轴承效率G2029TA125TA125G104A128A12914697G1040991455NG103MTA124TA124G104A128A1295529G1040995474NG103M轴名效率P（KW）转矩T（NG103M）转速NR/MIN传动比I效率输G1849输G1998输G1849输G1998电动机轴5131469796028096G265轴4924921469714553204095G266轴4534535529547480100099卷筒轴4174175204928480第3章V带的设计（1）G17885G6333G7234G17902V带G6142G3423由机械设计G3534G11796G16850本1P165G1593296G5483KA12P513KWPCKAA127P12G1045136156KWG7693据PC6156KW，NA125320R/MIN由G16850本1P165G328299G5483G11705G1866G1144G9869G3324BG3423G1144G11040G13459G3800，G6937G17885BG3423VA140A141（2）G11842定带轮的G3534G1946直径，G5194G20576G12651带速A130A131A132A133A134A135A136A137A138A13910由G16850本1P165G1593299G2462P164G1593293G2474G4579带轮D1180MMD2N1A142D1A1421G166/N2IA142D1A1421G1663G104180G10410015346MM由G16850本G4631G464P164G1593293G2474D2560MMG15441使N2G11065有减G4581，G1306G1866G16835G5058G4579于5，G6937G1813G16780带速G20576G12651V1NG1031DG103G177/（1000G10460）960G104180G103G177/（1000G10460）904M/SG1183于525M/SG14551G3272G1881，G6937合适3G11842定带G19283和中G5527G17329AG2033定中G5527G17329为0A580MMG2474带的G3534G1946G19283G5242DL为AL20A2PI（D1D2）02124ADD25802PI（180560）58041805602238463MMG7693据G16850本G4631G464P162由G1593292G17885G2474G11468G17829的LD2240MMG11842定G4466G19481中G5527G17329A0A2ADLL5802632384224050769MM（4）G20576G12651G4579带轮G990的G2265G1629411O180ADD12O357O18069507180560O357O112137120合适（5）G11842定带的G7693数ZA143A144A145A146A147A148A149A150A151A15211G7693据G16850本G4631G464G1593294A和BG54151D180MM1N960R/MIN0P322G5415I03时0P003KWG7609G16850本G4631G464G1593295G5483K088G7609G1593292G5483LK100G2029V带的G7693数为ZLCKKPPP0000188030022315661987（G6937要G2474G21G7693G37G3423G57带）6计G12651轴G990的压力由G16850本G4631G464G1593291G7609G5483Q017MKG/由课本P166918单根V带的G2033拉力公式为0F2152500QVKZVPCA204917018805204921566500327N由G16850本G4631G464919G5483作用G3324轴G990的压力为QF2Z0FSIN222327SIN2112137O1217N带轮示意G3282G3926G991第4章齿轮传动的设计计算1选择齿轮传动类型、材料、热处理方式、精度等级。根据机械设计手册【2】卷3表14182，选用便宜便于制造的材料，小齿轮选硬齿面，大齿轮选软齿面，小齿轮的材A153A154A156A157A158A159A160A161A163A16412料为45号钢调质，齿面硬度为250HBS，大齿轮选用45号钢正火，齿面硬度为200HBS。精度等级运输机是一般机器，速度不高故齿轮精度初选8级。2、G2033G17885G1039要G2454数Z120，U4Z2Z1G103U20G104480由G16850本G4631G464P116G1593274G2474D11（3）按齿面接触疲劳强度设计计算小齿轮分度圆直径D1UUHKTD16762213G11842定G2520G2454数值1、G7609G16850本G1593266G2474K122、轮名义转矩T1955106P/N1955106492/320147510NMM3、许用应力G7609G16850本G3282621G4579齿轮的齿面平均硬G5242为240HBSG16780用应力可G7693据G16850本G4631G464G1593273G17902过G13459性插值来计G12651即1H513513545217255217240532AMP1F301217255217240301315309AMP2H491AMP2F291AMP4、重合度系数A165A166A167A168A169A170A171A172A173A17413T18832（1/Z11/Z2）18832（1/201/80）168大齿轮的齿面平均硬G5242为190HBS由G16850本G4631G464G1593273G13459性插值求G5483G16780用应力分别为2H491AMP,2F291AMPD1UUHKTD167622137664144911121104132615252MM4确定模数M11ZD2052152763由课本【1】P104标准模数第一系列上的值，取标准模数值M85按齿根弯曲疲劳强度校核计算A175FFSFYYMBDKT112校核式中1小轮分度圆直径D1MZ820160MM2齿轮啮合宽度BDD111160176MM3复合齿轮系数YFS1436YFS23984重合度系数Y025075/T025075/168068345许用应力查图622（A）FLIM1245MPAFLIM2220MPA查表68，取SF125则AFFFMPS1962512451LIM1A176A177A178A179A180A181A182A183A184A18514AFFFMPS1762512202LIM26计算大小齿轮的FFSY并进行比较19636411FFSY00222417698322FFSY0022611FFSY）（A107PFCFNLDTH预期寿命足够G8504轴承合格A108A109A110A111A112A113A114A115A116A1172682输出轴的轴承设计计算（1）初步计算G5415G18339G2172载荷P因该轴承G3324G8504G5049G1328条G1226G991只G2475到FR径G2533G2159G1328用，G6164以PFR5778N（2）求轴承应有的径G2533基本额G4462载荷值N3946384001080601857721106031616）（）（HTDLNFPFC（3）选择轴承G3423号查机械设计手册第二卷表7277，选择6211轴承CR432KN由课本式113有38400503706018577214320018060106010366）（A118PFCFNLDTH预期寿命足够G8504轴承合格第9章密封和润滑的设计91密封由于选用的电G2172机为低速，常温，常压的电G2172机则可以选用毛毡密封。毛毡密封是G3324壳G1319G3292G1881填以毛毡G3292以堵塞泄漏G19400隙，达到密封的目的。毛毡具有G3837G9994G5389G5627，G2588G7506G4392G9035G13513G10378，可G1660G4396G9082G9381油G2656G17986G6389G9796G4588。轴G7071G17728时，毛毡又可以将G9082G9381油G14270行G2050G991G2465G3809G14270行G9082G9381。A119A120A121A122A123A124A125A126A127A1282792润滑1G4557于齿轮来G16840，由于传G2172G1226的的圆周速度V12M/S,G18331用G9036油G9082G9381，因G8504机G1319G1881G19668要有足够的G9082G9381油，用以G9082G9381G2656G6967G9921。G2528时为G1114G18003G1825油G6617G2172时G8879起G8797G9207，齿G20042到油G8756底G19766的G17329G12175HG993应小于3050MM。G4557于G2345级减速G3132，G9036油G9157度为一个齿G1852高，G17837G7691G4613可以G1927G4462G6164G19668油G18339，G2345级传G2172，G8611G177281KWG19668油G18339V003507M3。2G4557于G9390G2172轴承来G16840，由于传G2172G1226的速度G993高，G1000G19602以G13475常G1391油，G6164以选用G9082G9381G14038G9082G9381。G17837G7691G993G1177密封G12628G2345，G993G4464G8981G3845，G2528时G1075G14033G5430G6116将G9381G2172表G19766G4448G1852G2010开的一G4630薄G14192。第10章联轴器的设计（1）类G3423选择由于两轴G11468G4557G1313G12239很小，运G17728G5191G12295，G1000结构G12628G2345，G4557G13543G1926要求G993高，故选用G5389G5627G7621G19156联。（2）类G3423选择由于两轴G11468G4557G1313G12239很小，运G17728G5191G12295，G1000结构G12628G2345，G4557G13543G1926要求G993高，故选用G5389G5627G7621G19156联。第11章设计小结机械设计课G12255设计是G6117G1216机械类G999G1006G4410G10995第一G8437较G1852G19766的机械设A129A130A131A132A133A134A135A136A137A13828计G16769G13463，是机械设计G2656机械设计基础课G12255G18337要的G13520合G5627与G4466G17353G5627G10627G14422。1通过G17837G8437机械设计课G12255的设计，G13520合运用G1114机械设计课G12255G2656G1866G1194有G1863先G1474课G12255的理G16782，结合G10995G1147G4466G19481知G16794，G3533G1871G2010G7524G2656解G1927一G14336G5049G12255G4466G19481G19394G20076的G14033G2159，并G1363G6164G4410知G16794G5483到进一步G5053G3278G451G9157G2282G2656G6205G4649。G32G4410G1076机械设计的一G14336G7053G8873，G6496G6581通用机械G19658G1226G451机械传G2172装G13634或G12628G2345机械的设计G2419理G2656过G12255。G3G33进行机械设计基本G6228G14033的G16769G13463，G392