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外文翻译--关于大型绞车制动系统最佳设计方面的研究.doc

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外文翻译--关于大型绞车制动系统最佳设计方面的研究.doc

英文原文WinchbrakesystemonlargescaledesignofthebestRedPhosphorusTechnicalInstituteoftheChineseRedPhosphorusMuroranInstituteofTechnologyMuroranJapanHitachiMachineryMotorcyclelaboratoryTsugaruStraitJapanAbstractInordertoadaptlikethetowermoldingmachine,makesthewinchasfaraspossiblesmallandlightisveryimportant.Therefore,thisarticlereportedbrakingsystemsoptimumdesign.Becauseofbrakingsystemsprecisecontrollabilityandsoon,thedispositionbrakingsystemscanimprovethesystemsoperationthesecurity.Theauthorstudiedonekindtoinstallonthe1000kwwinchbrakediscspliersdiscbrake,thiskindofwinchhadthe10m/sfluctuationspeed.PrefaceInordertodoasmuchaspossibletowinchthesmallandlightisveryimportant.Inthisareaofahoistareusuallyequippedwithdiscbrakes.However,inordertoachievethisobjectivebytryingtoimprovethebrakingsystem,particularlytheimprovedallocationofabrakewinchsafetyoftheoperation.Winchisconnectedwithatraditionalbrakediscbrakes.Springfrictionwiththepressureinthebrakedisc,andpressureonthesizeofthedeviceinstalledinthebrakingpressureonthehydrauliccylindercontrol.Ifanyoilhydrauliccylindersealsbroken,thefilmwillbeexposedtothefrictioninthemist.Thiswillresultinadangerousresultsreducethepressureonthebrake.Toavoidthispotentialdanger,theauthorofthestudyindicativeofanewtypeofbrake,peoplefromthemaintainabilityoftheviewtostudythisnewtypeofbrakeagencies.Asbrakeinstitutionsshouldalsobeverysmall,20MPAisconsideredtheworkpressure.Inordertofindthebestsystemforustostudythecharacteristicsofsystemdynamics.BrakingSystemWetakeatypicalwinch1000kwasastudyexample.Therearetwobrakediscandfourgroupsofinstitutionstargetedinthebrakedisc.Themaximumtorqueiswhentheemergenciesoccurs,isalsowhenthemaximumbrakingtorqueneedstodrop,themaximumbrakingtorqueexpressestheequality121112122DppddvDMDITtVwb1IntheformulawIrevolvingcomponentsmomentofinertia2kgmVMcomponentsqualitykg1Dwinchspooldiametermvvelocityofwhirlsm/1pwhenloadingropespullingforcen2pwhenunloadingropespullingforcenInthiscase,whenwinchspoweris1000speedsis100,theequilibriumvalueisnot100,therefore,biggestbrakingtorque250hasthefollowingresearchinstitutetodecide.PliersdiscbrakeThedemonstrationsuchnewstylebrakingsystemhasapairofclamp.Theclampclampsthebrakediscwiththebrakepad.Aonhydrauliccylinderusesforlocatedatsidethebrakepadoppositiontocontrolinstallsintheabovespringpressure.Wheneightbrakingmechanismssimultaneouslyaffectonwinchstime,equatesaffectsa32knmbrakingtorquewhichinthebrakepadcenter29knproduces,iffrictioncoefficientμ0.4.Canseetwopairofpliersplatesseparatelybythepinsealinandthefeatherpieceisfixedtogetheronthewinch.Tenhelicalspringsplaceinthetogetherspringassemblycanexert24knthestrength.Thestrengthcanthroughestablishadjustsintheabovescrewrod,inordertoonmanykindsofspecificationwinchsbrakingsystemasfaraspossiblewidespreadapplication.Throughcontrolshydrauliccylindersflowingtubingheadpressureasapriminghydrauliccylindertocontrolthebrakingtorque.Becausebrakingtorqueshysteresisisoppositeincontrolsignalisbecauserubscauses,Thereforeprimingbyveryprecisedesignsothateliminatespistonsresistance.Theelastomermaterialisplacedtogetherbetweeneachbrakepadandthepliersplate,thegoalisobtainsthesamecontactforce.Agroupofpliersplatebrakeisplacednearbybrakediscstwo.Theirrelationscanlook.Lookslikesuchwhichinthechartdemonstratedthatisloadedwiththenewstylepliersplatebrakeandthewinchhastheverygoodunion.ControlsystemThebrakingmechanismadjustsunderthesafepremise,withtheaimofusingfullyfromhydrauliccylinderspressureoilappliesthebrake.TwobrakevalveconnectsonthehydrauliccylinderOneisasafetyvalve,onetreadonsthevalve.Becauseintheworldwidescalemustincreasetheworkload,winchspowerandthewinchmovementsspeedisgettingquickerandquicker.Underthiskindofenvironment,tomaintainwinchssecurity,brakingmechanismscharacteristicshouldimprove.Wehadalreadystudiedcontrolsystemsdynamics.ControlsystemsdynamicsimulationTheinputsignalgivesthemagnetcoilcontrollingspringimpelsthepressurecontrolvalvebythisservicebrakepressureF1.ValvesoutputP2anddrivinginfluenceF1isbecomestheproportionunderthesteadystate,achievesthesteadystatethroughnegativefeedbackP2andthepressureF1inverseproportionrelations.Onewiththenegativefeedbackconnectionsaccumulator,itsroleisusesfortoremove,becausetheoilpressuresleepsvalvesmisalignmentquantitywhichthenaturecauses.Simultaneouslythissystemalsohasaphaseangleofadvance.Therelatedequationisasfollowsincircuitdiagramstrengthequation,0211101111pAkxxxxm2InductsthefeedbackroompressureP2}/exp1{112Ttpp3TriestohittheT1timeconstant,pressurizeP2,butneedscurrentcapacityQ121QQQS21111}/2{ppxdcs4TriestohittheCleakagecoefficient,fluiddensity,inflowprimingcurrentcapacity11/RppQaSabpaaaaapKKAKxAV}//{2(5)TriesthemediumoilcoefficientofvolumeKatohavepressurePatocause,R1istheelasticitycoefficient,flowstofeedbackroomcurrentcapacityQ2212/RppQa(6)Aboutprimingstrengthequation000apbabbaaaaaaxkFxkFpAxxm(7)Moreoverinhere,impelsthebrakepadstrengthFbis,abbbxkFF0(8)Infact,qualityMaandthedisplacementmeasureXatobesmall,mayneglectintheequality7inertiaandtheviscousfrictionintheactualsystem.Asaresultofthisreason,theinstructionbrakingtorqueTbresponsewhichpressurePaitselfcanbeapproximate.Wesimultaneouslyaretryingwithmathematicsmethodsolutionequationset28,hasthe32Knmbrakingtorquetwobrakesbyeachtotakeagroup.Inviewofappliesinthebrakesituationroutinecalculationresult,wheninputsignalinsteppedchanges,pressurePafasttoinstallationvaluechange.Onoursexperience,brakescontrolsystemhascertainlyabestresponsefastresponsenottocausetheharmfulvibration.Thebestresponsewasconsideredthatshouldbeforeapplyingthebraketheconstant,thebestvalueis0.3second.1Isrevolvingtheconstant0.3changecurvearoundsome,theresidehasnotradiatedhasnotbeenabletocausetheobvioustimelagwhichthesystemstabilitygoesbad.Compareswiththecomputationresult,hasotheronenottoaffecttheresult.Itistheobviousaccumulator,notonlythetimelagwasquiteshortmoreoverthecurvecharacteristicalsotoobtaintheimprovement.ConsiderationThisdiscbrakeneedsaflexiblematerialtoobtainthesamebrakepadcontactpressure.Usually,thebrakepadmustexposeinthebrakeprocessinthehightemperatureair.Asaresultofthisreason,usesinthiskindofsituationflexiblematerial,musthavethestrictlimit.ConclusionHasanalyzedthediscbrakeanditscontrolsysteminhereus,theseanalysisresultissummarizedforbelowa1winchstopassemblysmethodThediscbrakewasalreadyincludedtheplan.Thiskindofoptimumdesignandthemachinematchareverygood,althoughthebrakehadalreadyacceptedspringthistype,simultaneouslyitscompatibilityalsoobtainedtheconsideration.2throughcontrolsthebrakepadusingtheflexiblematerialthecontactpressure,causesthecontactpressuretheassignmentisthesame,buttheflexiblematerialschoiceneedsthecarevery.the3brakingforcessizehasthefunctiononpistonsflowingtubingheadpressuretodecidethatthebrakingforceandthespringstrengthareopposite.Theaccumulatorandbrakevalvesnegativefeedbackconnectsintogether,affectsthebrakethestability.ThanksTheauthorhopedtheMurorani.tstudentgentlemanexpressessincerethankstoM.Kodo,M.Kodointheseresearchperiodhasgiventheverybighelp.中文译文关于大型绞车制动系统最佳设计方面的研究赤磷技术学会赤磷中国室兰技术学会室兰日本日立机械机车实验室津轻海峡日本摘要为了适应如塔型机器,把绞车做的尽可能的小而轻是非常重要的。所以,这篇文章报告了制动系统的最佳设计。因为制动系统的精密可控性等等,配置制动系统能改善系统运行的安全性。作者研究了一种安装在1000kw绞车制动盘上的钳盘式制动器,此种绞车有10m/s波动速度。序文为了把绞车做的尽可能的小而轻是非常重要的。在这一个领域提升机通常都配置有盘式制动器。然而,为了达到这个目的作者设法改进了制动系统,尤其是改良了配置有制动器绞车的运行安全性。绞车是连接有盘式制动器的一种传统制动装置。装有弹簧的摩擦片压在制动盘上,并且压力的大小受装在制动装置上的压力液压缸控制。如果液压缸的任何油密封坏掉了,摩擦片就会暴露在油雾中。这样就会产生一个危险的结果制动压力减小。为了避免这种潜在的危险,作者研究了图.2中示意性的一种新型制动机构,人们从可维护性的观点来研究了这种新型的制动机构。由于制动机构也应该很小,20MPA被认为是系统的工作压力。为了找到系统的最佳特性我们学习了系统动力学。制动系统我们拿一个典型的绞车1000kw作为一个研究的例子。有两个制动圆盘且四组制动机构配置在圆盘上。最大的扭矩bT是在紧急事件发生时,也就是当最大的制动扭矩需要下降时,最大的制动扭矩bT被表示成等式121112122DppddvDMDITtVwb1式中wI旋转零件的惯性矩2kgmVM零件的质量kg1D绞筒直径mv旋转速度sm/1p装载时绳索的拉力n2p卸载时绳索的拉力n在这种情况下,当绞车的功率是1000wk速度是100sm/,不平衡值21pp为100kn,因此,最大的制动扭矩bT250knm是有下列的研究所决定的。钳盘式制动器

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