悬架系统偏频仿真方法误差分析

悬架系统偏频仿真方法误差分张宝，苏申1121悬架系统偏频仿真方法误差分张宝，苏申1121关键词：偏频；仿真；试验ErrorAnalysisofSimulationMethodsForCalculationFrequencySuspensionZhangBao1,SUSheng2,GuoFuxiang1,Zhang(1.NAVECOLtd.;2.AutomotiveEngineeringResearchInstitute.NAC;Nanjing,210009)Abstract:Objective:Basedonthevehicle,thedifferentmodelingandsimulationmethodsareusedforcalculatingthenaturalfrequencyofthesuspensionsystem,theerrorsareanalyzedandamorepracticalsimulationmethodissummedup.Method:Theerrorsofthesimulationsusingdifferentsimplifiedmodelsareanalyzedbycombiningthemulti-bodydynamicsimulationmethodsandvehiclevibrationtests.Results:Comparedwiththevehiclevibrationtests,theerrorofthemethod1is6.6%,theerrorofthemethod2is5.4%,theerrorofthemethod3is2.8%;Conclusion:Thesimulationresultofmethod3matchesmorewiththeexperiment.Themodelingandsimulationmethod3isestablishedagreesmorewiththepracticalengineeringapplications.Keywords:Thenaturalfrequency;Simulation;Testing;Error2.11引型，对簧上偏频进行理论计算11Tab.1Therearsuspension212.33悬架在重力作用下自由落下[4][5]，记录得到4所示。2.33悬架在重力作用下自由落下[4][5]，记录得到4所示。Fig.1Thetwo-freedommodelofwhole悬架和轮胎（双胎）串联的等效弹簧刚度RR可由式（1）求得[3]KsKtKsRRFig.3Themulti-bodymodelofrearMfn式中M—簧上质量，kg；1中的数据带入到公式（2）中可以计算出簧上偏频为1.55Hz。2.22按照表1中的数据进行设置。Fig.4Thevibrationcurveofthecenterof2.4Fig.2Thetwo-freedommodelofrear采用Switchtolinearmodescontrols5Fig.5Themulti-bodymodelofwhole模型中的车架采用柔性体处理，利用Nastran计算生成车架模态中性文件MNF)，文件中包含了柔性体的几何信息、2MNFADAMS息[6]ADAMS软件中柔性体车架的频MNFADAMS息[6]ADAMS软件中柔性体车架的频型进行对比，验证MNF8Fig.8Theinstalllocationsofthe6Fig.6Theframe上方车架模型上建立一个Z向加速度测量信Fig.9Thevibrationtestingcurvesofthemeasurementpointonframe3.1采用简化理论公式方法计算出的悬架166253果与样车试验结果比较接近，误差为Fig.7Thevibrationsimulationcurvesofthemeasurementpointonframe由图7可知加速度衰减曲线的振动周期为0.62s，悬架偏频为1.613Hz。2.5LMStestlab测试测试工况如图8所示。10Fig.10Thecomparisonof33.2法3的仿真精度较高[7][8]。4结K&M系统，悬架系统和整3综合考虑了整车转动的偏频误差分析和准主频计算[J].汽车技王宇，秦峰，高连兴.汽车悬架主要性能参数的匹配研究[J].拖拉机与农