三线性滞回系统的稳态响应

提出了一种三线性滞回阻尼模型。用Krylov-Bogoliubov缓变系灵敏法研究了正弦型激励下单自由度三线性滞回系统的稳态响应。当本文的三线性模型退化为双线性模型时。本文结果与Caughey的结果是一致的。研究结果还发现。这种系统的稳态解总是稳定的，没有振幅的跳跃现象发生。但在激振力力幅达到一定值时能够发生无界响应。此外还发现，稳态振动达到峰值振幅时滞回面积（即最大滞回面积）对峰值振幅的比值和激振力力幅成正比。这个结论与双非线性滞回系统的相应结论是一致的。     

转子-叶片干摩擦耦合系统的稳态和非稳态振动

本文用数值方法研究转子扭振-叶片弯曲振动等效系统的稳态和非稳态响应。叶片受气流周期激励力作用，与转轴通过平台干摩擦阻尼器相连，干摩擦力采用光滑模型计算。分析扭振和弯曲振动的固有频率具有1：1和1：3两种比值情况（内共振关系）的振动表明，系统不仅存在两个主共振，由于干摩擦力的非线性特点，还存在超谐和亚谐共振状况。由于阻尼器的引入，耦合系统的主共振频率点既可能升高（1：1情况），也可能降低（1：3情况），这是耦合系统中阻尼器的调频特点，在升速的非稳态响应中，主共振和超、亚谐共振幅值将会降低．而共振点一般会出现延迟现象，但也有某些共振点有所提前（1：3情况），因此存在内共振条件的干摩擦系统，具有丰富和复杂的振动现象。     

汽轮机转子在气流力和油膜力作用下的非线性动力学特性

为了分析转子在油膜力和气流激振力共同作用下的非线性振动特性，本文以短轴承支撑的不平衡刚性对称Jeffcott转子系统为研究对象，首先分析转子在非稳态油膜力作用下的振动特性，然后分析转子在油膜力和气流激振力共同作用下的非线性振动特性。采用数值模拟的方法研究了系统的分岔和混沌特性，计算结果表明，考虑气流激振力和油膜力共同作用下的转子系统与仅考虑油膜力的转子系统相比，在相对进气速度v=30m／s时，随着无量纲转速ω的增加。二者都出现了周期运动和混沌运动多次交替出现的复杂运动特性，但是前者首次出现倍周期分岔和混沌运动时的转运提前，在定转速情况下，随着v的增大，系统最终在经历周期运动之后进入混沌运动，而且圆盘中心的最大振幅随着v的增大而增大。     

混沌振动压实动力学的仿真研究—（Ⅱ）压实性能

影响振压路机压实性的参数－压实参数,主要有：振动轮振幅Ａ、激振频率Ｗ,激振力Ｆｅ,力的传递比Ｒｒ（土壤受力Ｆｓ与激振力Ｆｅ之比）。本文通过对“混沌”与“普通”振动压路机压实参数的对比,来比较“混沌”与“普通”振动压路机的压实性能。结果表明：“混沌”振动压路机的压实优性能优于“普通”振动压路机。     

近壁面柱体涡激振动的迟滞效应

柱体涡激振动是典型的流固耦合问题,其响应规律大多是在升速流动和远离壁面条件下获得的.而自然环境流动通常不断经历升速和降速过程,近壁面柱体的涡激振动可呈现与远离壁面柱体不同的响应特征.本研究结合大型波流水槽,设计了具有微结构阻尼的柱体涡激振动装置.基于量纲分析,开展系列水槽模型实验,通过同步测量柱体涡激振动位移时程和绕流流场变化,研究了升降流速作用下柱体涡激振动触发和停振的临界速度(即上临界和下临界速度)变化规律,探究了近壁面柱体涡激振动迟滞效应.采用自下向上激光扫射的PIV流场测量系统,对比分析了固定柱体和涡激振动柱体的绕流特征.实验观测表明,近壁面柱体涡激振动触发的临界速度呈现随壁面间距比减小而逐渐减小的变化趋势;但流动降速条件下的涡激振动停振所对应的下临界速度却明显小于升速时的涡激振动触发所对应的上临界速度.采用上临界与下临界约减速度差值可定量表征涡激振动迟滞程度,研究发现该值随着柱体间距比减小呈线性增大趋势.涡激振动迟滞现象通常伴随振幅阶跃,振幅阶跃值则随着间距比减小而非线性减小.     

光纤传感器和压电作动片对薄板振动控制的分析

利用双模模态域光纤传感器的模间干涉感知薄板结构中应变的变化、获得薄板结构振动变化状况，进一步利用压电体作为动元件，减小振幅，实现振动的主动控制，采用振型叠加法和直接积分相结合的方法，从理论上论证薄板分别受到正弦波激振力，脉冲激振力和方波激振力时的振动主动控制，并由脉冲激振下的响应得到控制前后的幅频特性曲线和相频特性曲线．。     

混沌振动压实动力学的仿真研究——（Ⅱ）压实性能

影响振动压路机压实性能的参数——压实参数，主要有：振动轮振幅A、激振频率ω、激振力Fs、力的传递比Rp(土壤受力Fs与激振力Fs之比)．本文通过对“混沌”与“普通”振动压路机压实参数的对比，来比较“混沌”与“普通”振动压路机的压实性能．结果表明：“混沌”振动压路机的压实优性能优于“普通”振动压路机．     

基于电压约束的微机械谐振器幅-频耦合抑制方法

针对微机械谐振器中存在的幅度-频率耦合带来振动稳定性变差的问题，提出了一种闭环自激控制的直流参考电压约束方法来抑制谐振器振幅。首先，从理论上分析了决定谐振器临界振幅的因素，利用计算机视觉辅助测量方法和高频方波调制方法获得相关尺寸参数及品质因数计算得到微机械谐振器的临界振幅。然后，提出频谱边带比的振动幅度测试方法实现封装后的振动幅度测试。最后，构建了自激振荡闭环测控电路分析模型，根据临界振幅计算得相应的临界直流参考电压为0.866V。恒温实验测试表明：直流参考电压为0.4 V（小于临界参考电压）时，谐振器能够稳定地保持恒定幅度振动；直流参考电压为1.0 V（大于临界参考电压）时，谐振器振动幅度不恒定，谐振器稳定性变差，所提方法通过确定临界参考电压值，并将直流参考电压约束在临界参考电压以内能有效抑制幅度-频率的耦合。     

近壁面柱体涡激振动的迟滞效应

柱体涡激振动是典型的流固耦合问题,其响应规律标识码在升速流动和远离壁面条件下获得的. 而自然环境流动通常不断经历升速和降速过程,近壁面柱体的涡激振动可呈现与远离标识码体不同的响应特征. 本研究结合大型波流水槽,设计了具有微结构阻尼的柱体涡激振动装置. 基于量纲分析,开展系列水槽标识码验,通过同步测量柱体涡激振动位移时程和绕流流场变化,研究了升降流速作用下柱体涡激振动触发和停振的临界速度(即上临标识码临界速度)变化规律,探究了近壁面柱体涡激振动迟滞效应. 采用自下向上激光扫射的 PIV 流场测量系统,对比分析了固定柱体标识码振动柱体的绕流特征. 实验观测表明,近壁面柱体涡激振动触发的临界速度呈现随壁面间距比减小而逐渐减小的变化趋势;但标识码速条件下的涡激振动停振所对应的下临界速度却明显小于升速时的涡激振动触发所对应的上临界速度. 采用上临界与下临界约标识码差值可定量表征涡激振动迟滞程度,研究发现该值随着柱体间距比减小呈线性增大趋势. 涡激振动迟滞现象通常伴随振幅阶跃标识码阶跃值则随着间距比减小而非线性减小.      

复合材料薄壁圆柱壳内共振的受迫响应

采用多尺度法分析复合材料悬臂圆柱壳考虑内共振的受迫振动。建立考虑动态弹性模量、阻尼、几何非线性时系统的振动方程;利用Galerkin方法将时间扣空间变量进行分离,然后应用多尺度法推导出内共振条件下系统的频率．振幅方程;通过算例获得了系统参数变化导致复杂非线性振动响应变化的规律。理论分析发现：由于所采用的两个轴向模态相距较近,引起了能量在两个模态之间相互传递,系统存在1：1内共振现象;相比较而言,激振力大小对系统内共振下的复杂振动响应影响比较大,而阻尼的变化对其影响则很小。     

Dynamic analysis of a dielectric elastomer-based microbeam resonator with large vibration amplitude

A non-linear vibration equation with the consideration of large amplitude, gas damping and excitation is developed to investigate the dynamic performance of a dielectric elastomer (DE)-based microbeam resonator. Approximate analytical solution for the vibration equation is obtained by applying parameterized perturbation method (PPM) and introducing a detuning variable. The analysis exhibits that active tuning of the resonant frequency of the resonator can be achieved through changing an applied electrical voltage. It is observed that increasing amplitude will increase the natural frequency while it will decrease the quality factor of the resonator. In addition, it is found that the initial pre-stretching stress and the ambient pressure can significantly alter the resonant frequency of the resonator. The analysis is envisaged to provide qualitative predictions and guidelines for design and application of DE-based micro resonators with large vibration amplitude.     

Nonlinear dynamic responses of high-speed railway vehicles under combined self-excitation and forced excitation considering the influence of unsteady aerodynamic loads

The dynamic characteristics of a railway vehicle system under unsteady aerodynamic loads are examined in this study. A dynamic analysis model of the railway vehicle considering the influences of aerodynamic loads was established. The model not only considers the forced excitation effect of unsteady aerodynamic loads but also accounts for the effect of unsteady aerodynamic loads on the change of the wheel–rail contact normal forces as well as changes of the wheelset creep coefficients and creep forces/moments. Therefore, this model also considers the influences of unsteady aerodynamic loads on the self-excited vibration characteristics of the vehicle system. The time-history curves, phase trajectory diagrams, Poincaré sections, and Lyapunov exponents of the vehicle system running on a smooth straight track under unsteady aerodynamic loads were determined. The results show that when the critical speed is exceeded, the vehicle system usually performs quasi-periodic motion under unsteady aerodynamic loads, which is significantly different from the periodic motion under steady aerodynamic loads. In different cases, the amplitude and phase of motion are significantly different. The amplitude of the motions can be increased by more than 159%, and the difference of phase can be up to 173°. (The phase is almost reversed.) The dynamic responses of the vehicle system under unsteady aerodynamic loads contain abundant frequency components, including the frequency of the self-excited vibration, the frequency of the forced excitation, and combinations of their integer multiples. The vibration forms corresponding to the main harmonic components under unsteady and steady aerodynamic loads were compared, and the self-excited vibration component of the vehicle system under unsteady aerodynamic loads was identified. The variations in the critical speed with various parameter combinations were computed. The variation range of the critical velocity can reach 73%.

     

两尺度Duffing系统的动力吸振器减振研究

两尺度耦合的Duffing系统存在复杂振动, 此类振动具有振幅大、频率高的特点, 对系统的危害不容忽视. 研究了线性动力吸振器对低频参数激励下Duffing系统的振动控制问题, 通过对比耦合动力吸振器前后系统的时间历程图、相图, 发现加入动力吸振器后系统会由单一振动模式转变为混合振动模式(簇发振动), 振动幅值明显减小, 尤其对高频振动部分抑制明显. 利用快慢分析法, 当参数激励为慢变过程时得到相应的自治系统, 并发现自治系统稳定性与分岔行为对非自治系统振动响应具有明显调节作用. 研究结果表明, 虽然耦合动力吸振器前后自治系统均发生叉形分岔, 但是加入吸振器后自治系统稳定性发生变化, 稳定中心变为渐进稳定的焦点, 稳定平衡线对非自治系统轨线的吸引力增强, 使得响应振动幅值减小; 另外轨线在不同吸引子之间的跳跃次数减少, 也是导致响应振动幅值减小的另一个原因. 通过对参数激励的相关参数减振效果分析, 发现加入的动力吸振器在较大的振动幅值和频率范围内都能起到抑制系统振动的作用. 为两尺度系统耦合线性动力吸振器减振研究提供了理论依据.      

Nonlinear dynamic analysis of dielectric elastomer membrane with electrostriction

The dielectric elastomer (DE) is an important intelligent soft material widely used in soft actuators, and the dynamic response of the DE is highly nonlinear due to the material properties. In the DE, electrostriction denotes the deformation-dependent permittivity. In the present study, we formulate the nonlinear dynamic governing equations of the DE membrane considering the electrostriction effect. The free vibration and parametric excitation of the DE membrane with different geometric sizes are calculated. The free vibration bifurcations induced by the initial location and the voltage are both discussed according to an energy-based approach. The amplitude-frequency characteristics and bifurcation diagrams of parametric excitation are also given. The results show that electrostriction decreases the free vibration amplitude and increases the frequency, but it has less influence on the parametric excitation oscillation frequency and decreases the parametric excitation amplitude except when the membrane resonates. The initial location and the applied voltage can induce the snap-through instability of the free vibration. A large geometric size will lead to a much lower resonance frequency. The resonance amplitudes increase while the resonance frequencies decrease with the increase in the applied voltage. The critical voltage of snap-through instability for the parametric excitation is larger than that for the free vibration one.

     

Amplitude reduction of primary resonance of nonlinear oscillator by a dynamic vibration absorber using nonlinear coupling

The paper presents the characteristics of a new type of nonlinear dynamic vibration absorber for a main system subjected to a nonlinear restoring force under primary resonance. The absorber is connected to the main system by a link in order to be excited with twice the frequency of the motion of the main system. The natural frequency of the absorber is tuned to be twice the natural frequency of the main system, in contrast to autoparametric vibration absorber, whose natural frequency is tuned to be one-half the natural frequency of the main system. The presented absorber is not excited through the autoparametric resonance, i.e., no trivial equilibrium state exists. Therefore, the absorber always oscillates because of the motion of the main system and cannot be trapped by Coulomb friction acting on the absorber, in contrast to the autoparametric vibration absorber. Under small excitation amplitude, this absorber does not produce an overhang in the frequency response curve, which occurs because of the use of the conventional autoparametric vibration absorber; the overhang renders the response amplitude larger than that in the case without an absorber. In addition, the absorber removes the hysteresis in the frequency response curve caused by the nonlinearity of the restoring force acting on the main system. Regarding large excitation amplitude, the response amplitude in the main system can be decreased by increasing the damping of the absorber, but that decrease is limited by the nonlinearity in the restoring force acting on the main system. This paper also describes experimental validation of the absorber under small excitation amplitude using a simple apparatus.     

On the use of discontinuous nonlinear bistable dynamics to increase the responsiveness of energy harvesting devices

There is promise in the use of bistable devices to transduce ambient vibrations into electrical power. However, it is critical to sustain the relatively large amplitude snap-through motion, or interwell motion, to significantly improve the responsiveness of bistable devices as compared to linear resonance-based approaches. This work posits that relatively stiff structural elements can be placed in the vicinity of the equilibria of bistable devices such that the discontinuous change in dynamics will tend to eject an otherwise small amplitude motion into the large amplitude interwell orbit that is to be preferred for energy harvesting applications. The discontinuous nonlinear dynamic equations of motion are derived and a proxy system parametrically studied. These numerical studies demonstrate that discontinuous nonlinear bistable devices have a significantly broadened frequency range that elicits the large amplitude snap through behavior. It is also seen that interwell motion is achievable at significantly reduced excitation amplitudes through these discontinuous structural elements.     

Nonlocal and strain gradient effects on nonlinear forced vibration of axially moving nanobeams under internal resonance conditions

Based on the nonlocal strain gradient theory(NSGT), a model is proposed for an axially moving nanobeam with two kinds of scale effects. The internal resonanceaccompanied fundamental harmonic response of the external excitation frequency in the vicinities of the first and second natural frequencies is studied by adopting the multivariate Lindstedt-Poincaré(L-P) method. Based on the root discriminant of the frequencyamplitude equation under internal resonance conditions, theoretical analyses are performed to investigate the scale effects of the resonance region and the critical external excitation amplitude. Numerical results show that the region of internal resonance is related to the amplitude of the external excitation. Particularly, the internal resonance disappears after a certain critical value of the external excitation amplitude is reached.It is also shown that the scale parameters, i.e., the nonlocal parameters and the material characteristic length parameters, respectively, reduce and increase the critical amplitude,leading to a promotion or suppression of the occurrence of internal resonance. In addition,the scale parameters affect the size of the enclosed loop of the bifurcated solution curves as well by changing their intersection, divergence, or tangency.     

斜拉桥塔-索-桥面耦合参数振动模型及响应分析

针对大跨度斜拉桥拉索与桥塔、桥面的协同振动问题,考虑拉索垂度、阻尼、倾角以及重力弦向分力的影响,引入拉索高精度抛物线形,建立了桥塔-索-桥面连续非线性精细化振动模型,推导了桥塔和桥面共同激励作用下斜拉索耦合振动方程,对比分析了2种激振模式下斜拉索的参数振动特性,并编制程序研究了桥面与拉索的频率比、桥面激励幅值、索力及阻尼对结构耦合振动特性的影响规律。结果表明：桥面与拉索频率比对系统振动的影响较大,频率比为1:2和2:1时拉索均产生强烈振动,但2:1激振模式下拉索振幅更大,达到共振时间较长;随着桥面激励幅值的增大,2:1亚谐波共振模式下的拉索振幅增长速率更快;拉索振幅随索力的增大呈非线性减小趋势;斜拉索阻尼超过2%时,继续提高自身阻尼不能有效减小其振动幅值,需要通过设置附加阻尼才能更好地抑制其振动。     

Nonlinear dynamic analysis of a quarter vehicle system with external periodic excitation

In this paper, a nonlinear dynamic model of a quarter vehicle with nonlinear spring and damping is established. The dynamic characteristics of the vehicle system with external periodic excitation are theoretically investigated by the incremental harmonic balance method and Newmark method, and the accuracy of the incremental harmonic balance method is verified by comparing with the result of Newmark method. The influences of the damping coefficient, excitation amplitude and excitation frequency on the dynamic responses are analyzed. The results show that the vibration behaviors of the vehicle system can be control by adjusting appropriately system parameters with the damping coefficient, excitation amplitude and excitation frequency. The multi-valued properties, spur-harmonic response and hardening type nonlinear behavior are revealed in the presented amplitude-frequency curves. With the changing parameters, the transformation of chaotic motion, quasi-periodic motion and periodic motion is also observed. The conclusions can provide some available evidences for the design and improvement of the vehicle system.     

Nonlinear dynamics of axially moving beam with coupled longitudinal–transversal vibrations

In this study, the nonlinear vibrations of an axially moving beam are investigated by considering the coupling of the longitudinal and transversal motion. The Galerkin method is used to truncate the governing partial differential equations into a set of coupled nonlinear ordinary differential equations. By detuning the axially velocity, the exact parameters with which the system may turn to internal resonance are detected. The method of multiple scales is applied to the governing equations to study the nonlinear dynamics of the steady-state response caused by the internal–external resonance. The saturation and jump phenomena of such system have been reported by investigating the nonlinear amplitude–response curves with respect to external excitation, internal, and external detuning parameters. The longitudinal external excitation may trigger only longitudinal response when excitation amplitude is weak. However, beyond the critical excitation amplitude, the response energy will be transferred from the longitudinal motion to the transversal motion even the excitation is employed on the longitudinal direction. Such energy transfer due to saturation has the potential to be used in the vibration suppression.