The Modelling and Vibration Control of Beams With Active Constrained Layer Damping

Shi, Yinming; Li, Z.F.; Hu, Hua; Zhang, Fu; Liu, T.X.

doi:10.1006/jsvi.2001.3614

Cited by 35 publications

(17 citation statements)

References 20 publications

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“…where Em (m = 1, 2, 3, 4) are complex functions in T. From equation (7) and (9) into equation (5) (11) where H,.. (m = 1, 2,... , 26) are complex functions in T. From (7), (9) and (11) into (6), we get the third order approximation as: (12) where P,,,, (m = 1, 2, ... , 55, 62, 63, ... ,86) are complex functions in T. From the above analysis the solution of u is given by…”

Section: Perturbation Analysismentioning

confidence: 99%

“…Eissa and El-Ganaini [5,6] studied the control of vibration and dynamic chaos of mechanical structures having quadratic and cubic non-linearities, subjected to harmonic excitation using single and multi-absorbers. Active constrained layer damping (ACLD) has been successfully utilized as effective means of damping out the vibration of various flexible structures [7][8][9][10][11][12]. In weakly non-linear systems, internal resonances may occur if the linear natural frequencies are commensurate or nearly commensurate, and internal resonances provide coupling and energy exchange among the vibration modes [13,14].…”

Section: Introductionmentioning

confidence: 99%

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Comparison between passive and active control of a non-linear dynamical system

El-Serafi

Eissa

El-Sherbiny

et al. 2006

Japan J. Indust. Appl. Math.

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Vibrations and dynamic chaos should be controlled in structures and machines. The wing of the airplane should be free from vibrations or it should be kept minimum. To do so, two main strategies are used. They are passive and active control methods. In this paper we present a mathematical study of passive and active control in some non-linear differential equations describing the vibration of the wing. Firstly, non-linear differential equation representing the wing system subjected to multi-excitation force is considered and solved using the method of multiple scale perturbation. Secondly, a tuned mass absorber (TMA) is applied to the system at simultaneous primary resonance. Thirdly, the same system is considered with 1:2 internal resonance active control absorber. The approximate solution is derived up to the fourth order approximation, the stability of the system is investigated applying both frequency response equations and phase plane methods. Previous work regarding the wing vibration dealt only with a linear system describing its vibration. Some recommendations are given by the end of the work.

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Section: Perturbation Analysismentioning

confidence: 99%

Section: Introductionmentioning

confidence: 99%

Comparison between passive and active control of a non-linear dynamical system

El-Serafi

Eissa

El-Sherbiny

et al. 2006

Japan J. Indust. Appl. Math.

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“…Control of vibrational waves in structures includes the control of structure-borne vibration and noise, disturbance rejection in flexible manipulators, precision broadband control of pointing devices and space systems in microgravity environment. It is well established that, an efficient way to increase damping is by sandwich construction with alternating elastic and viscoelastic layers, and is known as passive damping with constrained layers [1,2,3] . Active vibration control, in which active materials are used as actuators and sensors, has been studied with many approaches with various feedback laws and suitable controllers.…”

Section: Introductionmentioning

confidence: 99%

Viscoelastic phenomenology based structure assignment for closed-loop vibration control of a beam with sensors and actuators

Vadiraja

Mahapatra

2009

SPIE Proceedings

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In this paper we incorporate a novel approach to synthesize a class of closed-loop feedback control, based on the variational structure assignment. Properties of a viscoelastic system are used to design an active feedback controller for an undamped structural system with distributed sensor, actuator and controller. Wave dispersion properties of onedimensional beam system have been studied. Efficiency of the chosen viscoelastic model in enhancing damping and stability properties of one-dimensional viscoelastic bar have been analyzed. The variational structure is projected on a solution space of a closed-loop system involving a weakly damped structure with distributed sensor and actuator with controller. These assign the phenomenology based internal strain rate damping parameter of a viscoelastic system to the usual elastic structure but with active control. In the formulation a model of cantilever beam with non-collocated actuator and sensor has been considered. The formulation leads to the matrix identification problem of two dynamic stiffness matrices. The method has been simplified to obtain control system gains for the free vibration control of a cantilever beam system with collocated actuator-sensor, using quadratic optimal control and pole-placement methods.

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“…Eissa and El-Ganaini [6,7] studied the control of both vibration and dynamic chaos of both internal combustion engines and mechanical structures having quadratic and cubic nonlinearties, subjected to harmonic excitation using single and multi-absorbers. Active constrained layer damping (ACLD) has been successfully utilized as effective means of damping out the vibration of various flexible structures [8][9][10][11][12][13]. A variable stiffness vibration absorber without damping is used for controlling the principal mode of a vibrating structure.…”

Section: Introductionmentioning

confidence: 99%

“…The derivatives will be in the forms (12,13) where ∂ ∂ = n Tn D , n = 0,1. Equating the similar powers of ε in both side's yields.…”

Section: Introductionmentioning

confidence: 99%

A Comparison between Active and Passive Vibration Control of Non-Linear Simple Pendulum. Part II: Longitudinal Tuned Absorber and Negative Gφ and Gφn Feedback

Eissa

Sayed

2006

MCA

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In part I [1] we dealt with a tuned absorber, which can move in the transversally direction, where it is added to an externally excited pendulum. Active control is applied to the system via negative velocity feedback or its square or cubic value. The multiple time scale perturbation technique is applied throughout. An approximate solution is derived up to second order approximation. The stability of the system is investigated applying both frequency response equations and phase plane methods. The effects of the absorber on system behavior are studied numerically. Optimum working conditions of the system are obtained applying passive and active control methods. Both control methods are demonstrated numerically. In this paper, a tuned absorber, in the longitudinal direction, is added to an externally excited pendulum. Active control is applied to the system via negative acceleration feedback or via negative angular displacement or its square or cubic value. An approximate solution is derived up to the second order approximation for the system with absorber. The stability of the system is investigated applying both frequency response equations and phase plane methods. The effects of the absorber on system behavior are studied numerically. Optimum working conditions of the system are extracted when applying both passive and active control methods.

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The Modelling and Vibration Control of Beams With Active Constrained Layer Damping

Cited by 35 publications

References 20 publications

Comparison between passive and active control of a non-linear dynamical system

Comparison between passive and active control of a non-linear dynamical system

Viscoelastic phenomenology based structure assignment for closed-loop vibration control of a beam with sensors and actuators

A Comparison between Active and Passive Vibration Control of Non-Linear Simple Pendulum. Part II: Longitudinal Tuned Absorber and Negative Gφ and Gφn Feedback

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