[优秀毕业设计精品]电动汽车升降仪系统结构设计

1毕业设计说明书论文作者学号学院机械工程学院系专业机械设计制造及其自动化专业题目电动汽车升降仪系统结构设计指导者教授评阅者2010年06月01日2毕业设计（论文）中文摘要电动汽车升降仪摘要本文主要设计了专用于升降汽车的双立柱升降机，采用电动机作为驱动元件，通过带轮传动使传动螺杆旋转，根据螺旋装置的特性将梯形螺杆螺母的旋转运动转化为轴向的上下运动，从而实现设计目的。本设计加入了保险螺母的设计，加强传动的安全保障。另外，还采用了行程位置极限保护装置，即采用JR1型继电器和行程开关达到控制升降臂不超过最低、最高升降范围。在润滑方面，本设计采用了手动液体吸油器润滑以提高其寿命。在设计过程中，主要进行了两部分的设计机械部分和控制电路部分。机械部分有螺旋传动的强度G7669G7692、带G2462带轮G17885G6333计G12651、轴G6227G17885G6333、保险螺母G12573的设计G727控制电路部分主要G11842G4462继电器在本设计中的G5049作G2419G10714G2462控制G3282设计。通过控制电路G4557机械部分进行运转G16855G14422，方G1427、G5567G6475的实现运动要G8726，实现机械G994电G4388G13007G13491化、G2499G19764性的设计。关键词螺旋G2115传动G30行程极位G30继电器G30吸油器3毕业设计（论文）外文摘要TITLETHEDESIGNOFAUTOMOBILEELEVATORABSTRACTTHISDESIGNISABOUTADOUBLECOLUMNAUTOMOBILEELEVATORSPECIALLYDESIGNEDFORLIFTINGVEHICLESICHOOSETHEMOTORASPOWERSUPPLIER,WHICHCANACTIVATETHESCREWROTATIONTHROUGHBELTDRIVEACCORDINGTOTHECHARACTERISTICSOFHELICALDEVICE,THEROTATIONOFTRAPEZOIDALSCREWANDNUTCANBETURNEDINTOUPANDDOWNMOVEMENTALONGTHEAXLEDIRECTION,SOTHEGOALPROMISEDCANBEACHIEVEDTHEMECHANICALSTRUCTUREISCOMPACTIVELYANDSECURITILLYPLANNEDBYADDINGTHEDESIGNOFINSURANCENUTSTILLMORE,ISTATEAPROTECTIONDEVICEOFLIMITPOSITIONINTHEDESIGNTHATISUSINGTHERELAYTYPEDJR1TOENSURETHEARMWILLNEVERTRAVELEXCEEDTHEMINIMUMORMAXIMUMLOCATIONINTHELUBRICATIONAREA,ISELECTAMANUALDEVICEUSINGLIQUIDLUBRICATIONOILTOENHANCEITSLIFETHEREARETWOSECTIONSINMYTHESISTHEMECHANICALPARTANDTHECIRCUITCONTROLLINGPARTTHEMECHANICALPARTINCLUDETHESTRENGTHCALCULATIONOFSCREWDRIVE,THESELECTIONOFBELT,PULLYANDBEARING,THEDESIGNOFINSURANCENUTANDSOONINTHECIRCUITCONTROLLINGFIELD,IMOSTLYFOCUSEDONTHEWORKINGPRINCIPLEOFTHERELAYAPPLIEDANDTHEDESIGNOFCONTROLLINGCHARTSTHEMECHANISMOFTHEELEVATORCANWORKSMOOTHLY,CONVENIENTLYANDRAPIDLYTHROUGHOPERATINGBUTTONSCONTROLLEDBYTHECIRCUITRELAYKEYWORDSSCREWDRIVELIMITPOSITIONRELAYOILABSORBINGDEVICE4目录1绪论611课题简介612方案拟定613汽车升降机的组成及其性能9131汽车升降机的组成9132设计方案综述10133工作原理102升降机机械机构设计1221传动方案的设计1222传动螺旋副的设计12221设计参数及选材12222螺杆强度校核15223螺纹牙强度计算与校核15224按抗磨损能力计算螺母的旋合圈数1623电动机的选择17231基本参数17232电动机的选用计算1724带及带轮的设计选择18241带的型号选择18242确定带轮直径19243验算带速19244确定带长L及中心距A19245校核小带轮包角120246带的根数Z计算21247轴拉力F计算21248带轮型号的选用2225轴承的选择22251螺杆顶部的轴承的选择22252螺杆底部的轴承的选择2326法兰盘设计2427保G19517螺母的设计25271G1186G5379G7366强度计算螺母G1813G16780磨损的G7380G3835G1833925272G1186G2110G2011G5224力计算螺母G1813G16780的磨损G7380G3835G18339263G6523G2058电G17347的设计2731G13499电G3132简介27532G6523G2058电G17347的设计27321G1039G16213G4466G10628的G2163能G72627322G6523G2058原理G3282G72628323G6523G2058原理G16840G7138284G2572G8845G3132的G9082G93812941G2572G8845G3132简介2942G2572G8845G3132的工作原理30G13479论32G14280G1688633参G13783G7003G104983461绪论11课题简介G19555G11540工G1006G12050G1262的G20146速G2469G4649G712G6117G3281的汽车G1147G1006G1075G5483G2052G1114G2081G6164G7422G7389的G3778G3835G452G3281G1147车G17754G2656G17839G2487车G17754的G3698G2164G712G1166G8677G10995G8975G8712G5191的G6564G20652G18129G1363汽车的G7234及G12255度G7097G17247G2164G3835G452G1306G7171G712G19555G1055G13792G7481的G1427G7171汽车保G1871G2656G13512G6264的G19394题G712G3926G1321G1363G1055简G1427G2614G731G1038G1114G16311G1927G17837G1022G19394题G712G1166G1216设计G1998G1114升降机G712G4439的G17828用G7509G3835方G1427G1114汽车的G13512G6264G712G4600其G7171G3324G3332盘G13512G1474G7114G712G7368G7186其G1260G17246性G452G13449G16278G3281G1881G3818的G11752G12362G8022G1929G712G11458G2081的G1042升机G1039G16213G2010G1038G8680动G451G9094动G451机械G5347G989G3835类G452其中G4600以G9094动居多G712机械G5347次G1055G712G8680动G7380少,且每类里又可G2010G1038二柱G5347G2656四柱G5347G452具体言G1055G712G9094动的特点G7171G5191稳G451噪音小G451力G18339G3835G712缺点G7171用久G1055后易漏G8845G712污染工作环境G452G13792机械G5347的一般多G1038电机驱动G712螺旋传动G712G4439不存G3324漏G8845G19394题G712且自锁保G6264简单易行G452就其G2469G4649G17247势G13792言G712一定G7171朝G11540安全G451简G1427G451G1363用寿命长G451噪音小G451价格低廉的方向G2469G4649G45212方案拟定通常机G3132由动力源G451传动装置G451执行装置G451G6523G2058装置及辅助系统等组成G72671方案选择（1）G9094压G451G8680压G451机电传动系统的比较G7261）G9094压传动系统利用G9094压泵将原动机的机械能转换G1038G9094体的压力能G712通过G9094体压力能的变化G7481传递能G18339G712经过各种G6523G2058阀G2656管G17347的传递G712借助于G9094压执行元件G9094压缸或马达把G9094体压力能转换G1038机械能G712G1186G13792驱动工作机构G712G4466G10628直线往复G17828动G2656回转G17828动G452G9094压传动的G1260点G7389G726体积小G451重G18339轻；调速范围G3835；换向容易；空间位置无严格G16213求；操G13449G6523G2058简G1427；自动化G12255度G20652；容易G4466G10628过载保G6264；G9094压元件G4466G10628G1114标准化G451系列化G451通用化G451G1427于设计G451G2058造G2656G1363用G452其缺点G1039G16213G7389G726G1363用G9094压传动对G13512G6264的G16213求G20652G451工作G8845G16213始终保持清洁；对G9094压元件G2058造精度G16213求G20652G712工艺复杂G712成本较G20652；G9094压元件G13512G1474较复杂G712且G19668G7389较G20652的G6228G7427G8712G5191；G9094压传动G3324能G18339转化的过G12255中G712特G2047G7171G3324G14422G8981调速系统中G712其压力G3835G712G8981G18339损G3845G3835G712G6937系统G6940G10587较低；G9094压传动对G8845G9213变化较G6947G5875G712G17837G1262G5445G2721G4439的工作稳定性G712G17837不G17878用于对于G5191G15925G16213求较G20652的汽车升降机构G452G21）G8680压传动系统G7171以压G13565G8680体G1038工作介G17148G712G19764G8680体的压力传递动力或G1461G5699的G8981体传动G452传递动力的系统G7171将压G13565G8680体经由管G17959G2656G6523G2058阀G17767G17877G13485G8680动执行元件G712把压G13565G8680体的压力能转换G1038机械能G13792作G2163G452其传动的特点G7171工作压力低,一般G1038G19G22G794G19G27G1818G5097G712G8680体G12908度小G712管G17959G19471力损G3845小G712G1427于G19610中G1391G8680G2656中距G12175G17767G17877G712G1363用安全G712无G10202G9868G2656电G1999G2373G19517G712G7389过载保G6264能力；G1306G8680压传动速度低G712G19668G16213G8680源G452G8680压传动由G8680源G451G8680动执行元件G451G8680动G6523G2058阀G2656G8680动辅件组成G452G8680动执行元件把压G13565G8680体的压力能转换G1038机械能G712用G7481驱动工作部件G712包G6336G8680缸G2656G8680动马达G452G8680动G6523G2058阀用G7481调G14422G8680G8981的方向G451压力G2656G8981G18339G712G11468G5224G3332G2010G1038方向G6523G2058阀G451压力G6523G2058阀G2656G8981G18339G6523G2058阀G452G8680压传动的基本特点类G1296于G9094压传动G712二G13785合G12228G1038G8981体传动G712G14521G5224用于汽车G13512G1474升降机G13479构G712不能保持G1016G1403G6272升的G5191稳G712G3252G8504G3324G8504G5785G1929G991G5194不G17878用G452G22）机械传动系统利用机械方G5347传递动力G2656G17828动的传动G452机械传动G3324机械工G12255中G5224用G19762常G5203G8879G712G7389多种G5430G5347G712G1039G16213可G2010G1038G1016类G726G311G19764机件间的G6717G6842力传递动力G2656G17828动的G6717G6842传动G712包G6336带传动G451G13511传动G2656G6717G6842轮传动等G452G6717G6842传动容易G4466G106288无G13435变速G712G3835G18129能G17878G5224轴间距较G3835的传动G3342合G712过载G6183G9381G17836能G17227G2052G13543G1926G2656保G6264传动装置的作用G712G1306G17837种传动一般不能用于G3835G2163G10587的G3342合G712G1075不能保G16789准确的传动比G452G312G19764G1039动件与G1186动件G2882合或借助中间件G2882合传递动力或G17828动的G2882合传动G712包G6336G21843轮传动G451G19154传动G451螺旋传动等G452G2882合传动能G3827用于G3835G2163G10587的G3342合G712传动比准确G712一般G16213求较G20652的G2058造精度G2656安装精度G452带传动一般用于G1016轴G5191行G451且G2528向转动的G3342合（G12228G1038G5332G2487传动）G712中小G2163G10587电机与工作机G1055间的动力传递G452G2379G12582G5347G19062G13511传动G13479构简单G712自重较轻G712G1306不G17878用于速度G6925变G20069G10587较G20652的G3342合G712且工作G9213度对G19062G13511寿命G5445G2721较严重G452G6717G6842轮中由于轮G19766G8821G7389轮G21843G712G6164以G2058造简单G712过载G7114可G6183G9381保G6264装置G712G1306G1262G1147G10995G17226G6717G6842G13792G4560G14280磨损G5567G451寿命低且G5529G20047G18331用压G13051装置G452G21843轮传动G7171利用G1016G21843轮的轮G21843G11468G1126G2882合传递动力G2656G17828动的机械传动G712G21843轮传动的特点G7171G726G21843轮传动G5191稳G712传动比精确G712工作可G19764G451G6940G10587G20652G451寿命长G712G1363用的G2163G10587G451速度G2656G4622G4556范围G3835G712G1306G7171G2058造G21843轮G19668G16213G7389G999G19388的设G3803G712G2882合传动G1262G1147G10995噪G3780G452G19154传动G7171通过G19154G7477将具G7389特G8542G21843G5430的G1039动G19154轮的G17828动G2656动力传递G2052具G7389特G8542G21843G5430的G1186动G19154轮的一种传动方G5347G452G19154传动G7389G16780多G1260点G712与带传动G11468比G712无G5389性G9381动G2656G6183G9381G10628G16949G712G5191G3355传动比准确G712工作可G19764G712G6940G10587G20652；传递G2163G10587G3835G712过载能力强G712G11468G2528工G1929G991的传动G4622G4556小；G6164G19668G5364G13051力小G712作用于轴G990的压力小；能G3324G20652G9213G451G9538G9299G451多G4588G451G7389污染等G5706G2167环境中工作G452G19154传动的缺点G1039G16213G7389G726G1177能用于G1016G5191行轴间的传动；成本G20652G712易磨损G712易G1292长G712传动G5191稳性G5058G712G17828转G7114G1262G1147G10995G19480G2164动载G14667G451G6403动G451G1926G1999G2656噪G3780G712不G4464用G3324G5625速G2465向的传动中G452G3252G8504G712G19154传动多用G3324不G4464G18331用带传动与G21843轮传动G712G13792G1016轴G5191行G712且距G12175较G17840G712G2163G10587较G3835G712G5191G3355传动比准确的G3342合G452螺旋传动G7171利用螺杆G2656螺母的G2882合G7481传递动力G2656G17828动的机械传动G452G1039G16213用于将旋转G17828动转换成直线G17828动G712将转G11709转换成G6524力G452按工作特点G712螺旋传动用的螺旋G2010G1038传力螺旋G451传G4560螺旋G2656调G6984螺旋G452一般螺纹升G12255G2656G6717G6842系数G18129不G3835G712G3252G8504G15441G9994轴向力FG11468当G3835G712G13792转G11709T则G11468当小G452传力螺旋就G7171利用G17837种工作原理获G5483机械G3698益的G452螺旋副传动G13479构G13051凑G451操作简单G451保G1871方G1427G452G8504传动方G5347G1039G16213用于负G14667G3835G451低速与无G19668G20069繁工作的G3342G6164G452其梯G5430螺旋特性9具G7389自动锁定G2163能G712既G1363G8821G7389G2058动装置G1075可保持载重G452G21根据设计指G4560及各部件工作G16213求G712确定方案G3926G991G726（1）动力源G726G18331用Y系列G989G11468异步电动机；（G21）传动装置G726G13783虑经济成本及可G1126换性G451G1363用寿命等方G19766G712G18331用G5203G8879G17828用的螺杆螺母传动；（G22）执行装置G726通过螺旋传动带动螺母沿轴向G990G991移动G712G1363螺母与G1042升臂连接G712G1186G13792G4466G10628G1363汽车G6272升G991降的G2163能；（4）G6523G2058部G2010G726G18331用行G12255位置G7509限保G6264装置G712即通过G18331用JR1型G13499电G3132G2656行G12255G5332关G7481达G2052G6523G2058G1042升臂不超过G7380低G451G7380G20652G1042升范围的G11458的G452另G3818通过G1363用JR1型G13499电G3132G1363G1016立柱G1881螺旋传动G2528G7114工作G712当G7389一旋转副停止G7114G712立即停止电机G712避免汽车倾斜G712以达G2052保G6264G1166G451机的G11458的；（5）辅助部G2010G726G3324G9082G9381方G19766G712G8504G18331用G1114G2572G8845G3132自动G9082G9381以G6564G20652其寿命G4521汽车升降机的组成及其性能131汽车升降机的组成升降机系列G7171由传动机构G451G6272升机构G712电动G6523G2058机构G712支撑机构组成的一种升降机设G3803G452汽车升降机的机械G13479构简G3282G72610132设计方案综述G8504汽车G13512G1474升降机G18331用G989G11468鼠笼型异步电动机作G1038源动力装置通过带传动带动螺旋副的螺杆转动G712根据螺旋传动的属性G712将旋转G17828动转化G1038升降臂沿轴向的G17828动G712G6984G1022机械系统通过G13499电G3132G6523G2058电G17347的G5332关G17839行操G13449G712可根据G4466际G19668G16213G19555G7114换档位以达G2052G16213求的G17828动过G12255G452传动螺旋副本身带G7389自锁的G2163能G712G3324设计中G2164入保G19517螺母G712可G17839一步保G16789升降机的安全G1363用G712G3324升降臂G17828动G2052G7509限位置G7114G712G6523G2058电G17347自动断G5332电机的G5332关G712确保升降臂G3324设定的G20652度G1881G6272升与G991降G452G8504类型升降机的G5332G2469G3324汽车G13512G6264领域占G7389一定的G1260势G712G18331用双立柱G5347身架G712G7389利于工G1166G17839行G13512G1474工作G712且可根据自身G19668求G19555G7114调G6984G6272升G20652度G452其G3818G16278灵巧G451占G3332G19766积小G451G13479构G7138G1114G451操作简单G451利于G6523G2058G5194可根据G2469G4649G17839一步G6925造G451G13792且G2058造成本不G20652G712G7171G13512G1474市G3342的又一股清G8981G452133工作原理系统的工作原理简述如下112升降机机械机构设计21传动方案的设计12根据G990述各传动方案的比较G712螺旋副传动G7389其他传动方G5347不可比拟的G1260势G712其自身G6164带的自锁G2163能G3324升降机械类的设计中G7171不容忽视的G712G3324G8504方案中G712立柱G1016端G18331用对G12228G5347的螺杆螺母传动G712G1016台电动机通过一G1022电机G5332关G6523G2058G712G1363G1016端G2528G7114启动G712G13792达G2052保持G1016端升降臂G5191G15925的G6940果G452G3324监督G1166员视觉G1998工作异常G7114G712可G19555G7114通过断G5332保G6264按钮停止电机的转动G712以达G2052安全保障的G16213求G45222传动螺旋副的设计221设计参数及选材1已知G7477件G7261轴向载G14667QG7380G3835G6272升重G18339G103815吨G712假设单边G1042升臂的重G18339G103815G19千克G726Q15G19G19/G219G2715G199G27NG27G27G21G19NG21G7380G3835G6272升G20652度LLG21G19G19G19MMG22G7380G3835工作宽度D13D19G19G19MMG21选材参见参G13783书G11458,表1G191选取材料G726螺杆45G19062螺母青铜选梯G5430螺纹15（G21G22G19）G712取单头G451梯G5430螺纹G712G6984体螺母G22由螺纹副耐磨性计算中径2D1螺纹副材料G726G19062（螺杆）对青铜（螺母）P11MPA取值（H/2D）G712HG1038螺母旋合长度当螺母G1038G6984体G5347G451磨损后间隙不能调G6984G7114G712G4464取1G21G215当螺母G1038G1016半G5347G451间隙能G3827调G6984G712或螺母兼作支承G13792受力较G3835G7114G712可取G215G225G6164以取1G27G21求中径2DG11709G5430G451梯G5430螺纹G726MMPHQPDPI2G5347（G211）G5347中Q轴向力；P螺距；比例系数H/2D；H螺纹工作G20652度G712梯G5430G2656G11709G5430螺纹HG195P,锯G21843G5430螺纹HG1975P；PG16780用压强；G11709G5430G451梯G5430螺纹中G726MMPQD802按梯G5430螺纹计算MM881611818820802D14查G7389关手册取标准值G726取公G12228直径DG21G19MM,螺距P4MM螺纹中径G7262DDG195P；G5347（G21G21）螺纹小径G7261DDP；G5347（G21G22）螺纹G3835径G726CADD24；G5347（G214）其中CAG19G215；求G5483G7262D1G27MMG7121D16MMG7124DG21G195MM4计算螺母G20652度H2HDH1G271G27MMG22G214M5螺杆螺母旋合圈数Z求G16311根据G5347PHZG5347（G215）由于旋合各圈螺纹牙受力不G3355G712Z不G4464G3835于1G19求G548310184432,表1G19G21中F求G5483G726FG191G19ARCTGFARCTGG191G19571G5347（G217）15G21当G18339G6717G6842系数的计算1035015COS100COSFFVG22当G18339G6717G6842角的计算10350ARCTGARCTGFVV5914校核VG712表1G19G22）青铜螺母MPAB5G19即BB知各传动件的传动G6940G10587G2010G2047G1038240540690890540690890A0A2A0A3A4A5A6A7A0A2A0A3A4A5A6则VVG5347（G211G21）232电动机的选用计算电动机的G17767G1998G2163G10587G1038G72618KWV830PPW8352W4008820PWVPA8A9A8A10A11A12A13A14A15A16A14A15A14A15由参G13783书知,取电动机的G20081定G2163G10587G103811KWY系列G989G11468异步电动机G7171一般用G17896低压G989G11468鼠笼型异步电动机基本系列G452G8504类电动机具G7389G20652G6940G451G14422能G451性能G3921G451G6403动小G451噪G3780低G451寿命长G451可G19764性G20652G451G13512G6264方G1427G451G17227动转G11709G6183等G1260点G452安装G4622G4556G2656G2163G10587等G13435G4448全符合IG40G38标准G452G18331用G37G13435G13489G13548G451G3818G3783G19462G6264等G13435G1038IP44G712G1931G2376方G5347IG38411其G20081定电压G1038G22G27G19G57G712G20081定G20069G10587G10385G19HZG712G22KW及以G991G1038G256YG257接法,4KW及以G990G1038G256G141G257接法G452选用电动机的型号G1038Y9G19SG344G712G9397载转速G103814G19G19R/MING45224带及带轮的设计选择带传动G7171G1016G1022或多G1022带轮G1055间用带作G1038G6388性拉G6353G19658件的传动G712工作G7114借助G19658件G1055间的G6717G6842（或G2882合）G7481传递G17828动G2656动力G452根据带的G6142G19766G5430G10378不G2528G712可G2010G1038G5191带传动G451G57带传动G451G2528步带传动等G452带传动G7171用中间G6388性件的一种传动G712G6164以G7261）能G13543G2656载G14667G1926G1999；G21）G17828行G5191稳G712无噪G3780；G22）G2058造G2656安装精度不G1699G2882合传动G18039G7691严格；4）过载G7114将G5353G17227带G3324带轮G990G6183G9381G712G3252G13792可G19462止其他G19658件的损G3363；5）可G3698G2164带长以G17878G5224中心距较G3835的工作G7477件G452241带的型号选择1螺杆转速2N传动G2163G10587P11KW转速1N14G19G19R/MING1042升机的升G12255G1038G21G19G19G19MMG712G4560G12255G10384MM及G2033步定的G990升G7114间5G19S,可G6524算G1998螺杆转速2NG726由2000504602N,知2N6G19G19R/MIN19G21确定计算G2163G10587查参G13783书G11458,表7G22的工作G5785G1929系数AK1G21则根据G726ACPKPKWG5347（G211G22）G5347中PG2529G1053G2163G10587求G5483CP111G211G22G21KWG22选G57带型号由,P2NCG712查参G13783书中G3282715确定G57带型号G712G6142G19766G4622G4556见参G13783书中的表71可知G726可选取A型带242确定带轮直径由参G13783书G712表74选1D1G19G19MMG712MMDNNIDD323312112G5347（G2114就取2DG215G19MM传动比G726332600140021NNIG5347（G2115）243验算带速SMSMND/337/100060V11PIG20047G575M/SG215M/S,则G6164取带轮基本G4622G4556符合转动G7477件244确定带长L及中心距A1G2033选带长0L,中心距A1G2033取中心距21021270DDADD,表7G21选与0LG11468G17829G12257长的L选L16G19G19MM,LKG1999G22G4466际中心距200LLAAG5347（G211G27）可G11053G1998调G6984G1325G18339G102G19G19G22LA5G19G19（16G19G19156G1975）/G215196G22MMG712取A5G21G19MMG141LG102G19G19G2216G19G19G1024G27MM245校核小带轮包角1G57带传动的包角1一般不小于1G21G19由G5347G72660180121ADDG5347（G2119）G20047符合11G21G19G4466际1120716260520100250180G6937合G1787821246带的根数Z计算KKKPPPZL00CG5347（G21G21G19）K包角系数；1K长度系数；G46材G17148系数1由参G13783书G11458G455G21G456G712表111G19查G54830P值当选择A带G712传动比IG21G7114取0PG1917KWG21由参G13783书G11458,表11G27查G19980P用G6566值法算G1998中间值0P1G22KWG22由查G13783书,查117查G1998包角系数KG1995由查G13783书,表111G21查G1998长度系数1KG19994材G17148系数G46的取值1G7837G12395G5079,G7837线G13511G13479构G46G1975G21化G13432G13511G13479构G461G19本设计的取G461G195计算根数根950Z00KKKPPPLCG5347（G21G211）G13783虑带传动的G1363用寿命及G3818G16278等G712可取Z4根247轴拉力F计算1查参G13783书G11458G712表71G712查G1998Q值（G4506度）G72622/10MSNQG21计算G2033拉力NQV1421K25VZP500F2C0G5347（G21G21G21）由G726N973322SINZ2FF1022G8504可作G1038设计轴承的G1393据248带轮型号的选用由参G13783书可知G726（1）带轮基准直径DDG304G215D（DG1038轴的直径G712单位G1038MM）G7114G712可G18331用G4466心G5347；（G21）DDG22G19G19MM,可G18331用G14157G7507G5347（当,100D11MMD可G18331用G4392G7507G5347）；（G22DDG22G19G19MMG7114G712可G18331用轮副G5347小带轮选择G726G7234通G57带轮A41G19G19SG42G371G1941G21G3835带轮的选择G726G7234通G57带轮A4G215G19G40G42G371G1941G2125轴承的选择251螺杆顶部的轴承的选择1选择的G2081G6564G7477件1G3835带轮的轮G8598直径G7380G3835G10386G19MMG21轴承G5224以承受轴向载G14667G1038G1039,径向载G14667G1038辅G22G20056G7411计算寿命G1038HLG22G19G19G19H查参G13783书表1G271,根据传动螺杆的受力G5785G1929G712选用G3290G19193G9390G4388轴承类的轴承G21G9390动轴承当G18339动载G14667P计算1当RAFFEG712RPFFPG5347（G21G21G22）G21当RAFFEARPYFXFFPG5347（G21G214）RF径向载G14667；AF轴向载G14667；G59G451Y径向动载G14667系数G2656轴向动载；PFG1926G1999载G14667系数；23由G990述知G726AFG27G27G21G19NG712RFG22G22G2197N0134926973328820FEFRA查参G13783书表1G277G726取G59值G1038G194G712Y值G1038G19G27查参G13783书表1G226G726知G1926G1999载G14667系数PF1G21G6164以P1G21G194G22G22G2197G19G27G27G27G21G19N71G27919NG22计算轴承G5224G7389的基本G20081定动载G14667轴承寿命与载G14667的G7366线方G12255G1038G72610LP常数G5347（G21G215）G5347中P当G18339动载G14667G712N；10L基本G20081定寿命G712常以610RG1038单位；G166寿命指数G712G10711轴承G166G22,G9390G4388轴承G1661G19/G22；已知轴承的当G18339动载G14667PG2656G20056G7411G1363用寿命10LG712则G726可由G72661060PCHNLG5347（G21G216）求G5483G11468G5224的计算G20081定动载G14667G38G712G4439与G6164选用的轴承型号的G38值G5529G20047G9397G17287G726G38G305C310610300060060718919CG219G219G46N4查参G13783书表71G191G712选择轴承G726G9390动轴承G22G19G21G195G42G37/TG219794其G20081定动负G14667G38G22G21G21G46N5计算轴承的G4466际寿命HPCNRH01411516670L252螺杆底部的轴承的选择1选择的G2081G6564G7477件由于底部的轴承G1039G16213受轴向力G712G6164以取G3290G19193G9390G4388轴承作G1038选用类型24G21查参G13783书,表61,计算当G18339动负G146671当RAFFE,RPFFPG21当RAFFEG712ARPYFXFFP由G990述可求G5483G726AFG27G27G21G19,RFG22G22G2197RAFFG21649EG2167取G59G194G712YG19G27查参G13783书G712表1G226可知G726G1926G1999载G14667系数PF1G21G6164以G726ARPYFXFFP1G21G194G27G27G21G19G19G27G22G22G2197455G22G215G22计算轴承G5224G7389的基本G20081定动载G1466761060PCHNL1G2755G46N4查参G13783书,表61G712选择轴承选择G726G9390动轴承G22G19G21G194G42G37/TG2197G712其G20081定动负G14667G38G21G27G21G46N5计算轴承的G4466际寿命HH13121212545532820060016670L310则G8504轴承寿命较长G712能G9397G17287G1363用G7477件26法兰盘设计法兰连接就G7171把G1016G1022管G17959G451管件或G3132材各自G3278定G712G3324用法兰通过螺G7655G13051G3278于底G5243或连接G3800G452法兰连接G1363用方G1427G712能G3827承受较G3835的压力G452法兰G2010螺纹连接（G1009接）法兰G2656G9950接法兰G452低压小直径G7389G1009接法兰G712G20652压G2656低压G3835直径G18129G7171G1363用G9950接法兰G712不G2528压力的法兰盘的G2414度G2656连接螺G7655直径G2656数G18339G7171不G2528的G452G3324本设计中G712法兰盘G6164支承G9390动轴承G1038低中压力G19466G8585G712可G18331用小直径G1009接法兰G712材料G1038HT15G19G4522527保险螺母的设计G13783虑G2052螺杆与螺母G16213长G7411G2469G10995G11468对G6717G6842G712G13792螺杆的耐磨性又G20652于螺母G712G6164以G2494G16213保G16789螺母不G3845G6940G1427行G452271从弯曲强度计算螺母允许磨损的最大量G5379G7366强度公G5347G726BBZDBQHPI23G5347（G21G227）1BG1038螺纹牙根部宽度对G11709G5430螺纹BG195P对梯G5430螺纹BG1965PG6164以BG19654G216MMG21HG1038工作G20652度对G11709G5430G2656梯G5430螺纹HG195PG6164以HG1954G21MMG22HG1038螺母G20652度G712则旋合圈数26814324PHZ4G16780用G5379G7366G5224力（见参G13783书G712表1G19G22）青铜螺母50BMPA5计算螺纹牙根部G1813G16780宽度的G7380小值MMDZQHBB0823MINPIG21G19G27MMG6164以螺母G1813G16780的轴向的磨损G18339G1038G726MMBB52008262MIN272从剪切应力计算螺母允许的磨损最大量由G16780用G2110G2011G5224力G726PIBDZQG5347（G21G229）青铜螺母G180G22G19MPA4G19MPAMMDZQB430MINPIG6164以螺母G1813G16780的轴向的磨损G18339G1038G726MMBB172MIN综G990G6164述G712当保G19517螺母与传动螺母间的间隙由G5332始调G3921的G22MM变成1MMG7114G712即磨损G