使用应变模态和遗传算法的有限元模型修正方法

提出了采用应变模态置信度为待修正响应特征的有限元模型修正方法。应变模态置信度是评价有限元仿真与试验测试结果相关性的方法,可以为模型修正提供全局的频率误差信息和局部的应变相关性信息。首先,介绍了应变模态和有限元模型修正的相关理论方法;然后,以某航空加筋壁板结构为对象,通过仿真分析和"仿真试验"获得结构的应变模态频率以及对应的应变振型,进一步计算频率误差和应变模态置信度误差;最后,基于两种误差构造模型修正的目标函数,采用遗传算法对目标函数进行优化,修正结构中的待修正参数,并将修正后参数代入模型,验证所提方法的正确性和有效性。结果表明:所采用的方法获得的修正后有限元模型具有复现修正响应特征的能力,并且对于未修正频段内的响应也具有较好的预测能力。     

基于灵敏度分析的刀形天线有限元模型修正

准确可靠的有限元模型是结构动态特性分析、设计改进的基础,文中利用模态试验得到的模态参数对某刀形天线进行有限元模型修正.首先建立天线结构的参数化模型,然后通过灵敏度分析选择合适的设计参数作为后续优化对象,利用计算与试验的模态频率之间的相对误差构造加权的优化目标函数,最后应用1阶优化方法修正结构的有限元模型.修正后有限元模型的模态频率最大相对误差降低至10%以内,模态置信度(MAC)均大于0.8.该修正模型可用于后续的动力学分析.     

循环对称结构随机子空间法模态分析及验证

为探究仅基于响应测量的随机子空间法能否准确识别循环对称结构的重根模态,以制动盘为例,分别对其进行基于随机子空间法的模态分析及传统的试验模态分析,并提取了相应的模态参数,结果显示二者前9阶固有频率最大误差仅为0.66%,且振型吻合。表明仅基于响应测量的随机子空间法同样适用于循环对称类结构的模态分析。     

空间遥感器支撑桁架的模态计算与试验

为保证空间遥感器成功发射,采用有限元法计算了主要承受动力学载荷支撑桁架的模态特性,用锤击法对支撑桁架实物进行了模态测试。对计算结果与试验结果的模态频率进行了对比,用视觉比较、模态置信准则等方法进行了模态振型相关性分析。结果表明,桁架结构的一阶频率为154 Hz,满足了一阶频率＞140 Hz的设计要求;桁架结构的有限元模型平均频率计算误差＜10%,局部存在与试验结果相关性＜0.5的振型,需要进一步的修正,才能满足后续工程的应用要求。     

气体静压主轴模态仿真分析及试验研究

为准确获取气体静压主轴的动力学模态特性,分别建立主轴转子及主轴部件的有限元模型,对有限元模型中添加的弹簧及电机约束边界条件进行了研究,并分别对以上两个有限元模型进行模态计算。比较两种情况下的结构固有频率、振型趋势及各阶模态下的有效参与质量,分析主轴部件中的外壳对主轴转子模态参数的影响,其中仅保留主轴转子的前六阶固有频率为1.5 Hz、277 Hz、279 Hz、316 Hz、384 Hz、385 Hz,而主轴部件的前六阶固有频率为1.5 Hz、259 Hz、270 Hz、281 Hz、352 Hz、363 Hz,以上结果中均包含刚体模态及重根模态。两者比较结果表明主轴部件的固有频率因其质量的增加而有所降低,且主轴部件不再满足对称结构形式,因而相对于仅保留主轴转子重根模态的情况有所减弱。基于有限元仿真分析结果,进一步对主轴部件进行模态试验验证,通过仿真与试验对比,结果表明主轴转子的有限元仿真结果与试验测量结果更加贴近,其前三阶误差分别为0.6%、10.6%和2.6%。上述仿真边界条件的加载与计算过程及试验测试方法对进一步提高气体静压主轴模态参数仿真精度及修正动力学仿真模型提供了有益参考。     

某夹具结构模态仿真与试验及相关性验证

针对某雷达夹具,首先系统地介绍了LMS试验模态测试方法,得到了该结构的固有频率与振型,进一步使用有限元方法计算了结构的自由模态.在此基础上,研究了仿真模态结果与试验模态结果的差异,给出了相关性分析的预处理方法,进而得到了试验模态与仿真模态的相关性结果,验证了仿真模型的有效性,为进一步的频谱分析,减少样机试验奠定基础.     

基于DASP的汽轮发电机定子EMA试验模态分析

汽轮机发电机定子端部的主要结构包括绕组、内部支撑环及大锥壳等结构,其主要作用是约束、支撑绕组。汽轮机定子绕组端部模态对汽轮机定子的安全运行有较大影响。文中通过EMA试验模态分析,得到了前8阶(即前4阶对称重根)模态参数(振型、频率及阻尼比),为建立该型汽轮机定子绕组端部的动力学模型、新机设计和监测评价及修正完善理论模态计算结果等提供了参照依据。     

基于模态相关分析的发动机曲轴箱模型修正

以发动机曲轴箱为例,给出一种复杂结构有限元模型合理性验证的方法。采用锤击法测得曲轴箱的试验模态频率和固有振型,应用Ansys建立有限元模型并进行了计算模态分析,对试验模态和有限元模态进行模态相关分析,检验有限元模型的合理性。修正后的有限元模型,与实验的前5阶频率和振型基本吻合。     

轴流通风机叶片模态仿真及其对气动噪声的影响

利用有限元模型对叶轮模态进行了计算，判断分析了各阶模态振型对气动噪声的影响程度，求解中利用了ANSYS的模态循环对称功能，同时分析了旋转软化、应力强化对叶轮真实运转状况下模态频率的影响。     

行波管模态分析与有限元模型修正

行波管的工作环境恶劣,其结构的振动特性对寿命及可靠性有着重要影响。应用有限元分析软件对行波管进行模态分析,并通过模态试验实测了行波管的模态参数,得到行波管前四阶固有频率和振型。对比分析仿真和试验结果,仿真计算的模态频率偏高。应用Kriging模型构建固有频率与材料参数的关系,将试验结果作为目标进行材料参数修正。修正后的仿真模型的计算精度有了大幅度提高,行波管结构的固有振动特性得到更加真实地反映,为进一步研究其动力学特性提供了更加准确的模型基础。     

基于模态扩展技术的天线阵面形变重构

文中通过扩展实验模态,利用模态法思想进行形变重构,使用局部对应（Local Correspondence, LC）原理进行重构数值仿真和实验验证。该方法首先通过实验模态测试获得有限个测点的位移模态振型数据,根据实物建立较为准确的有限元模型并提取其模态数据。然后利用LC 原理选择最优的有限元位移模态振型簇对所测实验模态逐阶进行扩展。最后利用扩展后的实验模态进行重构。该方法与系统等效缩减展开过程（System Equivalent Reduction Expansion Process, SEREP）法、模态法的重构结果对比表明,该方法能够显著降低实验模态测试误差对重构精度的影响,并在有限元模型较为准确的情况下提升重构精度。     

Frequency response based sensor placement for the mid-frequency range

Accurately characterizing mid-frequency vibrations is essential for structures that require ultra-quiet vibration environments. Selecting the proper sensor locations is an important step in the model verification and validation process. State-of-the-practice approaches to sensor placement are typically based on modes shapes of the pretest finite element model. However, these modal based techniques break down in the mid-frequency range due to the high modal density. The purpose of this work was to develop a sensor placement technique based directly on a structure's frequency response. The finite element model frequency response can be decomposed into principal directions and their corresponding singular values, which relate the principal directions to the system's energy. A system's response is usually dominated by a relatively small number of principal directions, even for frequency bands with high modal densities. Principal directions are always orthogonal, while mode shapes in general are not, which makes them more robust to modeling errors and experimental noise. The new method places sensors such that the independence and signal strength of the dominant principal directions are maintained.     

SENSITIVITY-BASED OPERATIONAL MODE SHAPE NORMALISATION

In the past few years, in-operation modal analysis has become a valid alternative for structures where classic forced vibration tests would be difficult, if not impossible, to conduct. A disadvantage of this method is that the excitation forces are unknown. Therefore, not all modal parameters can still be estimated. As a result, operational mode shape estimates remain unscaled (dependent on the unknown level of excitation) what restricts the applicability of operational modal models. So far, no techniques are available for the correct re-scaling of operational mode shapes purely based on experimental output-only data. All known methods involve either a detailed knowledge of the material characteristics of the test structure (finite element model approach) or make very restrictive assumptions about the excitation signal. In this contribution, a sensitivity-based method is proposed for the scaling of operational mode shapes on a basis of operational modal models only.     

Operational modal analysis by updating autoregressive model

This paper presents improvements of a multivariable autoregressive (AR) model for applications in operational modal analysis considering simultaneously the temporal response data of multi-channel measurements. The parameters are estimated by using the least squares method via the implementation of the QR factorization. A new noise rate-based factor called the Noise rate Order Factor (NOF) is introduced for use in the effective selection of model order and noise rate estimation. For the selection of structural modes, an orderwise criterion called the Order Modal Assurance Criterion (OMAC) is used, based on the correlation of mode shapes computed from two successive orders. Specifically, the algorithm is updated with respect to model order from a small value to produce a cost-effective computation. Furthermore, the confidence intervals of each natural frequency, damping ratio and mode shapes are also computed and evaluated with respect to model order and noise rate. This method is thus very effective for identifying the modal parameters in case of ambient vibrations dealing with modern output-only modal analysis. Simulations and discussions on a steel plate structure are presented, and the experimental results show good agreement with the finite element analysis.     

振动流化床干燥机的振型分析

为了研究LHZC6/60型振动流化床干燥机主要模态的特性,对干燥机进行简化,建立有限元模型。利用有限元分析软件ANSYS对干燥机进行了模态分析,求出干燥机的前8阶固有频率和振型图。通过分析干燥机的振型图得到振动流化床干燥机的动态特性和其结构的薄弱环节,这为该机结构的改进设计和动态分析提供了理论依据。     

Structural crack detection without updated baseline model by single and multiobjective optimization

Identification, localization and quantification of structural damage can be performed through a model-updating procedure. Model-updating methods require a baseline finite element (FE) model of the undamaged structure, which imposes a restriction on their applicability and can become very problematic especially for large and complex civil structures. Modeling errors in the baseline model whose effects exceed the modal sensitivity to damage are critical and make an accurate estimation of damage impossible. This paper presents an identification algorithm using modal data for assessing structural damage that is based on FE-updating procedures and takes modeling error into account. To overcome its influence, differences of mode shapes and frequencies before and after damage for both numerical model and experimental measurements are used instead of the mode shapes and frequencies themselves. To formulate the objective function, two different approaches have been considered taking into account how these differences are grouped: a single-objective approach and a multiobjective approach. The effectiveness of both approaches is verified against numerical and experimental results.