轮胎不平衡振动分析规范

Q/SZJ191001-2017轮胎不平衡振动分析规范SpecificationOfImbalanceVibrateAnalysisTire20XX20XX-12-31实施20XX-11-27发布XXXX汽车工程技术有限公司发布Q/SZXX-X-2017轮胎不平衡振动分析规范范围本标准规定了轮胎不平衡振动分析方法及结果处理方法。本标准适用于CAE部门轮胎不平衡振动分析。规范性引用文件无。术语和定义无。摘要ABSTRACT本规范描述了如何评估整车轮胎静/动不平衡，因轮胎质量分布不均导致的轮胎不平衡是汽车行驶时的一个主要振动源。它是由轮胎的转动速度相关的具有周期性特点的转动向心力引起的。这个力相对与轮心会产生周期性的力矩，轮子的力和力矩会传到相邻的结构上，如果轮子的力相互抵消的话只会传递力矩至相邻的结构中。这会产生两种不平衡的类型:力和力矩均传递的为轮胎静不平衡，只传递力矩的为轮胎动不平衡。Thisproceduredescribeshowtoassessthevehiclesensitivityforstaticanddynamictireimbalance.Oneofthesourcesofvibrationinamovingvehicleisduetotire-wheelimbalance,whichiscausedbythenon-uniformmassdistributioninthetire-wheelsystem.Asatirespinsacentrifugalforce,harmonicintimeandproportionaltothesquareoftherotationalvelocity,isgenerated.Thisforceproceduresharmonicmomentsaboutthewheelspindle.Bothforcesandmomentsfromeachtire-wheelsystemaretransferredtoadjoiningstructureunlesstheforcescanceloutinwhicheventonlythemomentsaretransferred.Thisleadstotwotypesofimbalancesinvehiclesystems;staticimbalance,whereforcesandmomentsaretransferred,anddynamicimbalancewhereonlymomentsaretransferred.流程图ProcessFlowDiagram计算出力和力矩等数据计算出力和力矩等数据Calculatetheforceandmoment用Sol111进行计算RunthemodelwithSOL111收集有限元模型信息Collectdetailfiniteelementmodel绘制曲线Plotcurve单位转化Scaletheresponseby1000*(2PI)^2/gtoexpressitintermsofmg/ozunit图1流程图Fig1ProcessFlowDiagram工具描述ToolDescription仿真分析过程中需要用到的如下软件:Thefollowingsoftwarefacilitatestheanalyticalsimulationprocess:前处理(Preprocessors):Hypermesh求解器(AnalysisCode):MSC.Nastran后处理(Postprocessors):Hyperview建模和分析过程Modeling/AnalysisProcedure单位Units分析中所用单位制如下所示:Theunitsusedintheanalysisareasfollows:力(Force) 牛顿(N)质量(Mass) 吨(Ton)长度(Length) 毫米(mm)时间(Time) 秒(Second)内容Contents图2整车组成示意图坐标系CoordinateSystems整车全局坐标系。Vehicleglobalcoordinatesystem.建模技巧ModelingTechniques参照整车NVH建模规范AccordingtothespecificationofvehiclemodelforNVH假设和限制Assumptions/Limitations假设系统响应是线性的，轮胎旋转产生正弦，温度的影响忽略。刚度与阻尼成正比。Itisassumedthatthesystemrespondsinalinearelasticmanner.Non-uniformityisassumedtobesinusoidal,andphasedwithrespecttoroadwheel/tirerotation.Temperatureeffectsonbushingratesanddampingareoftenignored.Forlinearmodels,stiffnessratesanddampingasafunction.载荷和边界条件Loads/BoundaryConditions频响分析，求解序列号Sol111。FRFSolutionSol111分析工况分析工况示意图如图2所示。figure1,isthesketchforloadcase静不平衡动不平衡图2分析工况示意图分析包含以下4个工况：Theanalysiscontains4casesasfollowing:左前轮静不平衡（Fx，Fz，Mx，Mz）Thestaticimbalanceforleftfronttire;左后轮静不平衡（Fx，Fz，Mx，Mz）Thestaticimbalanceforleftreartire;左前轮动不平衡（Mx，Mz）Thedynamicimbalanceforleftfronttire;左后轮动不平衡（Mx，Mz）Thedynamicimbalanceforleftreartire;加载位置加载点为轮心，如图3所示。Theloadcontains3types图3加载点位置载荷大小/load载荷大小分析包含以下2种情况：1）对于力不平衡工况，每个车轮的不平衡力为：式中：——车轮不平衡量，单位；——车轮转动频率；——车轮宽度，单位mm；若左右同相位则左右轮不平衡力相位差为0，若反相位则相位差为180°，取车轮产品开发技术要求中规定的不平衡量最大允许值，例如某车型17寸车轮的不平衡量最大允许值为650不平衡力在X向与Z向的分量为：式中：——车轮转角，Z方向的不平衡力滞后X方向90°。2）对于力矩不平衡工况，每个车轮的不平衡力矩为：若左右同相位则相位差为180°，若左右反相位则相位差为0。不平衡力矩在绕X向与绕Z向的分量为：式中：——车轮转角，绕Z方向的不平衡力矩滞后绕X方向90°。静不平衡的工况的不平衡力和力矩分别如下：其中L——加载点与不平衡质量在轮轴上投影点的距离。ω——圆频率动不平衡的力矩计算公式如下：加载频率Frequency车轮转动频率与车速（km/h）的对应关系如下：式中：——轮胎滚动半径，单位mm。由上式可得出最高车速对应的车轮转动频率。加载频率设置如下：激励频率范围：1至；模态求解范围：1至。结果Results《整车动不平衡测试规范》《Thespecificationofmodaltestforfullvehicle》性能要求PerformanceRequirements座椅导轨处各个方向的加速度输出小于30mG/oz（在0~最大车速范围内）方向盘处各个方向的加速度输出小于60mG/oz（在0~最大车速范围内）TheaccelerationofXYZdirectionforseattrackerisbelow30mG/oz（rangeofmaxvelocity）TheaccelerationofXYZdirectionforsteeringisbelow60mG/oz（rangeofmaxvelocity）分析要求ANALYSISREQUIREMENTS无。参考文件DOCUMENTATION无。联系人CONTACTS无。例子EXAMPLESDOMAINSOLVERACMS(PARTOPT=DOF,PRINT=YES)CEND$CASECONTROLSECTIONECHO=NONETITLE=A10TIREWHEELIMBALANCEANALYSISMETHOD=1MPC=1000FREQ=10SDAMPING(STRUCTURE)=2VELOCITY(SORT2,PUNCH,PHASE)=1ACCELERATION(SORT2,PUNCH,PHASE)=1SET1=27750006,27750012,27750003,27750009,50004102$$$SUBCASE101LABEL=STATICIMBALANCE,FRONTTIRE,LEFTHANDSIDEDLOAD=1101SUBCASE102LABEL=STATICIMBALANCE,REARTIRE,LEFTHANDSIDEDLOAD=1102SUBCASE103LABEL=DYNAMICIMBALANCE,FRONTTIRE,LEFTHANDSIDEDLOAD=1103SUBCASE104LABEL=DYNAMICIMBALANCE,REARTIRE,LEFTHANDSIDEDLOAD=1104$$BEGINBULKPARAMPOST-1PARAMAUTOSPCYESPARAMCOUPMASS1PARAMGRDPNT0PARAM,CHECKEL,noMPCADD100016000000160050001650000017000000170050002200500022105000240050002410500027000000270050002725000016505000$==============================================================================$$***EIGENVALUEEXTRACTION$EIGRLSIDLO_FREQUP_FREQNROOTSMSGLVLMAXSETEIGRL10.040.1$=======================================$IMBALANCEFORCEANDMOMENTCALCULATION$=======================================$***TABLED4=W^2=(2*PI*FREQ)^2=39.478*FREQ^2TABLED41000.01.00.0100.0+0.00.039.478ENDT$123456789$***STATICIMBALANCE,FRONTTIRE,LEFTHANDSIDEDLOAD11011.01.01011.01021.0103++1.0104$$***FRONTTIRE,LEFTHANDSIDE$***FxRLOAD2101101101100DAREA1012200000016.12e-3DPHASE10122000000190.$***FzRLOAD2102102102100DAREA1022200000036.12e-3DPHASE1022200000030.$***MxRLOAD2103103103100DAREA1032200000044.280e-1DPHASE1032200000040.$***MzRLOAD2104104104100DAREA1042200000064.280e-1DPHASE10422000000690.$***STATICIMBALANCE,REARTIRE,LEFTHANDSIDEDLOAD11021.01.01051.01061.0107++1.0108$***REARTIRE,LEFTHANDSIDE$***FxRLOAD2105105105100DAREA1052400000016.12e-3DPHASE10524000000190.$***FzRLOAD2106106106100DAREA1062400000036.12e-3DPHASE1062400000030.$***MxRLOAD2107107107100DAREA1072400000044.280e-1DPHASE1072400000040.$***MzRLOAD2108108108100DAREA1082400000064.280e-1DPHASE10824000000690.$$$***DYNAMICIMBALANCE,FRONTTIRE,LEFTHANDSIDEDLOAD11031.01.01091.0110$$***MxRLOAD2109109109100DAREA1092200000041.38000DPHASE1092200000040.$***MzRLOAD2110110110100DAREA1102200000061.38000DPHASE11022000000690.$***DYNAMICIMBALANCE,REARTIRE,LEFTHANDSIDEDLOAD11041.01.01111.0112$***MxRLOAD2111111111100DAREA1112400000041.38000DPHASE1112400000040.$***MzRLOAD2