scholarly journals Vibration Suppression Control of 2-Mass System Based on Robust Control. Experimental Studies.

1995 ◽  
Vol 115 (11) ◽  
pp. 1393-1401 ◽  
Author(s):  
Shigeyasu Kawaji ◽  
Kazunobu Kanazawa
Author(s):  
F Dohnal

Transient vibrations in mechanical systems are a common problem in engineering. Several theoretical studies have shown analytically and numerically that a vibrating system can be stabilised or its vibrations can be reduced when excited close to a specific parametric combination resonance frequency. At this operation, the transient vibrations are effectively damped by parametric excitation. The basic step in exploiting this method is its experimental implementation in mechanical systems. In this review, recent experiments are discussed for a simple chain mass system, a continuous cantilever and a flexible rotor system. The parametric excitation is realised by electromagnetic variable-stiffness actuators driven by a periodic open-loop control. It is demonstrated experimentally that a parametrically excited structure can exhibit enhanced damping properties. A certain level of the excitation amplitude has to be exceeded to achieve the damping effect in which the existing damping in the system is artificially amplified. Upon exceeding this value, the additional artificial damping provided to the system is significant and most effective for vibration suppression of the lower vibration modes.


2020 ◽  
pp. 107754632094378
Author(s):  
Haiping Liu ◽  
Kaili Xiao ◽  
PengPeng Zhao ◽  
Dongmei Zhu

Stiffness and damping of a structure usually show the opposite change so that the resonant frequency and the static load bearing capacity of a mechanical system often exhibit contradiction. To solve this dilemma, a novel high-damping oscillator which is constructed by a nested diamond structure with the purpose of enhancing the damping property is proposed in this study without reducing the overall systematic stiffness. The mathematical model and geometrical relationships are established at first. And then, the steady-state solutions under base excitation are derived by using the harmonic balance method and further verified by numerical simulation. In addition, the effects of some design parameters on the equivalent damping ratio for the high-damping oscillator are studied to reveal the nonlinear characteristic. Besides, the natural frequency of the nonlinear oscillator is also presented and investigated. By using the displacement transmissibility and comparing with the traditional linear isolator with the same overall stiffness, the vibration suppression performance of the high-damping oscillator is addressed. The obtained calculating results demonstrate that the vibration control performance of the high-damping oscillator outperforms the linear counterpart around resonant frequency. Moreover, the influences of systematic parameters of the high-damping oscillator for the base excitation case on the vibration transmissibility are also discussed, respectively. Finally, an experimental campaign is conducted on an in-house-built test rig to corroborate the accuracy of the analytical solutions of the high-damping oscillation system. The results discussed in this study provide a useful guideline, which can help to design this class of high-damping oscillation system.


2008 ◽  
Vol 144 ◽  
pp. 22-26 ◽  
Author(s):  
Arkadiusz Mystkowski ◽  
Zdzisław Gosiewski

Stabilization of a plant in case of uncertainty parameters and unmodeled dynamics are the main problems considered in this paper. A robust control of motion of a rigid shaft that is supported by magnetic bearings was used as an example. The dynamics of the active magnetic suspension system is characterized by instability and uncertainty. The uncertainty is modeled as an additive and multiplicative. Robust controller H∞ was designed for the defined plant with the uncertainty models. The robust controller assures high quality of control despite the uncertainty models. Robust control of vibrations of a rigid rotor is confirmed by experimental studies. A digital signal processor is used to execute the control algorithm in real time.


Author(s):  
Stephan Algermissen ◽  
Ralf Keimer ◽  
Michael Rose ◽  
Elmar Breitbach ◽  
Hans Peter Monner

Author(s):  
Vladimir P. Tregubov ◽  
◽  
Nadezhda K. Egorova ◽  

It is noted that the Kelvin—Voigt model is unsuitable for describing some polymers and biological tissues. In these cases, a three-component combination of elements, which consists of a spring and damper, connected in parallel and a spring sequentially attached to them, is used. The force characteristic of such a combination includes not only the strain, strain rate, and force, but also the rate of force change. Examples of such systems are the blood vessel wall and the intervertebral disc, which have been given special attention. Since the motion of such systems is described by an ordinary third-order differential equation, they are classified as systems with a non-integer number of degrees of freedom. For a single-mass oscillating system with one and a half degrees of freedom, a transfer function was constructed using the Laplace transform. In addition, the amplitude-frequency response (AFR) was also constructed. Analysis of this characteristic showed that increasing the damping coefficient from zero to infinity first leads to a decrease in its maximum to a certain non-zero value, and then to an increase and reaching infinity with an infinite value of the damping coefficient. The same feature is demonstrated on a two-mass system of chain structure, each link of which has one and a half degrees of freedom. A sequential combination of seven such links was used to model the lumbar spine in the structure of a General body model of a sitting person subject to vertical vibration. Multi-link elastic-viscous joints were used to model the multi-articular muscles of the lumbar spine. Additional experimental studies are needed to determine the numerical values of the parameters of the proposed model.


1999 ◽  
Vol 119 (8-9) ◽  
pp. 1121-1127 ◽  
Author(s):  
Hirohito Funato ◽  
Kiyohito Yamamoto ◽  
Kenji Hara ◽  
Seiji Hashimoto ◽  
Kenzo Kamiyama

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