液弹隔振器非线性传递特性研究

针对液弹隔振器下端空气弹簧变形特点,本研究从液弹隔振器结构模型出发,分析液弹隔振器各部分受力与位移关系,推导考虑和不考虑液弹隔振器下端非线性刚度的运动方程。获得两种条件下液弹隔振器位移传递率,分析存在非线性刚度下位移传递率特性。研究发现：考虑非线性的位移传递率表现出显著的硬化特性,最佳隔振频率随着激振位移幅值增长而增大,隔振频率设计值处的位移传递率随激振位移幅值增长而增大,即隔振效果下降;当液弹隔振器承受较大幅值振动,如激振位移幅值超过10%空气弹簧深度,应当考虑空气弹簧非线性刚度影响。     

一类液固混合介质隔振器的动力学特性研究

液固混合介质隔振器基于一种全新的工作机理,具有优良的隔振系统动力学特性.混合介质由一类几乎不可压缩液体和许多可压缩的固体单元混合而成.当振动、冲击发生时, 液体将动压力瞬间传递到所有单元体上,使它们同时参与变形,从而有效隔离振动,大幅度吸收、损耗冲击能量;若设计得当,这类隔振器可同时具有卓越的隔振和缓冲性能.以空心橡胶球作为固体单元体, 分析了该单元体在有限变形情况下的变形规律,分析了隔振器的非线性刚度特性; 采用MTS液压伺服试验系统进行了测试验证,理论分析和试验结果具有较好的一致性. 建立了系统的非线性动力学方程,采用多尺度摄动法获得了系统的频响特性, 发现系统具有软弹簧非线性动力学特性,并在试验中得到了证实; 因为弹性恢复力中存在位移平方项,通过试验和数值仿真进一步验证了系统响应的非对称性.      

基于蚁群优化最小二乘支持向量机模型的边坡稳定性分析

液固混合介质隔振器基于一种全新的工作机理,具有优良的隔振系统动力学特性. 混合介质由一类几乎不可压缩液体和许多可压缩的固体单元混合而成. 当振动、冲击发生时, 液体将动压力瞬间传递到所有单元体上, 使它们同时参与变形,从而有效隔离振动,大幅度吸收、损耗冲击能量; 若设计得当,这类隔振器可同时具有卓越的隔振和缓冲性能. 以空心橡胶球作为固体单元体, 分析了该单元体在有限变形情况下的变形规律, 分析了隔振器的非线性刚度特性; 采用MTS液压伺服试验系统进行了测试验证, 理论分析和试验结果具有较好的一致性. 建立了系统的非线性动力学方程, 采用多尺度摄动法获得了系统的频响特性, 发现系统具有软弹簧非线性动力学特性, 并在试验中得到了证实; 因为弹性恢复力中存在位移平方项, 通过试验和数值仿真进一步验证了系统响应的非对称性.     

带非线性弹簧的两自由度准零刚度隔振系统力传递率特性

基于多自由度系统中的反共振特性,分别在传统线性隔振系统的上、下两层引入非线性倾斜弹簧负刚度机构,构成两自由度准零刚度隔振器。通过静态特性分析,推导出系统满足零刚度条件时,各参数之间的关系,分析了力学参数及结构参数对系统刚度特性的影响。建立两自由度准零刚度隔振系统的非线性动力学方程,利用平均法求解,推导出力传递率表达式,结合数值分析方法,探讨系统在不同的上、下层隔振器阻尼比、竖直刚度比及质量比情况下的力传递率特性,并与单自由度准零刚度隔振系统及线性斜弹簧两自由度准零刚度隔振系统进行对比研究。结果表明：当结构参数 （即：倾斜弹簧处于静平衡位置的长度与倾斜弹簧原长的比值）较小且倾斜弹簧为软化弹簧时,可在平衡位置附近获得较小的系统刚度及较大的低刚度区间;通过选择适当的上、下层隔振器阻尼比、竖直刚度比与质量比,可减小系统的起始隔振频率,增宽隔振频带,加快系统力传递率在特定频段内的衰减速率,改善系统的低频隔振性能。     

一种准零刚度系统隔振性能的几何参数优化分析

提出了一种采用菱形连杆组件作为负刚度机构的准零刚度隔振器(下文简称菱形准零刚度隔振器)。通过静力学分析方法,建立了菱形准零刚度隔振器数学模型,并与其他调节变量较少的隔振器模型进行了对比;以被测量曲线在隔振器平衡位置处的曲率作为评价参数,研究了负刚度机构几何参数对系统刚度、阻尼非线性的影响,推导了利用几何参数进行隔振优化的条件;采用谐波平衡法求解系统动力学方程,对隔振器在不同几何参数下的隔振性能进行了分析。结果表明:菱形准零刚度隔振器具有体积相对较小且非线性调节能力较好的特点,可通过调节杆长,或满足相关临界值条件时调节杆长偏差量(下文简称杆长差)对刚度及阻尼非线性特征进行优化;刚度与阻尼的非线性优化方向不同,但通常情况下,刚度非线性因素对隔振优化起主导作用;归一化振动相对位移小于0.1时,由刚度曲线曲率得到的临界值可以较好地作为杆长差参数的隔振优化调节依据。本文提出的非线性评价方法与几何非线性优化临界值计算方法,对于类似隔振器研究和设计具有一定的指导意义。     

新型准零刚度隔振器设计及动力学研究

针对传统被动隔振器低频隔振性能不足的问题,提出了一种连杆-倾斜弹簧负刚度机构,并将其与线性弹簧并联构成一种新型准零刚度(quasi-zero stiffness, QZS)隔振器。首先,对该隔振器进行静力学分析,建立无量纲力-位移和无量纲刚度-位移关系式,并讨论设计参数对隔振器刚度的影响,进一步得出隔振器在平衡位置处具有零刚度特性的参数条件;其次,通过动力学研究,建立隔振器在位移激励下的非线性动力学方程,并应用谐波平衡法推导出位移传递率;最后,采用四阶龙格库塔法对准零刚度隔振器在不同激励频率下进行数值仿真,并与不含负刚度机构的线性隔振器进行对比分析。结果表明,准零刚度隔振器在低频激励下的隔振效果明显优于线性隔振器,而在高频激励下具备与线性隔振器相当的隔振性能。     

新型橡胶隔振器参数辨识及动力学特性研究

采用粘弹性-超弹性-弹塑性材料本构模型,对一种新型的橡胶隔振器进行了动态特性研究,并与已有实验结果进行了对比。根据所得到的恢复力-位移迟滞回线,研究了频率、动态位移幅值对橡胶隔振器的动刚度的影响。在此基础上,给出了这种新型橡胶隔振器的非线性恢复力模型并进行了参数辨识。根据所得恢复力模型对隔振器系统进行了动力性能研究,发现此橡胶隔振器在低频时隔振作用很小,但在高频时隔振效果明显且随频率增加力传递率逐渐减小,隔振效果最大可达到96%。该隔振器的建模和参数辨识方法为这类隔振器的优化设计和工程应用提供了理论依据和分析方法。     

一类分段光滑隔振系统的非线性动力学设计方法

分段光滑隔振系统是一类具备分段刚度或阻尼的非线性动力学系统,在振动控制领域中具有广泛代表性,诸如限位隔振系统、分级汽车悬挂等. 分段光滑的刚度或阻尼特性能够实现隔振系统的特定动力学性能及提升隔振性能,如抑制共振响应、提升共振区隔振性能等,但是亦会给隔振系统的动力学行为带来诸多不利影响. 以分段双线性分段光滑隔振系统为理论模型,系统研究了摒除不利于隔振的非线性动力学现象设计方法,包括幅值跳跃、周期运动的倍周期分岔等. 首先,利用平均法与奇异性理论给出了主共振频响曲线拓扑特征的完整拼图. 研究结果表明,参数空间分为4 个区域,其中2 个区域存在幅值跳跃,而其产生跳跃原因分别由鞍结分岔与擦边分岔所导致;基于此提出避免主共振跳跃的设计方法. 其次,建立了隔振有效区内周期运动的庞加莱映射,通过特征值分析给出了避免倍周期分岔发生的条件,证实增大阻尼可以抑制倍周期分岔的发生. 最后通过数值仿真分析了噪声对多稳态运动的影响. 研究结果发现在噪声影响下,分段光滑隔振系统的响应会在不同稳态间跃迁,非常不利于隔振. 因此,在完成跳跃与倍周期分岔的防治设计后,应采用数值仿真校验系统是否存在多稳态运动.      

橡胶隔振系统非线性振动参数识别与特性研究

建立单自由度非线性系统基础激励正弦扫描试验的数学模型,并针对多项式非线性阻尼与多项式非线性弹簧并联的橡胶隔振系统求解了数学模型.进而在此框架下通过正弦扫描振动试验,采用共振峰值法识别了橡胶隔振器的非线性阻尼与刚度系数,研究了不同振动量级下小型橡胶隔振器的振动特性.     

含机械调频式动力吸振器的准零刚度隔振系统隔振性能分析

基于动力吸振器原理,在单自由度准零刚度隔振器基础上耦合可调频动力吸振器构成两自由度隔振系统。首先,对动力吸振器工作原理进行理论分析并提出其力学模型;其次,通过静力学分析,推导出系统满足零刚度条件时,各参数间的关系并分析其对系统刚度特性的影响;然后,建立两自由度隔振系统非线性动力学方程,利用谐波平衡法进行幅频响应解析分析,得到力传递率表达式;最后,数值分析动力吸振器阻尼、刚度、质量、激励力幅值和弹簧片有效长度对力传递率的影响规律,并与单自由度准零刚度隔振系统及两自由度线性隔振系统对比分析。结果表明：通过选择适当的动力吸振器参数不仅可以减小系统的起始隔振频率,增宽隔振频带,且还能加快系统力传递率在特定频段内的衰减速率,改善系统的低频隔振性能,实现激励频率的可适应性。     

磁致伸缩主被动隔振装置中的磁机耦合效应研究

磁致伸缩材料和柔顺位移放大机构组成的主动驱动装置具有精度高、驱动力大等特点.将其与被动隔振装置并联,形成主被动隔振装置,可以弥补纯被动隔振在低频和微幅扰动工况下的不足.本文针对这类磁致伸缩主被动隔振装置进行磁机耦合效应研究.基于Jiles-Atherton模型,分析了磁致伸缩材料所受应力对有效磁场、磁化强度、磁致伸缩系数和材料杨氏模量的影响,表征了材料磁机耦合效应.在此基础上,建立了主被动隔振装置的动力学模型,分析了主动驱动装置与被动隔振装置间的耦合作用.在耦合作用影响下,若被动隔振装置刚度不同,即使输入磁场相同,驱动器产生的驱动位移和驱动力也不相同.磁致伸缩材料的变刚度效应使隔振装置整体等效刚度不再为定值,从而影响被动隔振效果.本文提出了通过柔顺机构参数设计减小前述两种耦合影响的方法.数值仿真结果表明,磁致伸缩主被动隔振装置在低于、接近和高于谐振频率三类扰动下,都能达到比被动隔振更好的振动抑制效果.此外,仿真结果验证了考虑磁机耦合效应的数值模型具有更高精度.      

基于混杂双稳定层合板的准零刚度隔振装置

准零刚度隔振装置(quasi-zero stiffness,QZS)在其平衡位置处的刚度接近于零,能够有效地隔离加速度幅值较低的微振动.因此,准零刚度隔振装置在卫星等航天器结构的微振动抑制领域有较好的应用前景.准零刚度隔振装置通常由正刚度部件及负刚度部件并联而成.在众多准零刚度隔振装置概念中,负刚度部件通常需要多个弹性部件及特定约束边界形成负刚度特性,导致准零刚度隔振装置的整体质量及体积相对较大.然而,航天器结构对隔振装置的质量特性及安装空间提出较高要求,因此需开发新型准零刚度隔振装置,降低隔振装置的质量及体积以满足航天器结构的使用要求.本文提出了一种基于混杂双稳定复合材料层合板的准零刚度隔振装置.通过利用混杂双稳定复合材料层合板自身的负刚度特性,降低了准零刚度隔振装置的结构复杂程度.本文对提出的准零刚度隔振装置的力学原理进行说明,对其隔振效果进行了仿真分析,并进行了隔振效果验证试验.隔振试验表明,准零刚度隔振装置的振动传递率曲线不再具有峰值,其实际振动传递率低于具有相同正刚度的线性隔振系统.基于试验及仿真分析结果,本文对隔振装置隔振性能的影响因素进行了分析讨论.分析结果显示,隔震装置中线性弹簧刚度与双稳定层合板负刚度之间的差异以及微小装配误差将导致隔振装置的隔振效果出现降低.      

Cascaded quasi-zero stiffness nonlinear low-frequency vibration isolator inspired by human spine

Human motion induced vibration has very low frequency, ranging from 2 Hz to 5 Hz. Traditional vibration isolators are not effective in low-frequency regions due to the trade-off between the low natural frequency and the high load capacity. In this paper, inspired by the human spine, we propose a novel bionic human spine inspired quasi-zero stiffness (QZS) vibration isolator which consists of a cascaded multi-stage negative stiffness structure. The force and stiffness characteristics are investigated first, the dynamic model is established by Newton’s second law, and the isolation performance is analyzed by the harmonic balance method (HBM). Numerical results show that the bionic isolator can obtain better low-frequency isolation performance by increasing the number of negative structure stages, and reducing the damping values and external force values can obtain better low-frequency isolation performance. In comparison with the linear structure and existing traditional QZS isolator, the bionic spine isolator has better vibration isolation performance in low-frequency regions. It paves the way for the design of bionic ultra-low-frequency isolators and shows potential in many engineering applications.

     

Dynamic stiffness of chemically and physically ageing rubber vibration isolators in the audible frequency range: Part 2—waveguide solution

The dynamic stiffness of a chemically and physically ageing rubber vibration isolator in the audible frequency range is modelled as a function of ageing temperature, ageing time, actual temperature, time, frequency and isolator dimension. In particular, the dynamic stiffness for an axially symmetric, homogeneously aged rubber vibration isolator is derived by waveguides where the eigenmodes given by the dispersion relation for an infinite cylinder satisfying traction free radial surface boundary condition are matched to satisfy the displacement boundary conditions at the lateral surface ends of the finite rubber cylinder. The constitutive equations are derived in a companion paper (Part 1). The dynamic stiffness is calculated over the whole audible frequency range 20–20,000 Hz at several physical ageing times for a temperature history starting at thermodynamic equilibrium at \(+25\,^{\circ }\hbox {C}\) and exposed by a sudden temperature step down to \(-60\,^{\circ }\hbox {C}\) and at several chemical ageing times at temperature \(+25\,^{\circ }\hbox {C}\) with simultaneous molecular network scission and reformation. The dynamic stiffness results are displaying a strong frequency dependence at a short physical ageing time, showing stiffness magnitude peaks and troughs, and a strong physical ageing time dependence, showing a large stiffness magnitude increase with the increased physical ageing time, while the peaks and troughs are smoothed out. Likewise, stiffness magnitude peaks and troughs are frequency-shifted with increased chemical ageing time. The developed model is possible to apply for dynamic stiffness prediction of rubber vibration isolator over a broad audible frequency range under realistic environmental condition of chemical ageing, mainly attributed to oxygen exposure from outside and of physical ageing, primarily perceived at low-temperature steps.     

A quasi-zero-stiffness isolator with a shear-thinning viscous damper

Quasi-zero-stiffness(QZS) vibration isolators have been widely studied,because they show excellent high static and low dynamic stiffnesses and can effectively solve low-frequency and ultralow-frequency vibration. However, traditional QZS(T-QZS)vibration isolators usually adopt linear damping, owing to which achieving good isolation performance at both low and high frequencies is difficult. T-QZS isolators exhibit hardening stiffness characteristics, and their vibration isolation performance is e...     

Static lateral stiffness of wire rope isolators

This paper presents an analytical model for the static lateral stiffness of Wire Rope Isolators (WRI). The wire rope isolator, which is a passive isolation device, has been widely adopted as a shock and vibration isolation for many types of equipment and lightweight structures. The major advantage of the WRI is its ability to provide isolation in all three planes and in any orientation. The WRI in the lateral roll mode, is required to possess the required lateral stiffness to support and isolate the equipment effectively. The static lateral stiffness of WRI depends mainly on the geometrical characteristics and wire rope properties. The model developed in this paper is validated experimentally using a series of monotonic loading tests. The flexural rigidity of the wire ropes, which is required in the model, was determined from the transverse bending test on several wire rope cables. It was observed that the lateral stiffness is significantly influenced by the wire rope diameter and height of the isolator. The proposed analytical model can be used for the evaluation of lateral stiffness and in the preliminary design of the WRI.     

Force and displacement transmissibility of a quasi-zero stiffness vibration isolator with geometric nonlinear damping

A geometric nonlinear damping is proposed and applied to a quasi-zero stiffness (QZS) vibration isolator with the purpose of improving the performance of low-frequency vibration isolation. The force, stiffness and damping characteristics of the system are presented first. The steady-state solutions of the QZS system are obtained based on the averaging method for both force and base excitations and further verified by numerical simulation. The force and displacement transmissibility of the QZS vibration isolator are then analysed. The results indicate that increasing the nonlinear damping can effectively suppress the force transmissibility in resonant region with the isolation performance in higher frequencies unaffected. In addition, the application of the nonlinear damping in the QZS vibration isolator can essentially eliminate the unbounded response for the base excitation. Finally, the equivalent damping ratio is defined and discussed from the viewpoint of vibration control.