磁力负刚度薄膜结构低频吸声特性

针对背腔深度较小的薄膜吸声结构难以实现低频吸声的问题,提出了磁力负刚度的解决方法。采用传递矩阵法,建立了负刚度薄膜吸声结构理论模型,分析得出该结构的声阻抗等同与大背腔常规薄膜吸声结构的声阻抗;阻抗管实验验证得出,在一定磁场条件下,不同背腔的负刚度薄膜吸声结构与无负刚度结构相比其共振频率显著下降,吸声系数曲线与理论结构吻合。负刚度机制能够降低薄膜吸声结构的共振频率,用较小背腔实现低频吸声,从而实现薄型低频吸声结构设计。     

对探究影响摩擦力大小因素实验的分析及改进

对传统的影响滑动摩擦力大小因素的实验进行改进,把物块的运动变换成下面木板的运动,并用定滑轮改变拉力的方向.使用改进后的装置不但可以降低操作的难度,还可提高实验的准确性.     

空间臂式补偿机构轴承预紧力与系统刚度关系分析

为了补偿空间光学望远镜在轨跟踪目标过程中受空间各种因素影响而导致的光学系统视轴和目标之间产生的相对移动和旋转(即指向偏差和指向振荡),设计由臂式补偿机构控制望远镜补偿与目标的相对运动.但由于臂式补偿机构的尺寸和质量严格限制在一定范围内,且望远镜尺寸很大,质量达3 000 kg,这种结构形式导致系统刚度很低.为了满足控制系统提出的结构高刚度要求,在系统结构形式确定的情况下,分析施加轴承预紧力提高系统刚度的可行性.分析了轴承预紧力、轴承刚度和系统刚度之间的关系,获得了轴承预紧力与系统固有频率的关系.分析证明在系统结构形式确定的情况下,施加合适的轴承预紧力,可以提高系统的刚度,同时为轴承最佳预紧力的确定提供了一个有效的方法.     

光子晶体负折射材料中缺陷对成像质量的影响EI北大核心CSCD

利用硅介质柱在空气中周期性排列构成六角结构的光子晶体平板,并在晶体平板中引入不同构型的缺陷,通过改变缺陷介质柱的半径和缺陷中心位置探讨引入缺陷对成像质量产生的影响。时域有限差分法模拟结果表明:介质柱半径和位置的改变,能使光的透射率提高,增加像方的强度。由于缺陷的引入,缺陷之间的相互干扰会降低成像的分辨率。     

光学元件狭缝柔性调节机构的设计与分析

设计了一种狭缝柔性结构的光学元件调节机构,使光学元件在具备较高调节精度的同时,保持较高的导向精度。采用弹性力学应力函数法分析了狭缝柔性结构的刚度,以径向刚度与轴向刚度的比值为目标函数,对狭缝柔性结构尺寸参数进行了优化,在不超过柔性结构材料屈服应力等约束条件下,刚度比最优值达到1 573.6,较大的刚度比值可以减小调节机构的耦合位移,从而提高机构的导向精度。该结构加工装配方便,可实现三自由度(θx-θy-Z)调节。对优化后的柔性结构进行仿真分析,结果表明:径向刚度与轴向刚度比值的仿真值为1 660.4,解析值与仿真值误差为5.23%,证明了刚度分析方法的有效性。优化后的结构,轴向调节行程为2.09 mm,绕x轴偏转角度调节行程为±16.6 mrad,绕y轴偏转角度调节行程可达到±14.4 mrad,满足光学元件调节的大行程要求。     

晶格常数对左手材料的能量透射率及负折射率的影响

研究晶格常数对左手材料的能量透射率、负折射率以及品质因素(FOM)的影响.结果表明,随着晶格常数的减小,左手材料的低阶透射峰出现异常增大,其物理机制为阻抗匹配;左手材料的负折射的中心频率随着晶格常数的减小而蓝移,与理论结果基本一致;晶格常数对左手材料的FOM有重要的影响,当晶格常数减小到一定值时,可以实现完美阻抗匹配,从而得到较高的FOM.     

含负折射率介质的多层结构中倏逝波传播及隧道效应的分析

研究了倏逝波在含负折射率介质的多层平板结构中的传播特性，解析地分析了倏逝波在不同结构参数下的放大或衰减规律及其原因以及能流的分布，并着重讨论了负折射率介质的损耗对隧道效应的影响，最后通过模拟高斯光束在该结构中的传播和能量储存，形象地给出了负折射率介质的损耗对倏逝波的影响和对光子隧道效应的减弱. 关键词： 负折射率介质 倏逝波 隧道效应     

不同负冲角工况下透平叶栅二次流的数值模拟及分析

本文应用TVD格式和Baldwin－Lomax代数紊流模型求解三维NS方程，对一个透平直列叶栅流场在两个不同的负冲角工况下进行了数值模拟，给出了叶栅马蹄涡及其分离鞍点、通道涡、角涡等二次流涡系的结构及其产生发展过程，并对不同工况下的涡系结构及冲角的影响作了详细的分析和比较．本文结果有助于对叶栅二次流涡系结构的产生发展机制的深入了解，同时表明所用数值求解技术有较高的精度和分辨率。     

二维蜂窝格子光子晶体的远场成像特性及界面对成像质量的影响

利用有限时域差分法研究了一种二维蜂窝格子光子晶体的远场亚波长成像特性，发现和折射率为-1时的负折射成像规律符合得很好.但是由于晶格结构本身的特性，入射光以大角度入射时，这种结构的耦合效率很低，影响了像的强度和质量.通过适当改变界面上介质柱的半径的方法可以提高耦合效率，进而有效提高成像的质量和强度.     

结构参数及工质对止推气体轴承的影响分析

利用Fluent对环形平板静压止推气体轴承进行了流场的模拟计算,分析结构参数及气体工质对气体轴承静态性能的影响。计算结果表明:环形平板静压气体止推轴承的承载力和最优气膜厚度随着供气孔数目和供气孔直径的增大而增大,而最大静态刚度随着供气孔数目的增加而增大,随着供气孔直径的增加而减小。使用氦气做工质能在小耗气量下获得比空气更大的承载力,但最大静态刚度有所下降,氦气对应的最优气膜厚度约是空气对应最优气膜厚度的1.7倍。     

Analysis and experiment of a vibration isolator using a novel magnetic spring with negative stiffness

The vibration isolator using a novel magnetic spring with negative stiffness (MS-NS) is proposed in this paper. The proposed isolator which combines a positive stiffness spring with the MS-NS in parallel possesses the characteristic of high-static–low-dynamic stiffness. The MS-NS is composed of three cuboidal magnets configured in repulsive interaction. An analytical expression of the stiffness of the MS-NS is derived by using the magnetic charge model, and the approximation to the exact analytical expression is sought. Then, the nonlinearity of the stiffness is analyzed, and it is shown that the MS-NS is approximately linear for small oscillations. In order to validate the correctness and effectiveness of the MS-NS, the vibration transmissibility of the proposed isolator with and without the MS-NS is measured. The experimental results demonstrate that combining a vibration isolator with the MS-NS in parallel can lower the natural frequency of the isolator; and the analytical calculations and experimental results show a good consistency.     

A tunable high-static-low-dynamic stiffness vibration isolator

In this study, a novel vibration isolator is developed. The developed isolator possesses the characteristics of high-static-low-dynamic stiffness (HSLDS) and can act passively or semi-actively. The HSLDS property of the isolator is obtained by connecting a mechanical spring, in parallel with a magnetic spring that is constructed by a pair of electromagnets and a permanent magnet. The mechanical spring is a structural beam whose stiffness exhibits a hardening behavior. The stiffness of the magnetic spring can be positive or negative, depending on the polarity of the current to the electromagnets. A passive HSLDS isolator is obtained when the electromagnet current is zero. In the stiffness characterization study, the analytical model for each of the springs is established and the tuning parameters are identified. Using the stiffness models, the design optimization issues are investigated. In the experimental study, the effectiveness of the isolator for vibration isolation is tested. The analytical natural frequencies of the isolator are validated experimentally. The relationships between the displacement transmissibility and the exciting frequency are measured both under the passive mode and under the semi-active mode. The on-line tuning capability of the isolator is investigated.     

A study of a nonlinear vibration isolator with a quasi-zero stiffness characteristic

A vibration isolator consisting of a vertical linear spring and two nonlinear pre-stressed oblique springs is considered in this paper. The system has both geometrical and physical nonlinearity. Firstly, a static analysis is carried out. The softening parameter leading to quasi-zero dynamic stiffness at the equilibrium position is obtained as a function of the initial geometry, pre-stress and the stiffness of the springs. The optimal combination of the system parameters is found that maximises the displacement from the equilibrium position when the prescribed stiffness is equal to that of the vertical spring alone. It also satisfies the condition that the dynamic stiffness only changes slightly in the neighbourhood of the static equilibrium position. For these values, a dynamical analysis of the isolator under asymmetric excitation is performed to quantify the undesirable effects of the nonlinearities. It includes considering the possibilities of the appearance of period-doubling bifurcation and its development into chaotic motion. For this purpose, approximate analytical methods and numerical simulations accompanied with qualitative methods including phase plane plots, Poincaré maps and Lyapunov exponents are used. Finally, the frequency at which the first period-doubling bifurcation appears is found and the effect of damping on this frequency determined.     

Analysis of Coulomb friction vibration dampers

An analysis of the steady state response of a rotational Coulomb friction vibration damper has been carried out. Such dampers are sometimes used in various industrial applications. Analysis of the steady state phase plane is used to determine various response quantities such as amplitude ratio, phase lag, energy dissipated per cycle, and rms power loss. The analysis shows that the response can be categorized into one of three main types. Expressions are developed to predict effect of the addition of a damper on the power and the disturbance amplitude transmitted to the load. It is shown that simple one parameter relationships exist for predicting the maximum vibration reduction achievable with this type of damper.     

金属橡胶隔振器随机振动加速度响应分析

通过对随机激励下干摩擦隔振系统理论的深入研究,推导了金属橡胶隔振系统随机激励均方加速度响应求解公式.对金属橡胶隔振器进行随机振动试验,分析了金属橡胶隔振器相对密度、预变形及所加试验量级对金属橡胶隔振系统均方根加速度响应的影响,得到了相关变化规律曲线.同时还分析了均方根加速度响应理论值与试验值的对比误差,确定了公式的适用范围. 关键词： 金属橡胶隔振器 随机振动 加速度响应     

Metrics for diagnosing negative mass and stiffness when uncoupling experimental and analytical substructures

When testing to identify an experimental model of a substructure, it is often beneficial to exercise the interface by attaching a fixture such as a rigid mass. An analytical representation of the fixture must then be used to subtract its effects from the assembly. However, this can cause the mass and stiffness matrices to become indefinite in some situations. This paper presents two new metrics that can be used by the analyst to determine the cause of indefinite mass or stiffness matrices after substructure uncoupling. The metrics rank the experimental and fixture modes based upon their contribution to offending negative eigenvalues. Once the troublesome modes have been identified, they can be inspected and often reveal why the mass has become negative. Two examples are presented to demonstrate the metrics and to illustrate the physical phenomena that they reveal.     

Active pneumatic vibration isolation system using negative stiffness structures for a vehicle seat

In this paper, an active pneumatic vibration isolation system using negative stiffness structures (NSS) for a vehicle seat in low excitation frequencies is proposed, which is named as an active system with NSS. Here, the negative stiffness structures (NSS) are used to minimize the vibratory attraction of a vehicle seat. Owing to the time-varying and nonlinear behavior of the proposed system, it is not easy to build an accurate dynamic for model-based controller design. Thus, an adaptive intelligent backstepping controller (AIBC) is designed to manage the system operation for high-isolation effectiveness. In addition, an auxiliary control effort is also introduced to eliminate the effect of the unpredictable perturbations. Moreover, a radial basis function neural network (RBFNN) model is utilized to estimate the optimal gain of the auxiliary control effort. Final control input and the adaptive law for updating coefficients of the approximate series can be obtained step by step using a suitable Lyapunov function. Afterward, the isolation performance of the proposed system is assessed experimentally. In addition, the effectiveness of the designed controller for the proposed system is also compared with that of the traditional backstepping controller (BC). The experimental results show that the isolation effectiveness of the proposed system is better than that of the active system without NSS. Furthermore, the undesirable chattering phenomenon in control effort is quite reduced by the estimation mechanism. Finally, some concluding remarks are given at the end of the paper.     

Vibration isolation characteristics of a nonlinear isolator using Euler buckled beam as negative stiffness corrector: A theoretical and experimental study

This paper concerns the vibration isolation characteristics of a nonlinear isolator using Euler buckled beams as negative stiffness corrector. Both analytical and experimental studies are carried out. The Harmonic Balance Method (HBM) is used to determine the primary resonance response for the single degree of freedom (SDOF) nonlinear system composed by a loaded mass and the nonlinear isolator. The distuning of the loaded mass is taken into consideration, resulting in a Helmoholtz–Duffing equation. The performance of the nonlinear isolator is evaluated by the defined two kinds of transmissibility and compared with that of the linear isolator without the stiffness corrector. The study shows that the asymmetric SDOF nonlinear system can behave like a purely softening, a softening–hardening or a purely hardening system, depending on the magnitude of the excitation level. An experimental apparatus is set up to validate the analytical results. The transmissibility results of the SDOF nonlinear system under base excitation with both discrete sinusoidal frequencies and slowly forward and backward sweeps are given and discussed. The complex jump phenomena under different excitation levels are identified. By introducing the stiffness corrector, the starting frequency of isolation of the nonlinear isolator is found to be lower than that of the linear one with the same support capacity. The proposed nonlinear isolator performs well in applications where the excitation amplitude is not too large.     

Performance analysis of nonlinear vibration isolator with magneto-rheological damper

A nonlinear vibration isolator is considered to study effectiveness of isolation against harmonic force and displacement excitations. Nonlinearity in the magneto-rheological (MR) fluid based damper as well as in the elastic member is taken into account. The MR-damper has been modeled including Bouc–Wen hysteretic element and the spring is taken to have cubic nonlinearity. Analytical expression for the energy dissipation characteristics of the damper has been derived. Near resonant response of the isolated mass is obtained by a modified averaging technique suitable for hysteretic type nonlinearity present in the system. The performance of the isolators is estimated for various nonlinear stiffness values, both hardening and softening types. Different performance measures are also proposed to judge the performance of the nonlinear isolator.