英文翻译 液压传动系统设计与计算.docx
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英文翻译 液压传动系统设计与计算.docx
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英文翻译液压传动系统设计与计算
河南农业大学毕业论文(设计)
英文翻译
翻译题目:
液压传动系统设计与计算
学院机电工程学院
专业班级06机制(3)班
学生姓名陈重
指导教师魏宗信
2010年5月3日
Hydraulicactuationsystemdesignandcomputation
1isclearaboutthedesignrequesttocarryontheoperatingmodeanalysis.
Whendesignhydraulicsystembelow,firstshouldbeclearaboutthequestion,andtakesitasthedesignbasis.
Mainengineuse,technologicalprocess,overalllayoutaswellastohydraulicgearpositionandspatialsizerequest;Themainenginetothehydraulicsystemperformancerequirement,liketheautomaticity,thevelocitymodulationscope,themovementstability,thecommutationpointingaccuracyaswellastherequestwhichtothesystemefficiency,warmpromotes;Hydraulicsystemworkingconditions,liketemperature,humidity,vibrationimpactaswellaswhetherhassituationandsooncorrosivenessandheat-sensitivematerialexistence.
Inintheaboveworkfoundation,shouldcarryontheoperatingmodeanalysistothemainengine,theoperatingmodeanalysisincludingthemovementanalysisandthemechanicalanalysis,alsomustestablishtheloadandtheoperatingcyclecharttothecomplexsystem,fromthisunderstoodthehydrauliccylinderortheoilmotorloadandthespeedchangeasnecessarytherule,belowmakestheconcreteintroductiontotheoperatingmodeanalysiscontent
1.1movementsanalyses
Themainenginefunctionalelementaccordingtothetechnologicalrequirementmovementsituation,mayusethedisplacementcirculationchart(L—t),thespeedcirculationchart(v—t),orthespeedandthedisplacementcirculationchartindicated,fromthiscarriesontheanalysistothemovementrule.
1.1.1displacementscirculationattemptsL—t
Thechart1.1isthehydraulicpresshydrauliccylindermovesthecirculationchart,they-coordinateLexpressionpistonmoves,thex-coordinatetexpressionstartsfromthepistontotherepositiontime,therateofcurveexpressionmovementofplungerspeed.
Chart1.1displacementscirculationchart
1.1.2speedscirculationchartv—t(orv—L)
Intheprojectthehydrauliccylindermovementcharacteristicmayinduceisthreekindoftypes.Thechart1.2isthreekindoftypeshydrauliccylindersv—tchart,thefirstkindoflikechart1.2centersolidlinesshow,thehydrauliccylinderstartstomaketheuniformacceleratedmotion,thenuniformmotion,
Chart1.2speedscirculationchart
Finallyuniformretardedmotiontoendpoint;Thesecondkind,thehydrauliccylinderprecedingpartlymakestheuniformacceleratedmotionintheoveralltravellingschedule,inanotheronepartlymakestheuniformretardedmotion,alsotheaccelerationvalueisequal;Thethirdkind,thehydrauliccylinderonemostabovemakestheuniformacceleratedmotionintheoveralltravellingschedulebyasmalleracceleration,thenuniformdeceleratestothetravellingscheduleendpoint.V—tchartthreevelocitycurve,notonlyclearlyhasindicatedthreekindoftypeshydrauliccylindersmovementrule,alsoindirectlyhasindicatedthreekindofoperatingmodesdynamicperformance.
1.2mechanicalanalyses
1.2.1hydrauliccylindersloadsanddutycyclechart
1.2.1.1hydrauliccylindersloadstrengthcomputations
Whentheoperatingmechanismmakesthestraightreciprocatingmotion,thehydrauliccylindermustovercometheloadiscomposedbysixparts
(1.1)
Intheformula:
FcInordertoresistancetocutting;FfInordertofrictiondrag;FiForinertiaresistance;FgForgravity;FmInordertosealtheresistance;FbInordertodraintheoiltheresistance.
1.2.1.2hydrauliccylinderscycleofmotionvariousstagesoverallloadstrength
Thehydrauliccylindercycleofmotionvariousstagesoverallloadstrengthcomputation,generallyincludesthestartacceleration,quicklyenters,thelaborenters,quicklydrawsback,deceleratesappliesthebrakeandsoonseveralstages,eachstageoverallloadstrengthhasthedifference.
(1)startstheaccelerationperiod:
Bynowthehydrauliccylinderorthepistonwereinfromstaticenoughtostartsandacceleratestothecertainspeed,itsoverallloadstrengthincludingguiderailfrictionforce,packingassemblyfrictionforce(accordingtocylindermechanicalefficiencyηm=0.9computation),gravityandsoonitem,namely:
(1.2)
(2)faststage:
(1.3)
(3)thelaborentersthestage:
(1.4)(4)decelerates:
(1.5)
Tothesimplehydraulicsystem,theabovecomputationprocessmaysimplify.Forexampleusesthesingleproportioningpumptosupplytheoil,onlymustcalculatethelabortoenterthestagetheoverallloadstrength,ifthesimplesystemusesthelimitingpressuretypevariabledisplacementpumporapairofassociationpumpsfortheoil,thenonlymustcalculatethefaststageandthelaborentersthestagetheoverallloadstrength.
1.2.2oilmotorsload
Whentheoperatingmechanismmakestherotarymotion,theoilmotormustovercometheoutsideloadis:
(1.6)
1.2.2.1operatingdutiesmomentofforceMe.Theoperatingdutymomentofforceispossiblyadefinitevalue,alsopossiblyasnecessarychanges,shouldcarryontheconcreteanalysisaccordingtothemachineworkingcondition.
1.2.2.2frictionmoments.Inordertorevolvethepartjournalplacefrictionmoment,itsformulais:
(1.7)
Intheformula:
Gisrevolvesthepartweight(N);Fistherubbingfactor,whenthestartforthefactor,afterthestartformovestherubbingfactor;Risthejournalradius(m).
1.2.2.3momentofinertiaMi.Themomentofinertiawhichinordertorevolvethepartaccelerationordecelerateswhenproduces,itsformulais:
(1.8)
Intheformula:
εIstheangleacceleration(r/s2);
istheaccelerationordeceleratesthetime(s);Jisrevolvesthepartrotationinertia(
),
Intheformula:
Inordertorotatetheparttheflywheeleffect(
).
Eachkindmaylookup
Accordingtothetype(1.6),separatelyfiguresouttheoilmotorinaoperatingcyclevariousstagesloadsize,thenmaydrawuptheoilmotorthedutycyclechart
2determinationshydraulicsystemmainparameter
2.1hydrauliccylindersdesigncalculations
2.1.1initiallydecidesthehydrauliccylinderworkingpressure
Inthehydrauliccylinderworkingpressuremainbasiscycleofmotionvariousstagesbiggestoverallloadstrengthdetermined,inadditionbelow,butalsoneedstoconsiderthefactor:
2.1.1.1eachkindofequipmentdifferentcharacteristicandusesituation.
2.1.1.2considerationseconomiesandtheweightfactor,thepressureelectslowly,thenpartsizebig,theweightisheavy;Thepressurechooseshighsomewhat,thenpartsizesmall,theweightislight,buttothepartmanufactureprecision,thesealingpropertyrequestshigh.
Therefore,thehydrauliccylinderworkingpressurechoicehastwoways:
One,electsaccordingtothemechanicaltype;Two,accordingtocutstheloadtoelect.
Ifthetable2.1,thetable2.2shows.
Thetable2.1pressestheloadtochoosetheexecutionfiletheworkingpressure
Load
/N
<5000
500~10000
10000~20000
20000~30000
30000~50000
>50000
Workingpressure
/MPa
≤0.8~1
1.5~2
2.5~3
3~4
4~5
>5
Thetable2.2pressesthemechanicaltypetochoosetheexecutionfiletheworkingpressure
Mechanicaltype
Enginebed
Farmmachinery
Projectmachinery
Grinder
Aggregatemachine-tool
DragonGatedigsthebed
Broachingmachine
Workingpressure
/MPa
a≤2
3~5
≤8
8~10
10~16
20~32
2.2oilmotorsdesigncalculation
2.2.1computationsoilmotordisplacement
Underoilmotordisplacementaccordingtothetypedecidedthat,
(2.1)
Intheformula:
Tistheoilmotorloadmomentofforce(N·m);
Foroilmotorimportandexportpressuredifference(n/m3);istheoilmotormechanicalefficiency,thecommongearandtheplungermotortakes0.9~0.95,theleafblademotortakes0.8~0.9.
2.2.2computationsoilmotorneedsthecurrentcapacityoilmotorthemaximumcurrentcapacity
(2.2)
Intheformula:
istheoilmotordisplacement(m3/r);
istheoilmotorhighestrotationalspeed(r/s).
3hydraulicpressurepartschoice
3.1hydraulicpumpsdeterminationswithneedthepowerthecomputation
3.1.1.1determinesthehydraulicpumpthebiggestworkingpressure.Thehydraulicpressurepumpingstationmusttheworkingpressuredetermination,mainlyactsaccordingtothehydrauliccylinderintheoperatingcyclevariousstagestohavemosttremendouspressurep1,inadditiontheoilpumplosesSigmaDeltaptheoilmouthtothecylinderplacealwayspressureΣΔp,namely
(3.1)
loses,thepipelineincludingtheoilaftertheflowvalveandotherpartslocalpressuresalongtheregulationlossandsoon,beforesystempipelinedesign,mayactaccordingtothesimilarsystemexperiencetoestimate,commonpipelinesimplethrottlevalvevelocitymodulationsystemΣΔpis(2~5)×105Pa,withthevelocitymodulationvalveandpipelinecomplexsystem
is(5~15)×105Pa,
alsomayonlyconsiderflowsaftervariouscontrolvalvespressureloss,butignoresthecircuitryalongtheregulationloss,variousvalvesratedpressurelosesmaysearchesfromthehydraulicpressureparthandbookortheproductsample,Alsomayrefertothetable1.3selections
Thetable3.1iscommonlyused,thelowpressureeachkindofvalvepressureloses(Δpn)
Valve
Δpn(×105Pa)
Valve
Δpn(×105Pa)
Valve
Δpn(×105Pa)
Valve
Δpn(×105Pa)
Cone-wayvalve
0.3~0.5
Cone-wayvalve
3~8
Cone-wayvalve
1.5~2
Cone-wayvalve
1.5~2
Crossvalve
1.5~3
Crossvalve
2~3
Crossvalve
1.5~3
Crossvalve
3~5
3.1.2determinesthehydraulicpumpcurrentcapacityqB
Pumpsthecurrentcapacity
basisfunctionalelementoperatingcyclemustthemaximumcurrentcapacity
andthes
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