液压与气压传动(英汉双语)第2版-教学课件-作者-陈淑梅-第9章-Chapter

Chapter9DesignofHydraulicTransmissionSystemChapter9DesignofHydrau9.1TheApproachforDesignofHydrostaticCircuits9.2ADesignExampleofHydraulicSystemsChapterlist9.1TheApproachforDesignof

IntroductionThedesignofhydrostatictransmissionsystemsisanimportantpartofthewholemechanicaldesignandalsoasummarizingandcomprehensiveapplicationofknowledgeinpreviouschapters.

Theaimofthischapteristoshowthroughanexamplehowhydrostatictransmissioncircuitscanbedesignedtosatisfyagivensetofrequirements.Introduction9.1TheApproachforDesignofHydrostaticsystems

9.1.1Determinationofdesignrequirements9.1.2Analysisforworkingconditionsanddeterminationofmainparameters9.1.3Determinationofhydraulicsystemdiagram9.1.4Calculationandselectionofhydrauliccomponents9.1.5Performancecheckforahydraulicsystemdesigned9.1.6Drawingofworkingdiagramsandtechnicaldocuments9.1TheApproachforDesignofFig.9-1Generaldesignprocessforahydraulictransmissionsystem

Fig.9-1Generaldesignprocess9.1.1DeterminationofdesignrequirementsBeforeahydraulicsystemisdesigned,theworkingconditionsofthemainframeinthemechanicalequipmentmustbeanalyzed.1.Thepurposeofthemainframe,theoverallarrangement,thelimitationstothepositionofthehydraulicdevicesandtheirsizes.2.Themainframeworkcycle,thesystemactions,theirsequence,interlockfunction,automatization.3.Theloadonactuatorsandtherangesofspeed,motionstability,positionaccuracy,conversionaccuracy,etc.4.Workingenvironmentandworkingconditions.

5.Workingefficiency,safety,reliability,cost,etc.9.1.1Determinationofdesign1.Analysisofworkingconditions1）Dynamicparametersanalysis

Aloaddiagramcanbedrawnoutbasedonthedeterminedextrinsicloads,seeFig.9-2a,whichisloadchart.Theloadchartisactuallyaload-displacement（F-l）curve.9.1.2Analysisforworkingconditionsanddeterminationof

mainparameters1.Analysisofworkingconditio

a)Loadchart

b)Speedchart

Fig.9-2Loadchartandspeedchartofactuators

1-Startupacceleration

2-Quickfeed

3-Workingfeed

4-Brake

5-Friction

6-Cuttingforce

7-Sealandbackpressureresistance

8-Inertiaforce

a)Loadchart(2)Movementparametersanalysis

Fig.9-2bisaspeed-displacement（v-l）curvedrawntoexpressthespeedofeachactuatorindifferentphases,itiscalledspeedchart.Whentheactuatorworksinlinereciprocating,theextrinsicloadwillbe(9-1)1)Theworkingload(2)Movementparametersanalysi2)Thefrictionresistanceforce(9-2)

3)TheinertialoadBesidesthreeloadsmentionedabove,anactuatorstandsalsoviscosityresistanceforce,sealedresistanceforceandbackpressureresistanceetc.(9-3)2)Thefrictionresistancefor2.DeterminationofmainparametersTheworkingpressureforactuatorscanbeselectedaccordingtothelargestloadintheloadchart(seeTab.9-1)orthemainframetype(seeTab.9-2).Howeverthelargestflowratemustbecalculatedbythehighestspeedshowninthespeedchart.

Thelowestworkingspeedmustsatisfythefollowingrequirements:Forcylinders

Formotors2.DeterminationofmainparamTab.9-1WorkingpressureselectedforanactuatoraccordingtoloadLoadF（N）<50005000~1000010000~2000020000~3000030000~50000>50000Workingpressurep（MPa）<0.8~11.5~22.5~33~44~55~7Tab.9-2WorkingpressureselectionforanactuatoraccordingtomainframetypeMainframetypeMachinetoolsAgriculturalmachinery,small-sizedengineeringmachinery,auxiliarydevicesforengineeringmachineryHydraulicpress,large-sizedexcavator,heavymachinery,liftingandconveyingmachineryGrin-derModularmachinetoolsPlanerDrawingbenchWorkingpressurep（MPa）≤23~5≤88~1010~1620~32Tab.9-1Workingpressureselec3.Drawingofworkingconditionchartoftheactuators

Afterthestructureparametersoftheactuatorsaredetermined,thepracticalworkingpressure,theflowrateandthepowercanbecalculatedaccordingtothedesigntaskanditsrequirements.Thenpressure(flowrate,orpower)—time(ordisplacement)curvescanbedrawnout,asshowninFig.9-3.Fig.9-3Workingconditionchartofactuators

1-Startupacceleration

2-Quickfeed

3-Workingfeed

4-Brake

3.Drawingofworkingconditio9.1.3Determinationofhydraulicsystemdiagram1.Analysisandselectionofthehydraulicscheme2.Analysisandselectionofthehydrauliccircuits3.Determinationofhydraulicsystemdiagram9.1.3Determinationofhydraul9.1.4calculationandselectionofhydrauliccomponents1.SelectionofpumpsAccordingtomaximumworkingpressureandprovidedflowratecalculatedabove,aproperpumpcanbeselectedfromproductsamples.Forthesakeofsafety,thechosenpumpmustbewitharatedpressure20%~60%higherthanthemaximumworkingpressure(describedabove)forpressurereserve,butwitharatedflowratejustmeetingthemaximumflowratetoavoidanexceedinglossofpower.2.Selectionofvalves9.1.4calculationandselectioTab.9-3Experientialvaluesofthepressurelossintheinletoilline

SystemconfigurationOverallpressureloss(MPa）Simplesystemwithgeneralthrottlespeed-regulatingcomponentsandpipelines0.2~0.5Complexsystemwithspeed-regulatingvalvesandpipelines0.5~1.53.SelectionofvalvearrangementsTherearethreetypesofarrangementsforhydraulicequipments(1)Modulartype(2)Manifoldplatetype(3)IntegratedblockTab.9-3Experientialvaluesof9.1.5Performancecheckforahydraulicsystemdesigned1.CheckingofthesystempressurelossThepressurelossincludesfrictionallossalongthepipelines,locallossinthepipelinesandtoalessproducedbythevalvecomponents.ThepressurelossofalongorlocalcanbecalculatedfromtheinvolvedexpressionsshowninChapter2,whilethelocallossofthevalvecomponentscanbeobtainedfromtheproductsamples.

Whenthepracticalflowrateqofavalvecomponentdoesn’tequalthenominalflowrate（9-4）9.1.5Performancecheckfora2.Checkingofthetemperaturerisecausedbyheatgenerationaccordingtoheatbalanceprinciple,whenthedimensionratiosofthreesidesofthereservoirarebetween1:1:1and1:2:3,theoilleveris80%thatofthereservoirheight,andthereservoirisingoodventilationCondition,then（9-5）Oncethecheckedoiltemperaturerisesurpassestheallowablevalue,apropercoolermustbesetinthesystem.Theallowableoiltemperatureriseinthereservoirisdifferentfordifferentmainframes2.Checkingofthetemperature9.1.6DrawingofworkingdiagramsandtechnicaldocumentsTheworkingdiagramsusuallyincorporatehydraulicsystemfigure,assemblydrawingandtheassemblyandpartDrawings.Theremustexistalistofcomponentsattachedtothehydraulicsystemfigure.Thesystemassemblyfigureistheconstructionanderectiondrawingforthehydraulicsystem.Generally,thetechnicaldocumentsincludetheexplanationsofdesigncalculation,manualtouseandmaintain,contentofparts,standardparts,universalparts,overalltableofoutsourcingparts,etc.9.1.6Drawingofworkingdiagr9.2ADesignExampleofHydraulicSystems9.2.1Analysisofworkingconditions9.2.2Determinationofmainparametersoftheactuator9.2.3Designofhydraulicsystems9.2.4Selectionofhydrauliccomponents9.2.5Performancecheckforhydraulicsystems9.2ADesignExampleofHydrau

Thissectionistostudythehydraulicsystemofasinglesidemulti-spindledrillmachinetool.axialcuttingforceoverallgrossweightG（N）Distanc-escoveredatrapidspeedDistanc-escovere-datworkspeedtherapidfeedandretractvelocityworkfeedvelocitytimeforaccelerationanddecelerationfrictioncoeffici-entofrestfrictionofmotionMechan-icalefficienc-yofthecylinder3000095001005050.00.9Thedynamicslipwayisrequiredtoachievesuchaworkcycle:rapidfeed→workfeed→blockdwell→rapidretract→stopattheoriginalposition.Thissectionistostudyt9.2.1AnalysisofworkingconditionsTheaxialcuttingforcewhichisalsotheonlyforcewhosedirectionishorizontal.Thentheinertiaforce,thefrictionofrestandthefrictionofmotionagainsttheguidewaycanbecalculatedasfollows9.2.1AnalysisofworkingcondTab.9-4Loadsonthecylinderineachworkstep

WorkingconditionLoadcombinationLoadF（N）ThrustStartup19002111Acceleration13541504Deceleration9501056Workfeed3095034389Rapidretract9501056TheloadsonthecylinderineachworksteparelistedinTab.9-4,wherethebackpressureintheoilreturnedchamberisneglected.TheloadandspeeddiagramsareindicatedinFig.9-4aandFig.9-4b.Tab.9-4Loadsonthecylinder

a)Load

b)Speed

Fig.9-4Loadandspeeddiagramsofthecylinder

a)Load9.2.2Determinationofmainparametersoftheactuator1）systempressure3）areaofcylinder2）

backpressure

Thecylinderareacanbecalculatedfromthethrustatworkfeedperiod:9.2.2DeterminationofmainpaThen

DanddmustbecorrectedtostandardvaluesaccordingtoGB2348－1997：,thenthepracticaleffectiveareasofthetwochambersofthecylinderareThepressure,flowrateandpowerateachworkstepasshowninTab.9-5.Theworkingconditionschartcanthenbedrawn,asindicatedinFig.9-5.ThenDanddmustbecorrectedTab.9-5Thepressure,flowrateandpowerateachstepTab.9-5Thepressure,flowratFig.9-5Workingconditionsdiagram

Fig.9-5Workingconditionsdia9.2.3Designofhydraulicsystems1.Selectionofhydrauliccircuits2.Designofhydraulicsystems3.Selectionofthehydraulicvalves9.2.3DesignofhydraulicsystFig.9-6PrinciplechartofhydraulicsystemFig.9-6PrinciplechartofhydFig.9-7PrinciplechatrofhydraulicsystemwithmodularvalvesFig.9-7Principlechatrofhyd9.2.4Selectionofhydrauliccomponents1.Pumps1）pressure2）flowrateThemaximumflowrateprovidedbythetwopumpsis25.13L/min.Iftheleakageinthereturnlineissupposed10%theinputflowrateofthecylinder,thentheoverallflowrateofthetwopumpsis9.2.4SelectionofhydrauliccFromthepressureandflowratecalculatedabove,thePV2R12-6/26typepairvanepumpcanbeadopted,Thedeliveriesofthesmallpumpandthelargepumpare6mL/rand26mL/rrespectively.3）motor

Accordingtoinvolvedmotorproductcontents,wecanselecttheY100L-6typemotor.Fromthepressureand2.ValvesandauxiliaryelementsThevalvesandauxiliaryelementscanbeselectedaccordingtothesystemworkingpressureandthepracticalflowratethroughthem,seeTab.9-6andTab.9-7.3.PipelinesAccordingtoYB231-1970,wecanchoosethe15-sizedcold-drawnseamlesssteeltubewhichhasaninnerdiameterof15mmandouterdiameterof18.2mm.2.ValvesandauxiliaryelemenNumberNameFlowrateestimated（L.min-1）Typeandspecification1Filter30XU-J63X802Pairvanepump5.1+22PV2R-6/263Pressuregaugeswitch-KF3-E3B4Checkvalve25AF3-Ea10B5Pressurereliefvalve5YF3-E10B6Five-way,three-positionsolenoidvalve6035DY-E10B7Checkvalve60AF3-Ea10B8Pressureswitch-PF-B8L9Strokevalve50AXQ-E10B10Speedcontrolvalve0.511Checkvalve6012Checkvalve25AF3-Ea10B13Backpressurevalve0.5YF3-E10B14Hydraulic-controlledsequencevalve25XF3-E10BTab.9-6Typesandspecificationofthecomponents

NumberNameFlowrateestimatedNumberNameFlowrateestimated（L.min-1）Typeandspecification1Filter30XU-J63X802Pairvanepump5.1+22PV2R-6/263Soleplateblock27.1EDKA-104PressuregaugeY-100T5Pressuregaugeswitch-4K-F10D36Pressureswitch-PD-F10D3-A7Hydraulic-controlledsequencevalve25X-F10D3-P/T(P1)8Pressurereliefvalve5Y1-F10D3-P/T9Electromagneticspeedcontrolcheckvalve-Q1AD-F6/10D3-B10Checkvalve25A-F10D3-T11Backpressurevalve0.5PA-Fa6/10D3-B(A)12Checkvalve25A-F10D3-T13Checkvalve60A-F10D3-T14Five-way,three-positionsolenoidvalve6035DY-E10BTab.9-7Typesandspecificationofthecomponents(modularvalves)

NumberNameFlowrateestimated

Tab.9-8Inputandoutputflowrateofthecylinder

Tab.9-8Inputandoutputflow4.ReservoirsThevolumeofthereservoircanbeestimatedfrom,whereisbyexperience,then：

Vcanbecorrectedtoastandardvalueof250LaccordingtoGB2876—19Performancecheckingofthishydraulicsystems1.Pressureloss2.Oiltemperaturerise4.ReservoirsThevolumeofyoursuggestions

arewelcome!TheEndyoursuggestions

arewelc液压与气压传动(英汉双语)第2版-教学课件--作者-陈淑梅-第9章-ChapterChapter9DesignofHydraulicTransmissionSystemChapter9DesignofHydrau9.1TheApproachforDesignofHydrostaticCircuits9.2ADesignExampleofHydraulicSystemsChapterlist9.1TheApproachforDesignof

IntroductionThedesignofhydrostatictransmissionsystemsisanimportantpartofthewholemechanicaldesignandalsoasummarizingandcomprehensiveapplicationofknowledgeinpreviouschapters.

Theaimofthischapteristoshowthroughanexamplehowhydrostatictransmissioncircuitscanbedesignedtosatisfyagivensetofrequirements.Introduction9.1TheApproachforDesignofHydrostaticsystems

9.1.1Determinationofdesignrequirements9.1.2Analysisforworkingconditionsanddeterminationofmainparameters9.1.3Determinationofhydraulicsystemdiagram9.1.4Calculationandselectionofhydrauliccomponents9.1.5Performancecheckforahydraulicsystemdesigned9.1.6Drawingofworkingdiagramsandtechnicaldocuments9.1TheApproachforDesignofFig.9-1Generaldesignprocessforahydraulictransmissionsystem

Fig.9-1Generaldesignprocess9.1.1DeterminationofdesignrequirementsBeforeahydraulicsystemisdesigned,theworkingconditionsofthemainframeinthemechanicalequipmentmustbeanalyzed.1.Thepurposeofthemainframe,theoverallarrangement,thelimitationstothepositionofthehydraulicdevicesandtheirsizes.2.Themainframeworkcycle,thesystemactions,theirsequence,interlockfunction,automatization.3.Theloadonactuatorsandtherangesofspeed,motionstability,positionaccuracy,conversionaccuracy,etc.4.Workingenvironmentandworkingconditions.

5.Workingefficiency,safety,reliability,cost,etc.9.1.1Determinationofdesign1.Analysisofworkingconditions1）Dynamicparametersanalysis

Aloaddiagramcanbedrawnoutbasedonthedeterminedextrinsicloads,seeFig.9-2a,whichisloadchart.Theloadchartisactuallyaload-displacement（F-l）curve.9.1.2Analysisforworkingconditionsanddeterminationof

mainparameters1.Analysisofworkingconditio

a)Loadchart

b)Speedchart

Fig.9-2Loadchartandspeedchartofactuators

1-Startupacceleration

2-Quickfeed

3-Workingfeed

4-Brake

5-Friction

6-Cuttingforce

7-Sealandbackpressureresistance

8-Inertiaforce

a)Loadchart(2)Movementparametersanalysis

Fig.9-2bisaspeed-displacement（v-l）curvedrawntoexpressthespeedofeachactuatorindifferentphases,itiscalledspeedchart.Whentheactuatorworksinlinereciprocating,theextrinsicloadwillbe(9-1)1)Theworkingload(2)Movementparametersanalysi2)Thefrictionresistanceforce(9-2)

3)TheinertialoadBesidesthreeloadsmentionedabove,anactuatorstandsalsoviscosityresistanceforce,sealedresistanceforceandbackpressureresistanceetc.(9-3)2)Thefrictionresistancefor2.DeterminationofmainparametersTheworkingpressureforactuatorscanbeselectedaccordingtothelargestloadintheloadchart(seeTab.9-1)orthemainframetype(seeTab.9-2).Howeverthelargestflowratemustbecalculatedbythehighestspeedshowninthespeedchart.

Thelowestworkingspeedmustsatisfythefollowingrequirements:Forcylinders

Formotors2.DeterminationofmainparamTab.9-1WorkingpressureselectedforanactuatoraccordingtoloadLoadF（N）<50005000~1000010000~2000020000~3000030000~50000>50000Workingpressurep（MPa）<0.8~11.5~22.5~33~44~55~7Tab.9-2WorkingpressureselectionforanactuatoraccordingtomainframetypeMainframetypeMachinetoolsAgriculturalmachinery,small-sizedengineeringmachinery,auxiliarydevicesforengineeringmachineryHydraulicpress,large-sizedexcavator,heavymachinery,liftingandconveyingmachineryGrin-derModularmachinetoolsPlanerDrawingbenchWorkingpressurep（MPa）≤23~5≤88~1010~1620~32Tab.9-1Workingpressureselec3.Drawingofworkingconditionchartoftheactuators

Afterthestructureparametersoftheactuatorsaredetermined,thepracticalworkingpressure,theflowrateandthepowercanbecalculatedaccordingtothedesigntaskanditsrequirements.Thenpressure(flowrate,orpower)—time(ordisplacement)curvescanbedrawnout,asshowninFig.9-3.Fig.9-3Workingconditionchartofactuators

1-Startupacceleration

2-Quickfeed

3-Workingfeed

4-Brake

3.Drawingofworkingconditio9.1.3Determinationofhydraulicsystemdiagram1.Analysisandselectionofthehydraulicscheme2.Analysisandselectionofthehydrauliccircuits3.Determinationofhydraulicsystemdiagram9.1.3Determinationofhydraul9.1.4calculationandselectionofhydrauliccomponents1.SelectionofpumpsAccordingtomaximumworkingpressureandprovidedflowratecalculatedabove,aproperpumpcanbeselectedfromproductsamples.Forthesakeofsafety,thechosenpumpmustbewitharatedpressure20%~60%higherthanthemaximumworkingpressure(describedabove)forpressurereserve,butwitharatedflowratejustmeetingthemaximumflowratetoavoidanexceedinglossofpower.2.Selectionofvalves9.1.4calculationandselectioTab.9-3Experientialvaluesofthepressurelossintheinletoilline

SystemconfigurationOverallpressureloss(MPa）Simplesystemwithgeneralthrottlespeed-regulatingcomponentsandpipelines0.2~0.5Complexsystemwithspeed-regulatingvalvesandpipelines0.5~1.53.SelectionofvalvearrangementsTherearethreetypesofarrangementsforhydraulicequipments(1)Modulartype(2)Manifoldplatetype(3)IntegratedblockTab.9-3Experientialvaluesof9.1.5Performancecheckforahydraulicsystemdesigned1.CheckingofthesystempressurelossThepressurelossincludesfrictionallossalongthepipelines,locallossinthepipelinesandtoalessproducedbythevalvecomponents.ThepressurelossofalongorlocalcanbecalculatedfromtheinvolvedexpressionsshowninChapter2,whilethelocallossofthevalvecomponentscanbeobtainedfromtheproductsamples.

Whenthepracticalflowrateqofavalvecomponentdoesn’tequalthenominalflowrate（9-4）9.1.5Performancecheckfora2.Checkingofthetemperaturerisecausedbyheatgenerationaccordingtoheatbalanceprinciple,whenthedimensionratiosofthreesidesofthereservoirarebetween1:1:1and1:2:3,theoilleveris80%thatofthereservoirheight,andthereservoirisingoodventilationCondition,then（9-5）Oncethecheckedoiltemperaturerisesurpassestheallowablevalue,apropercoolermustbesetinthesystem.Theallowableoiltemperatureriseinthereservoirisdifferentfordifferentmainframes2.Checkingofthetemperature9.1.6DrawingofworkingdiagramsandtechnicaldocumentsTheworkingdiagramsusuallyincorporatehydraulicsystemfigure,assemblydrawingandtheassemblyandpartDrawings.Theremustexistalistofcomponentsattachedtothehydraulicsystemfigure.Thesystemassemblyfigureistheconstructionanderectiondrawingforthehydraulicsystem.Generally,thetechnicaldocumentsincludetheexplanationsofdesigncalculation,manualtouseandmaintain,contentofparts,standardparts,universalparts,overalltableofoutsourcingparts,etc.9.1.6Drawingofworkingdiagr9.2ADesignExampleofHydraulicSystems9.2.1Analysisofworkingconditions9.2.2Determinationofmainparametersoftheactuator9.2.3Designofhydraulicsystems9.2.4Selectionofhydrauliccomponents9.2.5Performancecheckforhydraulicsystems9.2ADesignExampleofHydrau

Thissectionistostudythehydraulicsystemofasinglesidemulti-spindledrillmachinetool.axialcuttingforceoverallgrossweightG（N）Distanc-escoveredatrapidspeedDistanc-escovere-datworkspeedtherapidfeedandretractvelocityworkfeedvelocitytimeforaccelerationanddecelerationfrictioncoeffici-entofrestfrictionofmotionMechan-icalefficienc-yofthecylinder3000095001005050.00.9Thedynamicslipwayisrequiredtoachievesuchaworkcycle:rapidfeed→workfeed→blockdwell→rapidretract→stopattheoriginalposition.Thissectionistostudyt9.2.1AnalysisofworkingconditionsTheaxialcuttingforcewhichisalsotheonlyforcewhosedirectionishorizontal.Thentheinertiaforce,thefrictionofrestandthefrictionofmotionagainsttheguidewaycanbecalculatedasfollows9.2.1AnalysisofworkingcondTab.9-4Loadsonthecylinderineachworkstep

WorkingconditionLoadcombinationLoadF（N）ThrustStartup19002111Acceleration13541504Deceleration9501056Workfeed3095034389Rapidretract9501056TheloadsonthecylinderineachworksteparelistedinTab.9-4,wherethebackpressureintheoilreturnedchamberisneglected.TheloadandspeeddiagramsareindicatedinFig.9-4aandFig.9-4b.Tab.9-4Loadsonthecylinder

a)Load

b)Speed

Fig.9-4Loadandspeeddiagramsofthecylinder

a)Load9.2.2Determinationofmainparametersoftheactuator1）systempressure3）areaofcylinder2）

backpressure

Thecylinderareacanbecalculatedfromthethrustatworkfeedperiod:9.2.2DeterminationofmainpaThen

DanddmustbecorrectedtostandardvaluesaccordingtoGB2348－1997：,thenthepracticaleffectiveareasofthetwochambersofthecylinderareThepressure,flowrateandpowerateachworkstepasshowninTab.9-5.Theworkingconditionschartcanthenbedrawn,asindicatedinFig.9-5.ThenDanddmustbecorrectedTab.9-5Thepressure,flowrateandpowerateachstepTab.9-5Thepressure,flowratFig.9-5Workingconditionsdiagram

Fig.9-5Workingconditionsdia9.2.3Designofhydraulicsystems1.Selectionofhydrauliccircuits2.Designofhydraulicsystems3.Selectionofthehydraulicvalves9.2.3DesignofhydraulicsystFig.9-6PrinciplechartofhydraulicsystemFig.9-6PrinciplechartofhydFig.9-7PrinciplechatrofhydraulicsystemwithmodularvalvesFig.9-7Principlechatrofhyd9.2.4Selectionofhydrauliccomponents1.Pumps1）pressure2）flowrateThemaximumflowrateprovidedbythetwopumpsis25.13L/min.Iftheleakageinthereturnlineissupposed10%the