理工學院畢業(yè)設計（論文）外文文獻翻譯PAGEPAGE1氣動馬達的設計與研究杜長龍楊善國楊秀（機電材料工程學院中國礦業(yè)科技大學，蘇州，221008，中國）摘要：氣動馬達是將壓力能轉(zhuǎn)換為機械能的能量轉(zhuǎn)換裝置，特點為防爆、負載安全、絕不燒損、無段速度控制、緊急動力驅(qū)動、瞬間正逆轉(zhuǎn)向、安裝靈活、可在電動馬達、油壓馬達、步進馬達、伺服馬達不適用場合下使用。多種減速比可供選配。結構簡單、體積小、重量輕、操作容易、維修方便。廣泛用于攪拌設備、涂裝設備、食品藥物包裝、研磨機、礦井設備及自動生產(chǎn)線等設備上。在對現(xiàn)今氣動葉片電機結構原理分析的基礎上,,我們提出了氣動葉輪液壓馬達這一設想，并對此進行了研究。MFT80Y類型的氣動馬達的構造原理，是旋轉(zhuǎn)剪切機制研究的新項目。它整合了氣動葉片電機以及行星齒輪減速裝置。旋轉(zhuǎn)剪切機制的數(shù)學模型力求優(yōu)化設計，按照MATLAB優(yōu)化工具箱的指令而繪制。MFT80Y類型的氣動馬達的性能，設計優(yōu)化，經(jīng)現(xiàn)場試驗。關鍵詞:錨桿鉆機,氣動馬達、優(yōu)化設計0.簡介由于單電源，重量輕，輸出性能優(yōu)良等特點，氣動錨桿鉆機已被廣泛應用于礦井設備。根據(jù)氣動馬達的不同結構，氣動錨桿分為缸電機，齒輪電機，葉片電機三種類型。其中，葉片馬達類型結構最優(yōu)。特點是：尺寸小，輸出功率大，低噪音，低扭矩脈動。此外，在葉片頂端磨損和撕裂后，它還可以自動延伸到補償。本文旨在設計及研究氣動錨桿鉆機，在強調(diào)旋轉(zhuǎn)剪切機構的優(yōu)化設計同時，介紹樣機的研究和工業(yè)性試驗結果。1.構造原理新設計的MFT-80Y型氣動錨桿鉆機馬達葉片如圖1所示。它主要構成旋轉(zhuǎn)剪切機制，推進機制和運行機制。其中，旋轉(zhuǎn)剪切機制是由葉片氣動電動機，一個階段的行星齒輪箱和供水系統(tǒng)構成。;推進機制是由具有兩個玻璃纖維伸縮腿和輔助配件的三個階段構成。運行機制實行一體化操作處理。圖1MFT-80Y型錨桿鉆機當壓縮空氣通過操作閥門的運行機制進入葉片氣動時，MFT-80Y型錨桿鉆機開始旋轉(zhuǎn)，進入工作狀態(tài)。2扶輪剪切機構氣優(yōu)化設計扶輪剪切機構是氣動錨桿鉆機的重要組成部分。為了使整個錨桿鉆機結構緊湊，并完善其功能，以更好地滿足消費者的實際需求，本文將采用現(xiàn)代設計方法對扶輪剪切機構進行參數(shù)優(yōu)化設計。

處于工作狀態(tài)的氣動電機轉(zhuǎn)速通常高達每分鐘旋轉(zhuǎn)幾千轉(zhuǎn)，而設計的扶輪剪切機構輸出轉(zhuǎn)速是每分鐘旋轉(zhuǎn)幾百轉(zhuǎn)。錨桿鉆機通常包括氣動馬達和速度降低設備。本設計采用單一行為離子葉片氣動電機和行星齒輪減速裝置。（如圖2所示）圖2RSM的準則2.1目標函數(shù)和設計變量根據(jù)實際工程中應用的離子要求,此設計以采用最低數(shù)量的扶輪剪切機構為目標。缸體的內(nèi)半徑構成了氣缸的容量。氣缸的容量主要決定氣動電機的尺寸和量。太陽齒輪的體積和整個行星齒輪的體積和影響并決定行星齒輪箱的尺寸和量。那么V=V1+V2即可看作扶輪剪切機構優(yōu)化設計的目標功能。即：根據(jù)它的行星齒輪系統(tǒng)條件之間的關系，氣動馬達的與齒輪箱輸出轉(zhuǎn)動力矩的位移關系公式，以及葉片氣動馬達的位移公式公式如下：在公式(1)和(2)中R,B、e、Z、p、分別是定子內(nèi)半徑，轉(zhuǎn)子寬度、偏心距離,葉片數(shù)量、葉片厚度。表明氣動馬達的輸入和輸出空氣壓力和容積效率之間的差別。m,b,Za,c,T分別代表齒輪模數(shù)、齒輪寬度、數(shù)目、數(shù)字太陽齒輪的行星齒輪、輸出力矩和剖析行星變速箱的效率。通常情況下,有3個行星齒輪，所以獨立參數(shù)將會影響容量V，R,B，e,Z,m,b,Za所以設計變量為：目標函數(shù)設計變量可以是:2.2限制性條件

2.2.1幾何限制

（1）根據(jù)內(nèi)部半徑為R的定子，轉(zhuǎn)子寬度為B，葉片數(shù)，葉片厚度的經(jīng)驗公式，幾何限制為：（2）按不削弱齒輪，齒輪寬度，相鄰的行星齒輪限值條件，以及齒輪裝配條件，幾何約束條件為：除上述幾何限制外，每個設計變量必須在零以下。2.2定子葉片氣動馬達的運用公式,可以寫作如下:該公式中是葉片旋轉(zhuǎn)角。（1）氣動馬達葉片的相對滑動速度的限制性條件可以直接寫為：(2)氣動馬達的最高線速度的限制條件可直接寫為:(3)聽覺接觸疲勞強度的限制：（4）聽覺根彎曲疲勞強度的限制：綜上所述,數(shù)學模型的優(yōu)化設計就是一個最優(yōu)化的問題，它構成8個變量,以及27個平等和不平等限制條件。如下所示：基于以上優(yōu)化設計模型(3),通過MATLA工具箱，實現(xiàn)了扶輪剪切機構參數(shù)最優(yōu)化。3.性能參數(shù)和工業(yè)測試通過上述優(yōu)化方法，我們完成了MFT-80Y型葉片氣動馬達發(fā)動機性能參數(shù):(1)巖硬度<=8;(2)工作氣壓0.40~0.63兆帕;(3)額定功率2.6千瓦;(4)額定的離子扭矩80KN;(5)最大扭矩120KN;(6)負荷離子速度0~750轉(zhuǎn)/分鐘;(7)推動力5kN。國內(nèi)兩家知名企業(yè)已對該樣機進行了工業(yè)測試，測試結果顯示的是:與同一類型的機器相比,它有如下特性：輸出功率大、噪音低、巖石鉆探能力強，鉆井速度快,操作簡單。由此可知，采用最優(yōu)方法設計的MFT-80Y類型葉片電機、結構簡單，使用方便，工作性質(zhì)良好，結構簡單而緊湊，,可應用到煤礦等領域。4總結(1)本文涉及的氣動錨桿鉆機馬達葉片的優(yōu)點為：體積小、重量輕，，結構簡單,使用方便，運行穩(wěn)定。是錨桿中的最優(yōu)類型。(2)本品第一次整合葉片氣動馬達與行星變速箱，并采用最優(yōu)設計方法達到參數(shù)最優(yōu)化，實現(xiàn)該產(chǎn)品的最優(yōu)設計。(3)此試驗表明采用最優(yōu)設計方法設計的產(chǎn)品取得了令人滿意的結果。參考文獻：[1]楊善國.錨桿鉆機氣動葉片電機的研究[D]。徐州:中國礦業(yè)科技大學.2001[2]杜長龍.錨桿鉆機的設計與研制[J].中國礦業(yè)科技大學學報.2002(1):92~95[3]杜長龍.礦山機械的應用程序和優(yōu)化設計的數(shù)學模型[M].北京:煤炭工業(yè)出版社,1998,124~13DesignandresearchonpneumaticvanemotorroofbolterDUChanglongYANGShanguoYANGXiu（CollegeofMechatronicandMaterialEngineering，ChinaUniversityofMiningandTechnology，Xuzhou221008China）Abstract：Pneumaticmotoriswillstresscanconvertmechanicaldevicethatconvertsenergycharacteristicsforexplosion-proof,loadsecurity,neverburning,segmentlessspeedcontrol,emergencydriving,instantarereversedto,installationflexible,canbeinelectricmotors,hydraulicmotor,steppingmotor,servomotornotapplicableoccasionsuse.Avarietyofslowthanavailableforselection.Simplestructure,smallvolume,lightweight,easyoperationandeasymaintenance.Widelyusedformixingequipment,coatingequipment,foodanddrugpackaging,grindingmachine,miningequipmentandautomaticproductionlineequipment.Onthebasisofanalysisofthepresentroofboltersstructures,thepneumaticvanemotorroofbolterwasproposedandresearched.StructureprincipleofMFT80Ytypepneumaticvanemotorroofbolterwasexpounded,anewprojectoftherotaryshearingmechanismwithintegratingpneumaticvanemotorwithepicyclicreductiongearunitwascarriedout,themathematicalmodelforoptimumdesignoftherotaryshearingmechanismwassetup,andtheoptimumdesignfortherotaryshearingmechanismwasmadebyMATLABOptimizationToolbox.Finally,performanceofMFT-80typepneumaticvanemotorroofboltermadewithoptimummethodandtheonsiteexperimentwereintroduced.Keywords：roofbolter,pneumaticmotor,optimumdesign0.IntroductionPneumaticroofbolterhasnowbeenwidelyusedinthecoalmineroadwayroofboltingduetothefeaturessuchasexcellentoutputproperty，singlepowerandlightweight，Pneumaticroofboltersaredividedintothreetypeswhicharecylindermotortype，gearmotortypeandvanemotortypeaccordingtothedifferentstructureofthepneumaticmotor。Amongthem，vanemotortypeistheoptimumtypeofstructurebecauseitcanoutputgreaterpowerwithsmalldimension，anditcanautomaticallyextendtocompensateafterthevanetopiswornandtorn，andbecauseofitsstableoperation，lownoiseandsmalltorquepulsation。Thisarticlewilldesignandresearchintopneumaticvanemotorroofbolter，whichwillemphasizetheoptimumdesignoftherotaryshearingmechanismandintroducethesamplemachineandindustrialtestresults。StructureprincipleThenewlydesignedMFT-80Ytypevanemotorpneumaticroofbolterisshowninfig.1.Itmainlyconstitutesrotaryshearingmechanism,propellingmechanismandoperatingmechanism.Amongthem,rotaryshearingmechanismismadeupbyvanepneumaticmotor,onestageplanetarygearboxandwatersupplysystem;propellingmechanismismadeupbythreestageswithtwotelescopicglassfibrepneumaticlegandauxiliaryparts;operatingmechanismisintegrationbycombinationvalveandoperatinghandle.Fig.1MFT-80YtyperoofbolterWhenitsworking,thecompressedairentersthevanepneumaticmotorviatheoperatingvalveoftheoperatingmechanism,makesitrotate,reducesthespeedviaonestageplanet,andpowerstheroofboltingtiptodrilltherock5atthesametimeWthecompressedairenterstheglassfibrereinforcedplasticpneumaticlegviatheoperationvalvegrouptodrivethedrillingrodsandtipsupward。thenrealizestheroofboltingholeformationRWhendrillingtherockandformingthehole。hydrostaticwaterisusedtogothroughthecentricholeofthedrillingrodtoenterthedrillingtipstoaccomplishthecoolinganddustextermination。Rotaryshearingmechanism(RSM)optimumdesignRSMisthecriticalpartofpneumaticroofbolter.Inordertomakethewholearrangementofroofboltercompactandimprovetheroofbolterfunctionsoastobettermeetthepracticalrequirementsofroofbolting,thisarticlewillmakeparameteroptimumdesignontheRSMbythemoderndesignmethod.Becausetheworkingrotativevelocityofthepneumaticmotorisnormallyashighasseveralthousandrotationperminute,whilethedesignoutputrotativevelocityoftheRSMisjustseveralhundredrotationperminute,theRSMusuallyincludespneumaticmotorandspeedreducingequipment.ThisdesignadoptssingleactionvanepneumaticmotorandonestageepicyclicreductionpneumaticmotorshowninFig.2).Fig.2RSMprinciple2.1TargetfunctionanddesignvariablesAccordingtothepracticalapplicationrequirement,thisdesigntakestheminimumvolumeoftheRSMastargetfunction,andconsiderseachrictwithrestrictforms.BecausethecylindervolumeV1whichisformedbythestatorwhoseinsideradiusisRbasicallydeterminesthedimensionsandvolumeofpneumaticmotor,andthesumofsungearvolumeandthewholeplanetarygearvolumeV2canaffectanddeterminethedimensionsandvolumeofplanetarygearbox,thenV=V1+V2istakenasthetargetfunctionoftheRSMwholeoptimumdesign,thatisAccordingtotheconcentricconditionofplanetarygearsystem,therelationshipformulabetweenthedisplacementofpneumaticmotorandgearboxoutputrotationtorque,anddisplacementformulaofsingleactionvanepneumaticmotor,formula(1)isarrangedas[1]Intheformula(1)and(2),R,B,e,Z,p,arerespectivelytheinsideradiusofthestator,rotorwidth,eccentricdistance,vanenumber,vanethickness,thedifferencebetweeninputandoutputairpressureandvolumetricefficiencyofthepneumaticmotor;m,b,Za,c,T,arerespectivelygearmodulus,gearwidth,numberofsungear,numberofplanetarygear,outputtorqueandefficiencyofplanetarygearbox.Normallythenumberofplanetarygearis3,sotheindependentparameterswhichwillaffectvolumeVareR,B,e,Z,m,b,Za,sothedesignvariablesareselectedas:Thetargetfunctionindicatedindesignvariablescanbeshownas:2.2Restrictiveconditions2.2.1Heometricrestrictions(1)AccordingtotheexperientialformulabetweenstatorinsideradiusRandeccentricdistance。theexperientialformulabetweenrotorwidthBandstatorinsideradius,vanenumber,andvanethickness,thegeometricrestrictionsareshownas:(2)Accordingtonoundercutofgear,valuelimitsofgearwidth,planetarygearadjoiningCondition,andgearassemblycondition,thegeometricrestrictionconditionsareshownas:Excepttheabovegeometricrestrictions，eachdesignvariablemustbeabovezerothatis:2.2Literature[1]grantstheconditionofvanenoneextricatingfromthestatorofsingleactionvanepneumaticmotor,whichiswrittenasthefollowing:Intheformula：（）isthevanerotaryangle:Therestrictiveconditionofrelativeslidingvelocityvofpneumaticmotorvaneintherotorslotcanbedirectlywrittenas：Therestrictiveconditionofhighestlinevelocityofpneumaticmotorrotorcanbedirectlywrittenas：Hearfacecontactfatiguestrengthrestriction：Hearrootbendingfatiguestrengthrestriction：Tosumup，theoptimumdesignmathematicalmodelofRSMisanoptimumproblemthatconstitutes8designvariables，27inequalityrestrictionsandanequalityrestriction.Itcanbeindicatedas：Basedontheaboveoptimumdesignmodel（3），TheRSMparametersoptimizationisrealizedbyMATLABoptimumtollbox。3.PerformanceparametersandindustrialtestTheperformanceparametersoftheMFT-80Ytypevanemotorpneumaticroofbolterwhichisfinishedwiththeaboveoptimummethodare:（1）Rockhardness＜＝8;（2）Workingairpressure0.40~0.63MPa;（3）Ratedpower2.6kW;（4）Ratedrotationtorque80Nm;（5）Maximumtorque120Nm;（6）loadrotationspeed0~750r/min;（7）Propellingforce5kN.IndustrialtesthasbeencarriedoutonthesamplemachineinYaoqiaoCoalMineofDatunCoalandElectricCompanyandinZhangjiCoalMineofXuzhouCoalMiningGroup.Thetestresultsshows:comparedwiththesametypeofmachines,ithasthefollowingcharacteristicssuchasgreatoutputpower,lownoise,strongrockdrillingcapability,rapiddrillingspeed,andexcellentfeelingwheninoperation.Fromt