大型多级离心泵机组轴系的扭转振动分析

515201410PROCESSEQUIPMENT&PIPINGVol.51No.5Oct.20142014-08-13[2007]1187163714ADAMSAPI610TQ051.2TH311A1009-3281201405-0057-0051000kWAPI610[1][2-4][5][6],[7],,MATLAB,[8]ANSYSADAMS[9]ANSYS[10]ADAMSAPI610.17500r/min103500m1515·58·Table1Parametersofthemulti-stagepumpQHn100m3/h3500m7500r/min10Fig.1Structureofthemulti-stagepumpunit.232Fig.2Threedimensionalmodelofthegears4Table2Parametersofthemulti-stagepumprotorsystem/kg400091.535488131/(kg·m2)860.620.13893.4Fig.3CalculationGridsofthemulti-stagepumprotorFig.4Virtualprototypemodelofthemulti-stagepumpunit.ADAMSMDIADAMSADAMS201410·59·1KT1KT26.90107N·mm/deg[11]1.618109N/mm34.91N·mm·s/deg5Fig.5Torsionalvibrationnaturalfrequencyofthepumpshaftandpumpunit345106561061061054Table3Torsionalvibrationnaturalfrequencyofthepumpunitatdifferentgearmeshingstiffness/Hz2.46101145.16139.3636.3100215902.4610845.16139.3636.3100215902.4610645.16139.3636.3100215902.4610545.16139.3636.3100215902.4610445.16139.3636.310021590Table4Torsionalvibrationnaturalfrequencyofthepumpunitatdifferenthighspeedcouplingstiffness/Hz3.810745.16139.3636.3100215903.810643.4646.53214.1389.944.53.810514.2146.5371.40358.8939.13.81044.51222.67745.16356.3938.63.81031.4277.17445.16356.0938.5Table5Torsionalvibrationnaturalfrequencyofthepumpunitatdifferentlowspeedcouplingstiffness/Hz710745.16139.3636.31002159071065.601139.3209.3636.3100271051.77166.1837139.3636.3100271040.56020.93139.3636.3100271030.1776.618139.3636.31002.515·60·865367532-51-31Table6Torsionalvibrationnaturalfrequencyofthepumpunit/Hz145.16255.413139.34160.95357.96636.37100281590Fig.6TorsionalvibrationmodesofpumpunitFig.7LateralvibrationmodesofpumpunitAPI610105.9101071290110API610Table7Comparisonoftorsionalvibrationfrequencyandoperatingfrequencyofthepumpunit/Hz45.16139.3636.31002/Hz45.21~55.2690~110112.5~137.5225~275ADAMSAPI61012[1]ANSI/APIStandard610,CentrifugalPumpsforPetroleum,PetrochemicalandNaturalGasIndustries,TenthEdition[S],AmericanPetroleumInstitute,Washington,D.C.,2004[2]SankarS..OntheTorsionalVibrationofBranchedSystemsUsingExtendedTransferMatrixMethod[J],TransactionsoftheASME,JournalofMechanicalDesign,1979,101(5):546-553[3]MitchellL.D..ANewBranchingTechniquefortheStaticandDynamicAnalysisofGearedSystems[C],Proceedings201410·61·oftheSecondInternationalConferenceVibrationsinRotatingMachinery,TheInstitutionofMechanicalEngineers,London,England,heldatCambridge,England,September2-4,1980:37-42.[4]HibnerDH.DynamicResponseofViscous-DampedMulti-ShaftJetEngines[J].JournalofAircraft,1975,12(4):305-312.[5].[J].2011(1):11-14.[6].[J]2006,35(3):34-37.[7].[D].2013.6.[8][J].2011,31(9):649-654671.[9].1000MW[J].2013,5(31):394-400.[10].[J].2014,43(5):31-34.[11].[M].2004.TorsionalVibrationAnalysisofShaftsinLargeMulti-stageCentrifugalPumpSetYINHongquanDaqingPetrochemicalCompany,CNPC,Daqing163714,ChinaAbstract:Thetorsionalvibrationpropertyoftheshaftinlargemulti-stagecentrifugalpumpsetisdirectlyrelatedtothestabilityandreliabilityofmachineoperation.Inordertocalculatethetorsionalnaturalfrequencyoftheshaftinhigh-speedmultistagecentrifugalpumpwithgearbox,andanalyzethetorsionalvibrationproperty,thevirtualanalysismodelofshaftsystemwasestablishedbasedonmulti-bodydynamicanalysissoftwareADAMS,fromwhichthemodelingmethodswerepresented.Theeffectofthestiffnessofthegearandcouplingstothenaturalfrequencyoftheshaftwasanalyzed.ThetorsionalvibrationpropertyofthefinaldesignedshaftsystemwasevaluatedbasedonAPI610standard.Theresultsshowedthattherewereseveralnaturalfrequenciesneartheshaftsystem'sworkingfrequency.Thusitisnecessarytocarryoutthewholeshaftsystemmodelingandanalysis.Thenaturalfrequencywillbegreatlyinfluencedbymotorrotor,pumprotorandcouplings,andhoweverresonancecanbeavoidedbyappropriateadjustmentofthepumpshaftandcouplingstructure.Keywords:multi-stagecentrifugalpump;shaftsystem;tosionalvibration;naturalfrequency123456789101112131415161718192021222324252627281234567891011121314151617181920219224231524.