編號無錫太湖學院畢業設計（論文）相關資料題目：餃子機及輸送成型部件設計信機系機械工程及自動化專業學號：0923015學生姓名：指導教師：（職稱：副教授）（職稱：）201目錄一、畢業設計（論文）開題報告二、畢業設計（論文）外文資料翻譯及原文三、學生“畢業論文（論文）計劃、進度、檢查及落實表”四、實習鑒定表無錫太湖學院畢業設計（論文）開題報告題目：餃子機及輸送成型部件設計信機系機械工程及自動化專業學號：0923015學生姓名：指導教師：（職稱：副教授）（職稱：）2012課題來源自擬題目科學依據（包括課題的科學意義；國內外研究概況、水平和發展趨勢；應用前景等）（1）課題科學意義餃子食品機械的應用前景和發展現狀餃子食品在我國歷史悠久，伴隨著幾千年的文明的發展已經成為我國食品文化中的代表，如餃子、包子、餛飩是主食的一部分；湯圓、月餅、粽子是傳統節日中必不可缺的食物。如今，經濟的迅速增長、人民生活水平的提高和生活節奏的加快，對食品行業提出了新的要求。而本人認為這些要求可以歸納為兩大類：其一是食品的質量：如食用口感、衛生狀況、營養含量等。其二便是食品供應的速度。而解決這兩個矛盾要求的辦法便是實現食品生產的機械化和自動化，通過機械動作可以極大程度的提高食品的生產率；采用環保的機械材料和嚴格的密封技術可以很好的保證食品衛生；而合理的工藝編排更能改善食品的口感。（2）餃子機的研究狀況及其發展前景目前國內外廠家在包餡夾餡食品機械化上的研究已經取得了一定的成果成功研發了餃子機、包子機、餛飩機、湯圓機、月餅機以及自動化程度更高的全自動萬能包餡機。因東西方飲食文化的差異，目前國外包餡成型類機械主要為日本所生產，如日產的自動萬能包餡機，其最大生產能力可達每小時8000個，且加工范圍極廣，能生產各式饅頭、包子、餃子、夾餡餅干、壽司、等等近百種產品，采用可拆卸料斗能實現快速更換餡料，內置的無級變速調控裝置可以實現皮和餡的任意配比。廣泛用于各種帶餡食品的加工。而國內相關機械雖然在自動化和多功能方面較之日本產品還有一定的差距，但是通過改革開放以后二十余年的發展亦取得了很大的進步。以上海滬信飲料食品機械有限公司生產的水餃機為例：配備1.1Kw的電動機，生產效率達每小時7000個。已相當接近日產餃子機的生產水平。每逢過年過節現做現賣餃子往往出現供不應求的現象。當然也有很多人選擇在家里自己做餃子，卻需要提前半天甚至一天進行準備，而包餃子的時候更是要叫上好幾個親朋過來幫忙方可。因此如果能研究開發一種能夠以機械動作代替人工勞動的機器，那么除了可以節約大量的時間、降低餃子的生產成本、提高利潤之外，更可以免除人們冬日里冒寒排隊購物之苦，一舉多得。餃子生產機的初步目標確定為能夠實現子包餡工藝的機械化。未來可在此基礎上加以改進和擴展，以實現橫縱兩方向發展，即餃子生產全過程的無人干預自動化與多功能化研究內容①熟悉餃子機的工作原理與結構；②熟悉餃子機輸送成型部件的布置與結構；③熟練掌握絞龍、葉片泵的設計計算方法；④掌握ＣＡＤ的使用方法。擬采取的研究方法、技術路線、實驗方案及可行性分析（1）實驗方案對餃子機的整體的設計，確定面料和餡料的輸送方式與設備結構，確定餃子成型方式，使其能夠半自動的進行加工。（2）研究方法用ＣＡＤ進行二維畫圖，對餃子機結構有個全面的了解。對餃子機的輸送成型部分進行計算與結構設計，使其滿足物料的輸送要求，并加工出合適形狀的餃子。研究計劃及預期成果研究計劃：2012年10月12日-20122013年1月12013年1月282013年3月4日-2013年4月12013年4月15日-2013年4月29預期成果：達到預期的畢業設計要求，設計出的餃子機可以進行半自動加工，可以快速美觀的加工出餃子，并且輸送穩定有效、成型簡單、滿足工作要求。特色或創新之處①餃子機可以無需手工進行制作。②餃子制作過程安全，方便，快速，可以批量生產。已具備的條件和尚需解決的問題①設計方案思路已經明確，已經具備機械設計能力和餃子機方面的知識。②進行結構設計的能力尚需加強。指導教師意見指導教師簽名：年月日教研室（學科組、研究所）意見教研室主任簽名：年月日系意見主管領導簽名：年月日英文原文CaseStudyTheoreticalandpracticalaspectsofthewearofvanepumpsPartA.AdaptationofamodelforpredictivewearcalculationAbstractTheaimofthisinvestigationisthedevelopmentofamathematicaltoolforpredictingthewearbehaviourofvanepumpsuscdinthestandardmethodforindicatingthewcarcharactcristicsofhydraulicfluidsaccordingtoASTMD2882/DIN51389.Thederivationofthecorrespondingmathematicalalgorithmisbasedonthedescriptionofthecombinedabrasiveandadhesivewearphenomenaoccurringontheringandvanesofthepumpbytheshearenergyhypothesis,inconnectionwithstochasticmodellingofthecontactingroughsurfacesastwo-dimensionalisotropicrandomfields.Startingfromacomprehensiveanalysisofthedecisivering-vanetribocontact,whichsuppliesessentialinputdataforthewearcalculation,thecomputationalmethodisadaptedtotheconcretegeometrical,motionalandloadingconditionsofthetribosystemvanepumpandextendedbyinclusionofpartialelastohydrodynamiclubricationinthemathematicalmodej.Forcomparisonofthecalculatedwearbehaviourwithexpenmentalresults,atestseriesonarigdescribedinPartBwascarriedout.Amineraloil-basedlubricantwithoutanyadditiveswasusedtoexcludetheinfluenceofadditiveswhichcannotbedescribedinthemathematicalmodel.Agoodqualitativecorrespondencebetweencalculationandexperimentregardingthetemporalwearprogressandtheamountofcalculatedwearmasswasachieved.Keywords:Mathematicalmodelling;Simulationofwearmechanisms;Weartestingdevices;Hydraulicvanepumps;Elastohydrodynamiclubrication;Surfaceroughness1.IntroductionInthisstudy,thepreliminaryresultsofanewmethodologicalapproachtothedevelopmentoftribo-metersforcomplicatedtribosysLemsarepresented.Thebasicconceptinvolvesthederivationofamathematicalalgofithmforwearcalculationinaninteractiveprocesswithexperiments,whichcanbeusedmodelofthetribosystemtobesimulated.Inthisway,anadditionaldesigntooltoachievethecorrelationofthewearratesofthemodelandoriginalsystemiscreated.TheinvestigationsareperformedfortheVickersvanepumpV104CusedinthestandardmethodforindicatingthewearcharacteristicsofhydraulicfluidsaccordingtoASTMD2882/DIN51389.Inafirststep,amathematicaltheorybasedonthedescriptionofabrasiveandadhesivewearphenomenabytheshearenergyhypothesis,andincludingstochasticmodellingofthecontactingroughsurfaces,isadaptedtothetribologicalrealityofthevanepump,extendedbyaspectsofpartialelastohydrodynamiclubricationandverifiedbycorrespondingexperiments.PartAofthisstudyisdevotedtothemathematicalmodellingofthewearbehaviourofthevanepumpandtotheverificationoftheresultingalgorithm;experimentalwearinvestigationsrepresentthefocalpointofPartB,andthesearecomparedwiththeresultsofthecomputationalmethodderivedinPartA.2.AnalysisofthetribocontactTheVickersvanepumpV104Cisconstructedasapumpforconstantvolumeflowperrevolution.Thesystempressureisledtothebottomsideofthe12vanesintherotorslotstosealthecellsformedbyeachpairofvanes,thering,therotorandthebushingsinthetribologicallyinterestinglinecontactofthevaneandinnercurvatureofthering(Fig.1).Simultaneously,allothervanesidesarestressedwithdifferentandperiodicallyalternatingpressuresofthefiuid.Acomprehensivestructureandstressanalysisbasedonquasistaticmodellingofallinertialforcesactingonthepump,andconsideringtheinnercurvatureofthering,theswivelmotionofthevanesinrelationtothetangentofcurvatureandtheloadingassumptions,isdescribedinRefs.[1-3].Thereby,acharacteristicgraphforthecontactforceFeasafunctionoftheturnanglecanbeobtained,whichdependsonthegeometryofthevanesusedineachrunandthesystempressure.Fromthis,theinnercurvatureoftheringcanbedividedintofourzonesofdifferentloadingconditionsinvane-ringtribocontact(Fig.2),whichisingoodagreementwiththewearmeasurementsontherings:intheareaofmaximumcontactforce(zonen),thehighestlinearwearcouldbefound[2,3](seealsoPartB).3.Mathematicalmodelling3.1.BasicrelationsforwearcalculationThevaneandringshowcombinedabrasiveandadhesivewearphenomena(Fig.3).ThebasicconceptsofthetheoryforthepredictivecalculationofsuchwearphenomenaaredescribedinRefs.[4-6].Startingfromtheassumptionthatweariscausedbysheareffectsinthesurfaceregionsofcontactingbodiesinrelativemotion,thefundamentalequation(1)forthelinearwearintensityIhinthestationarywearstatecanbederived,whichcontainsthespecificshearenergydensityes/ro,interpretableasamaterialconstant,andtherealareaArsoftheasperitycontactsundergoingshear.Todeterminethisrealcontactarea,thede-scriptionofthecontactingroughsurfacesastwo-dimensionalisotropicgaussianfieldsaccordingtoRef.[7]isincludedinthemodelling.Thustheimplicitfunctionalrelationwiththeweightfunction(2)isfound,whichcanbeusedtocalculatethesurfaceratioinEq.(1)forunlubricatedcontactsfromthehertzianpressurePaactingintheinvestigatedtribocontactbyacomplicatediterativeprocessdescribedinRefs.[6,8].TheconcretestructureofthefunctionsFandcdependsontherelativemotionofthecontactingbodies(sliding,rolling).Theparametera-（m0m4）/m22representsthepropertiesoftheroughsurfacebyitsspectralmoments,whichcanbedeter-minedstatisticallyfromsurfaceprofilometry,andtheplasticityindex妒=(mOm4)y4(E'/H)isameasureoftheratioofelasticandplasticmicrocontacts.3.2.ExtensiontolubricatedcontactsThealgorithmresultingfromthebasicrelationsforwearcalculationwasappliedsuccessfullytounlubricatedtribosystems[8].ThefirstconceptsforinvolvinglubricationinthemathematicalmodelaredevelopedinRef.[8].Theyarebasedontheapplicationoftheclassicaltheoryofelastohydrodynamiclubrication(EHL)tothemicrocontactsoftheasperities,neglectingthefactthatthereisalsoa"macrolubricationfilm"whichseparatesthecontactingbodiesandisinterruptedinthecaseofpartiallubricationbytheasperitymicrocontacts.Thereforetheiruseforcalculatingpracticalwearproblemsleadstounsatisfactoryresults[9].Theyareextendedherebyincludingthefollowingassump-tionsinthemathematicalmodel.(1)Lubricationcausestheseparationofcontactingbodiesbyamacrofilmwithameanthicknessu.whichcanbeexpressedintermsofthesurfaceroughnessby[10](3)Whereu0isthemeanfilmthinknessaccordingtoclassicalEHLtheorybetweentwoideallysmoothbodies,whichcanbedeterminedforlinecontactofthevaneandringby[11](2)Inthecaseofpartiallubrication,themacrofilmisinterruptedduringasperitycontacts.Aplasticmicrocontactisinterpretedasapuresolidstatecontact,whereasforanelasticcontacttheroughnessissuperimposedbyamicrolubricationfilm.Becauseofthemodellingoftheasperitiesassphericalindenters,themicrofilmthicknesscanbedeterminedusingtheEHLtheoryforsphere-planecontacts,whichisrepresentedintherandommodelbytheslidingnumber[8](5)(3)Thehertzianpressureactinginthemacrocontactworksintwoparts:asahydrodynamicpressurepEHbornebythemacrolubricationfilmandasapressurepFKbornebytheroughnessinsolidbodycontact.(4)Forpuresolidstatecontacts,itisassumedthatthelimitforthemeanrealpressureprFKwhichanasperitycanresistwithoutplasticdeformationcanbeestimatedbyone-fifthtoone-sixthofitshardness(6)InvestigationsonthecontactstiffnessinRef.[11]haveledtotheconclusionthattheelasticpropertiesofthelubricationfilmcauseareliefoftheasperities,whichmeansthattherealpressureworkingontheasperityisdamped.Therefore,inthemathematicalmodelforlubricatedtribosystems,anadditionaltermfffin,whichcorrectstheupperlimitoftherealpressureasafunctionofthefilmthickness,isintroducedp,EH=prFK[1-fcorr(U)](7)Thisformulacanbeusedtodetermineamodifiedplasticityindex{PEHforlubricatedcontactsaccordingtoRef.[8].Altogether,thebasicmodelforwearcalculationcanbeextendedforlubricatedtribosystemsbyreplacingrelation(2)by(8)(3)3.3.Adaptationtothetribo’systemvanepumpToapplythemathematicalmodelforwearcalculationtoaconcretetribosystem,allmaterialdata(specificmaterialandfluidproperties,roughnessparameters)usedbythealgorithmmustbedetermined(seePartB).Moreover,themodelmustbeadaptedtothemechanicalconditionsofthewearprocessinvestigated.Ontheonehand,thisisrelatedtotherelativemotionofthebodiesintribocontact,whichinfluencestheconcretestructureoffunctionfinformulae(2)and(8).Inthecaseofvane-ringcontact,slidingwithsuperimposedrollingduetotheswivelmotionofthevaneswasmodelled(9)Adetailedderivationofthecorrespondingformulaeforfslidingandf.ollingcanbefoundinRefs.[8,9].Ontheotherhand,thehertzianpresstirePaactingontribocontactduringthewearprocesshasanesseritialimportanceinthewearcalculation.Forthetribosystemvanepump,themeancontactforceFeineachloadingzonecanberegardedasconstant,whereasthehertzianpressuredecreaseswithtime.Thereasonforthisistheweardebrisonthevane,whichcausesachange'nthevanetipshapewithtime,leadingtoanincreasedcontactradiusand,accordingly,alargercontactareaTodescribethisphenomenonbythemathematicalwearmodel,thevolumeremovalWvlofonevaneintermsoftherespectivecontactradiusRi(t)attimetandtheslidingdistanceSR(Rl(t》isgivenby(10)wheretheconstantsaandbcanbedeterminedbyregressionfromthegeometricaldataofthetestedvanes.ThecorrespondingslidingdistancenecessarytoreachacertainradiusRiduetovanewearcanbeexpressedusingthebasicequation(1):(11)Thus,applyingEq.(11)togetherwithEq.(10)totherelation(12)itispossibletoderivethefollowingdifferentialequationfortherespectivevolumeremovalWvllofthering,whichcanbesolvedbyanumericalprocedure(13)TherequiredwearintensitiesofthevaneandringcanbecalculatedbyEq.(8)asafunctionofthecontactradiusfromthehertzianpressuresworkingineachloadingzone,whichareavailablefromthecontactforcebythewell-knownhertzianformulae.3.4PossibilitiesofverificationIfallinputdataareavailableforaconcretevanepumprun(theconcretegeometrical,materialandmechanicalconditionsinthecartridgeusedandthespecificfluidproperties,seePartB),themathematicalmodelforthecalculationofthewearofvanepumpsderivedabovecandescribequantitativelythefollowingrelations.(1)TheslidingdistanceSR(RI)and,ifthenumberofrevolutionsofthepumpandthesizeoftheinnerringsurfaceareknown,therespectiveruntimetofthepumpwhichisnecessarytoreachacertainshapeofthevanetipsduetowear.(2)ThevolumeremovalW,.:uri(t)andthewearmassesWmW(t)ofthevaneandringasafunctionoftheruntimet.(3)ThemeanlocallinearwearWl(t)ineveryloadingzoneontheringattimet.Thusanimmediatecomparisonbetweenthecalculatedandexperimentallyestablishedwearbehaviour,withregardtothewearprogressintime,thelocalwearprogressontheringandthewearmassesatacertaintimet,becomespossible.4。ResultsInthisstudy,theverificationofthetheoreticalresultsobtainedbycomparisonwithexperimentsisbasedonatestseriesonarigaccordingtoDIN51389describedindetailinPartB.Thesamemineraloil-basedlubricant,withoutanyadditives,wasusedineachruntoexcludetheinfluenceofadditivesonthewearbehaviour,whichcouldnotbedescribedinthemathematicalmodel.Asinputdataforthecalculation,themeanvaluesofallthequantitiesneededbythealgorithmweredeterminedfromfour250htestrunswhichwerecarriedoutunderequivalenttestconditions.Thefollowingresultswereobtained.(1)Thecalculatedtemporalwearcurveforthevanes,resultingfromapproximation(9),isingoodqualitativeagreementw:iththemeasurementsinRef.[2](degressivecharacterandlengthoftheinletphase(seePartB》.Moreover,thecalculatedwearmassesafteraruntimeof250hcorrespondquantitativelywiththeexperimentalresults(Fig.5).(2)Forthering,adegressrveweartrendwasfoundbycalculation,whichisassumedtobearealisticresultinassociationwiththecorrespondingdegressivetrendofvanewearexperimentallyestablishedinRef.[2].Thecalculatedtotalwearmasses,whichrepresentthesumofthewearmassesachievedineachloadingzoneattimet,conformwiththewearmassesmeasuredin250hrunsaswellasshort-timerunsof10h(Fig.6).(3)ThewearmassescalculatedforeachseparateloadingzoneontheringareinquantitativeagreementwiththecorrespondingorderofthecontactforceFe(Fig.6).(4)Thedependenceofthewearbehaviourontemperatureduringtribocontact,representedinthemathematicalmodelbythedependenceofthelubricantpropertiesontemperature,issuitablyreflectedbythecalculation(Fig.7).Furtherresults,especiallywithregardtoacomparisonofthecalculatedandmeasuredlocallinearwearonthering,aredcscribcdinPartB.5.ConclusionsThemathematicalalgorithmforthecalculationofwearonvanepumpspresentedinthisstudyenablestheexperimentallyestablishedwearbehaviourofthetribosysteminvestigatedtoberetracedqualitativelyandquantitatively.Thustheextensionsintroducedtocoverpartialelastohydrodynamiclubricationhaveprovedasuccessandrepresentanessentialimprovementoftheresultsachievedsofar[9].Inthisway,thepreconditionsforthedevelopmentofamathematicaltoolforwearpredictionandforsimulationofthewearbehaviourofatribometerforthetribosystemvanepumphavebeencreated.Forfurtherqualificationofthemathematicalmodeltoachievearealforecastofthewearbehaviour,theoreticalinvestigationscombinedwithexperimentsmustbeenforced,espeaallywithregardtothefollowingtopics:(1)inclusionoftheinletphaseofthewearprocessinthemodel(sofar,themathematicalmodelisrelatedonlytothestationarywearstate;analgorithmmustbecreatedwhichisbasedexclusivelyontheinputdataobtainablebeforestartingthewearprocessandwhichcansuccessivelyadaptthedatausedbythecalculationtorealwearprogress);(2)extensionofthemodeltopracticallyimportantlubricantswithadditives(thiscanbeachievedinafirststepbyusingaheuristicrelationtodescribetheinfluenceofadditivesonthewearbehaviour,derivedfromcorrespondingtestScrieSwithscVerallubricants).中文譯文在理論和實踐方面葉片泵磨損的研究（A部分）:為適應預測磨損計算模型R.Gellricha,A.Kunzb,G.Beckmann‘,E.Broszeitba大學科技，經濟和社會科學Zittaul/Gorlitz，數學和自然科學學院，Th.-Kiirner-阿利16處，02763齊陶，德國

b材料科學研究所，達姆施塔特技術大學，Grafenstr。二，64283達姆施塔特，GermanyPetersilienshz二維，03044科特布斯，德國

1994年3月29摘要本次調查的目標是預測用于判斷液壓流體的磨損特性的葉片泵的磨損行為的一種數學工具的發展，根據ASTMD2882/DIN51標準方法389。相應的數學算法的推導是基于合并后的描述和磨料粘著磨損現象發生在環和假說的剪切能在葉片泵連接，與隨機建模為二維各向同性隨機粗糙表面接觸領域。從環葉片摩擦接觸的決定性全面分析開始，為磨損計算，適應具體的幾何，運動和摩擦系統葉片泵的負荷條件，被部分彈流潤滑延長列入數學模型的計算方法提供了必要的輸入數據。對于磨損性能的計算與試驗結果的比較，對鉆機的一系列測試在B部分的敘述中會提出。不含任何添加劑的礦物油基潤滑劑，采用排除添加劑的影響，不能在數學模型描述出來。在計算和實驗之間的一個良好的定性關系隨著時間磨損過程和計算磨損質量的量達到了。關鍵詞：數學模型;磨損機理模擬;磨損試驗裝置，液壓葉片泵;彈流潤滑;表面粗糙度簡介在這項研究中，對于復雜的摩擦系統摩擦計的發展的一種新的方法的初步結果被提出來了。這個基本概念涉及到一個在實驗的相互影響的過程中的的磨損計算的數學算法的起源，它可用于預測的摩擦磨損性能系統的力學模型可以模擬互動的過程推導。這樣，一個額外的設計工具，實現了模型和原系統的磨損率的相關性創建。調查是執行了用于判斷按照美國ASTM2882/DIN51389D型液壓流體的磨損特性威格士葉片泵V104的標準方法。在第一個步驟，一個以磨料和粘結磨損現象的描述剪能量假說為基礎，包括隨機粗糙表面接觸模型的數學理論，是適應了現實的葉片泵摩擦磨損，延長了部分問題彈流潤滑和相應的實驗驗證。這項研究的一個部分是專門用來對葉片泵的磨損行為的數學模型，并由此產生的算法驗證;實驗磨損調查代表了B部分的焦點，這些都是與計算方法和在A部分所得結果進行比較2．分析部落接觸威格士葉片泵V104C是一個每轉流量不變的泵。系統壓力導致了在轉子槽12個葉片的底部來封住由每一個葉片環槽盒和葉片的線接觸和環的內部彎曲組成的單元。同時，所有其他的不同的和定期交變的流體壓力葉片面也都被強調了。一個在泵慣性力作用的所有準靜態建模，考慮到環內曲率，和切線曲率和裝載假設相關的葉片旋轉運動在文獻中有描述，從接觸力F的特征圖上，作為轉角度的功能可以得到，這由每次運行和系統壓力所使用的葉片幾何形狀而定。由此可見，環內彎曲可分為葉片環摩擦接觸（圖2）這與上環的磨損測量吻合分為四種不同的負荷條件區：在最大接觸面積部分（第二區），最高的線性磨損可以發現[2,3]（見B部分）3．數學建模3.1．磨損計算基本關系葉片和環形顯示聯合磨料和粘結磨損現象（圖3）。預測磨損計算現象的理論的基本概念在文獻中有描述。【4-6】。從磨損是由在具有相對運動的接觸表面的高剪切效應引起的這個假設開始，基本方程如下：（1）在靜態磨損狀況中的線性方程組的磨損強度I可以得到，，其中包含具體的剪能量密度，可作為材料常數解釋，和真正的A區粗糙的接觸發生型剪切，為了確定這個實際的接觸面積，作為二維的基礎粗糙表面的描述根據文獻中的高斯領域。[7]是包含在建模。因此，隱函數關系被發現，它可以用來計算式中的表面比。（1）從赫茲壓力作用的研究摩擦接觸，由一個復雜的迭代過程每年在文獻中描述無潤滑接觸。[6,8]。對混凝土結構的函數F和c取決于身體的接觸（滑動，滾動）的相對運動。參數：u=通過它光譜表示了表面粗糙度的特性，也可以由表面的輪廓決定，塑性指數是彈性和塑性比例的量度。3.2擴展到潤滑接觸這個算法由摩擦計算的基本關系被成功應用于無潤滑摩擦學系統引出[8]。對于涉及數學模型中的潤滑的第一概念在文獻中被開發。[8].他們是基于彈流潤滑的經典理論，以粗擦的微接觸的應用，忽視了也有一個微膜隔開了這個連接機構在微接觸的部分潤滑情況下被打斷這個事實。因此用它們來做的磨損問題的實際計算不理想。他們在這里延伸，包括在數學模型的以下假設。潤滑導致了通過平均厚度為U的微膠卷的接觸機構的分離，它可以依據通過（10）的表面粗糙度表示(3)其中u是根據兩個非常光滑機構之間經典的彈流理論的平均膜厚，可以通過[11]的風向標和環的線接觸決定（4）在部分位置的情況下，微膜在粗接觸時被中斷。一個塑料微接觸被解釋為純固態接觸，而對于一個彈性接觸表面粗糙度是通過微潤滑膜疊加的。由于作為球型壓頭的粗糙的造型，微縮膠片的厚度可以由使用的球平面接觸彈流潤滑理論確定，代表了隨機滑數模型。[8]