利用遗传算法由电阻抗计算四阶带通箱的低频响应

提出了一种基于电阻抗得到四阶带通扬声器系统低频频率响应的方法。该方法无需消声室,首先建立扬声器系统的电阻抗集中参数电路模型并测量得到电阻抗曲线,然后运用遗传算法优化模型中的元件参数值,使得由模型计算得到的阻抗曲线与测得的阻抗曲线相吻合,再根据模型计算得到低频响应曲线。测量结果表明理论曲线与实测曲线相吻合,说明基于电阻抗得到低频响应的方法是可行的和有效的。     

电动扬声器悬置系统蠕变效应建模

对电动扬声器悬置系统的蠕变效应进行了分数阶建模。通过将标准线性固体模型中的牛顿黏壶替换为分数阶Abel黏壶,提出了悬置系统分数阶标准线性固体力顺模型。使用Klippel扬声器单元电阻抗激光测量系统,测量了2只具有不同橡胶折环的中频扬声器单元的电阻抗和传递函数(振膜输出位移/输入声压),并采用最小二乘法拟合实测曲线,得到了模型参数。通过与已有的考虑蠕变效应的4参数对数模型和标准线性固体模型拟合结果的对比,结果表明:分数阶标准线性固体模型能够准确描述力顺损耗因数随频率的变化规律,对蠕变效应具有更好的模拟精度。      

用激光自混合干涉测量扬声器的Q值

用激光自混合干涉方法测量扬声器振动,从扬声器振动引起的自混合干涉信号测量扬声器振动速率.由正弦波激振扬声器测量振速的幅频特性曲线,谐波中包含扬声器谐振频率的方波激振扬声器测量振速衰减曲线,分别按谐振法和衰减法测量得到扬声器的品质因数约13.3和10.2.由于方波激励时扬声器有谐波振动成分,由方波激励获得的衰减曲线测量得...     

利用声脉冲管测量平面阵阵元的输入力阻抗

本文提出了以声脉冲管测量辐射头为方形的一种阵元(纵向振动换能器)的输入力阻抗的方法。从电导纳圆图的测量所得到的并联共振频率与从输入力阻抗曲线上确定的共振频率两者非常一致,从而间接证明了这种方法是可行的。     

激光二极管自混合干涉实验仪和微振动研究

用振动激励信号做频率电压变换的倒相触发信号,可以从激光二极管自混合干涉信号还原扬声器谐振时的振动波形,输出信号的振幅与扬声器的振幅成正比. 用正弦波、方波和三角波信号分别激励扬声器,利用自制的激光二极管自混合干涉实验仪观测了的扬声器振动特性,测量了扬声器的谐振曲线.     

基于条纹投影的振动扬声器形变测量

动态傅里叶变换轮廓术是将结构光投影和傅里叶变换理论相结合的三维面形测量技术,它只需一帧变形条纹就可以恢复物体的三维面形,且速度快、精度高、易于实现,被广泛应用于各领域的动态三维测量。利用动态傅里叶变换轮廓术对扬声器在给定激励源频率下的振动过程进行动态测量,得到扬声器纸盆不同频率振动的三维面形数据。结合扬声器发声的机理,通过对振动扬声器三维面形数据的处理和分析,得到扬声器纸盆局部任意时刻的形变量,分析了产生纸盆自身形变量可能的原因,探究了纸盆振动对扬声器性能的影响,为扬声器的设计和改进提供依据。     

气流扬声器振动系统的设计原理

本文用等效电路方法分析了电动气流扬声器振动系统的特性,求得了气流扬声器的输入阻抗和位移振幅的频率特性,并把结果用于典型扬声器,说明用等效电路分析指导气流扬声器设计的作用。气流扬声器振动系统所需的电功率与其机械共振频率的四次方成正比,其声辐射主要限于共振频率以下,因而高频特性较差。求得了在共振频率以下,频率响应平直的最佳条件,实验表明,在最佳条件下,气流扬声器的高频特性随着磁隙中的磁感应强度的增加仍稍有提高。实验结果符合理论分析,测得气流扬声器喇叭喉部的声压级在不同情况下达181分贝或184.8分贝(零分贝等于2×10^-5牛顿/米²)。     

微型扬声器摆动模态对其辐射声场的影响*

与传统电动式扬声器单元相比,微型扬声器单元由于缺少定位支片等部件,更容易受到摆动模态的影响。该文利用激光传感器采集微型扬声器单元振膜各点振动位移,通过理论计算,从辐射声压级、辐射指向性等角度探究矩形微型扬声器单元摆动模态对其辐射声场的影响。经过研究发现,摆动模态会造成微型扬声器单元频响凹陷、中低频存在指向性等现象,对其辐射声场产生明显的影响。     

用声场和类比线路理论研究直射式扬声器系统特性

传统理论用类比线路图分析扬声器系统,认为腔内空气振动属集总参数系统,本文提出腔内空气振动属分布参数系统,通过分析腔内声场,并与类比线路理论有机结合,全面分析扬声器系统的辐射、频响和阻抗特性,得到更具普遍性的规律。     

采用全面最小二乘法测量开口箱扬声器系统低频特性参数

本文分析并建立了开口箱扬声器系统的自回归平均（ＡＲＭＡ）模型参数与低频特性参数的关系，采用全面最小二乘（ＴＬＳ）法辨识开口箱扬声器系统的ＡＲＭＡ模型参数，从而在时域上测出了开口箱扬声器系统的低频特性参数、阻抗曲线和低频响应曲线，取得了较好的结果。     

Transverse hysteretic damping characteristics of a serpentine belt: Modeling and experimental investigation

In this paper, the transverse dynamic hysteretic damping characteristics (HDC) of a serpentine belt are investigated. The variable stiffness and variable damping model (VSDM) constituted of a variable-stiffness spring and a variable-damping damper is developed to estimate the HDC of the belt. A test rig is designed to test the force–displacement hysteresis damping curve and resonance frequencies of serpentine belts with different lengths under diverse loading conditions. The force–displacement hysteresis damping curve getting from the experiment is then used to determine the transverse stiffness and damping coefficients needed for the VSDM. The experiment particularly shows that the orientation of the hysteresis curve swings left and right around each natural frequency as it is a symmetrical point. This interesting phenomenon is explicated in detail with the loss angle which is calculated by two methods. Moreover, two sub-analytical models included in the VSDM are proposed to model the dependence of transverse dynamic stiffness and damping coefficient of a belt on belt length, pretension and excitation frequency. A comparison of the hysteresis curves obtained from the VSDM and experiment indicates that they are in good agreement.     

A FEM-based method to determine the complex material properties of piezoelectric disks

Numerical simulations allow modeling piezoelectric devices and ultrasonic transducers. However, the accuracy in the results is limited by the precise knowledge of the elastic, dielectric and piezoelectric properties of the piezoelectric material. To introduce the energy losses, these properties can be represented by complex numbers, where the real part of the model essentially determines the resonance frequencies and the imaginary part determines the amplitude of each resonant mode. In this work, a method based on the Finite Element Method (FEM) is modified to obtain the imaginary material properties of piezoelectric disks. The material properties are determined from the electrical impedance curve of the disk, which is measured by an impedance analyzer. The method consists in obtaining the material properties that minimize the error between experimental and numerical impedance curves over a wide range of frequencies. The proposed methodology starts with a sensitivity analysis of each parameter, determining the influence of each parameter over a set of resonant modes. Sensitivity results are used to implement a preliminary algorithm approaching the solution in order to avoid the search to be trapped into a local minimum. The method is applied to determine the material properties of a Pz27 disk sample from Ferroperm. The obtained properties are used to calculate the electrical impedance curve of the disk with a Finite Element algorithm, which is compared with the experimental electrical impedance curve. Additionally, the results were validated by comparing the numerical displacement profile with the displacements measured by a laser Doppler vibrometer. The comparison between the numerical and experimental results shows excellent agreement for both electrical impedance curve and for the displacement profile over the disk surface. The agreement between numerical and experimental displacement profiles shows that, although only the electrical impedance curve is considered in the adjustment procedure, the obtained material properties allow simulating the displacement amplitude accurately.     

Measurement of the dispersion relation of guided non-axisymmetric waves in filament-wound cylindrical structures

To determine the dispersion relation, guided waves are excited in specimens over a broad frequency range. The surface displacements are measured over time and space. The recorded data are analysed using a quasi-three-dimensional spectrum estimation algorithm. In the time domain a fast Fourier transform is used to extract the frequencies. To obtain the wave numbers, in space a two-dimensional matrix-pencil approach is applied to the data set. Using a suitable constitutive model (transversely isotropic or orthotropic) dispersion curves are calculated. Good agreement was found between the experimental and the numerically calculated dispersion relations after adjusting the material parameters. Since the dispersion relation of a structure depends on the mechanical material properties frequency-dependent material parameters can be extracted from the above-mentioned relation between frequency and wave number.     

Passive-active vibration isolation systems to produce zero or infinite dynamic modulus: theoretical and conceptual design strategies

The application of mechanical springs connected in parallel and/or in series with active springs can produce dynamical systems characterised by infinite or zero value stiffness. This mathematical model is extended to more general cases by examining the dynamic modulus associated with damping, stiffness and mass effects. This produces a theoretical basis on which to design an isolation system with infinite or zero dynamic modulus, such that stiffness and damping may have infinite or zero values. Several theoretical designs using a mixture of passive and active systems connected in parallel and/or in series are proposed to overcome limitations of feedback gain experienced in practice to achieve an infinite or zero dynamic modulus. It is shown that such systems can be developed to reduce the weight supported by active actuators as demonstrated, for example, by examining suspension systems of very low natural frequency or with a very large supporting stiffness or with a viscous damper or a self-excited vibration oscillator. A more general system is created by combining these individual systems allowing adjustment of the supporting stiffness and damping using both displacement and velocity feedback controls. Frequency response curves show the effects of active feedback control on the dynamical behaviour of these systems. The theoretical design strategies presented can be applied to design feasible hybrid vibration control systems displaying increased control performance.     

Quasi-active suspension design using magnetorheological dampers

Quasi-active damping is a method of coupled mechanical and control system design using multiple semi-active dampers. By designing the systems such that the desired control force may always be achieved using a combination of the dampers, quasi-active damping seeks to approach levels of vibration isolation achievable through active damping, whilst retaining the desirable attributes of semi-active systems. In this article a design is proposed for a quasi-active, base-isolating suspension system.Control laws are firstly defined in a generalised form, where semi-active dampers are considered as idealised variable viscous dampers. This system is used to demonstrate in detail the principles of quasi-active damping, in particular the necessary interaction between mechanical and control systems. It is shown how such a system can produce a tunable, quasi-active region in the frequency response of very low displacement transmissibility.Quasi-active control laws are then proposed which are specific for use with magnetorheological dampers. These are validated in simulation using a realistic model of the damper dynamics, again producing a quasi-active region in the frequency response. Finally, the robustness of the magnetorheological, quasi-active suspension system is demonstrated.     

Polarization-dependent fractional loss improvement of laser scribed GO FeSi steels

Magnetization curves of untreated and laser scribed GO FeSi steels were measured for 19 different frequencies from 0.05 to 500 Hz and for four polarizations from 1.4 to 1.7 T. From hysteresis loops, hysteresis losses were separated and frequency-dependent anomaly factors were calculated. Frequency-dependent anomaly factors for all measured polarizations can be very well described by an empirical equation. This behavior can be explained by the fact that an increase in polarization at a fixed magnetizing frequency corresponds to an increase of magnetizing frequency at a fixed polarization. Both an increase in frequency and an increase in polarization activate a higher number of domain walls in the magnetization process. The power losses can be described only by the frequency dependence of the anomaly factor and by the additional knowledge of hysteresis loss.     

Measurement of resonance frequency and loss factor of a microphone diaphragm using a laser vibrometer

The pressure sensitivity of a laboratory standard microphone is determined using a reciprocity technique that measures the electrical transfer impedance of two microphones connected acoustically by a coupler. The electrical transfer impedance is a function of the coupler volume and the equivalent volumes of the microphones. The equivalent volume given as a function of the frequency can be determined in experiments or can be calculated if the equivalent volume at a low frequency as well as the resonance frequency and loss factor of the microphone diaphragm are known. Therefore, it is necessary to determine the resonance frequency and the loss factor accurately to obtain an accurate reading of the pressure sensitivity.In this paper, a new method to determine the resonance frequency and loss factor of a microphone diaphragm is proposed. The frequency response of the diaphragm displacement is measured by a laser vibrometer and the part of the response near the resonance frequency is used to determine the microphone parameters via least square fitting with the equation of a vibration model with one degree-of-freedom. Since the values measured by this method are close to the nominal values and the repeatability is highly feasible, the proposed method will be useful to determine the resonance frequency and loss factor of a microphone diaphragm.     

Quantum limits of cold damping with optomechanical coupling

Thermal noise of a mirror can be reduced by cold damping. The displacement is measured with a high-finesse cavity and controlled with the radiation pressure of a modulated light beam. We establish the general quantum limits of noise in cold damping mechanisms and we show that the optomechanical system allows to reach these limits. Displacement noise can be arbitrarily reduced in a narrow frequency band. In a wide-band analysis we show that thermal fluctuations are reduced as with classical damping whereas quantum zero-point fluctuations are left unchanged. The only limit of cold damping is then due to zero-point energy of the mirror. Received 1st August 2001 and Received in final form 12 October 2001     

On the damped frequency response of a finite-element model of the cat eardrum

This article presents frequency responses calculated using a three-dimensional finite-element model of the cat eardrum that includes damping. The damping is represented by both mass-proportional and stiffness-proportional terms. With light damping, the frequency responses of points on the eardrum away from the manubrium display numerous narrow minima and maxima, the frequencies and amplitudes of which are different for different positions on the eardrum. The frequency response on the manubrium is smoother than that on the eardrum away from the manubrium. Increasing the degree of damping smooths the frequency responses both on the manubrium and on the eardrum away from the manubrium. The overall displacement magnitudes are not significantly reduced even when the damping is heavy enough to smooth out all but the largest variations. Experimentally observed frequency responses of the cat eardrum are presented for comparison with the model results.     

Measurement of the glottal impedance with a mechanical model

An approximate but realistic model of the human larynx was constructed to gain better knowledge of the complex glottal impedance and its dependence on glottal width, flow, and frequency. The glottal width was adjustable from 0 to 3 mm, the flow from 0 to 500 cm3/s. The model was fitted into a system of tubes, through which compressed air could be conducted. Supraglottally, a broadband signal was fed into the tube, and, with a two-microphone directional coupler, the complex glottal impedance at a given reference plane was directly determined as a function of frequency. Since the calculated impedance is sensitively dependent on the definition of the position of the reference plane, it is difficult to obtain quantitative statements about the frequency dependence. Nevertheless, in the presence of flow, it is possible to achieve reliable results by analysis of the relative position of the measured curves. On the one hand, the glottal inductance decreases linearly with increasing flow velocity; on the other hand, it diminishes nonlinearly with decreasing frequency. Finally, some difficulties in the definition of glottal impedance are pointed out.