Vibration Analysis and Control New Trends and Developments Part 1 pot

Contents Preface IX Chapter 1 Adaptive Tuned Vibration Absorbers: Design Principles, Concepts and Physical Implementation 1 Philip Bonello Chapter 2 Design of Active Vibration Absorbe

VIBRATION ANALYSIS AND CONTROL – NEW TRENDS

AND DEVELOPMENTS Edited by Francisco Beltrán-Carbajal

Vibration Analysis and Control – New Trends and Developments

Edited by Francisco Beltrán-Carbajal

Published by InTech

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Contents

Preface IX

Chapter 1 Adaptive Tuned Vibration Absorbers:

Design Principles, Concepts and Physical Implementation 1

Philip Bonello Chapter 2 Design of Active Vibration Absorbers

Using On-Line Estimation

of Parameters and Signals 27

Francisco Beltran-Carbajal, Gerardo Silva-Navarro, Benjamin Vazquez-Gonzalez and Esteban Chavez-Conde Chapter 3 Seismic Response Reduction of Eccentric

Structures Using Liquid Dampers 47

Linsheng Huo and Hongnan Li Chapter 4 Active Control of Human-Induced Vibrations

Using a Proof-Mass Actuator 71

Iván M Díaz Chapter 5 Control Strategies

for Vehicle Suspension System Featuring Magnetorheological (MR) Damper 97

Min-Sang Seong, Seung-Bok Choi and Kum-Gil Sung Chapter 6 A Semiactive Vibration Control Design

for Suspension Systems with Mr Dampers

Hamid Reza Karimi 115

Chapter 7 Control of Nonlinear Active Vehicle Suspension

Systems Using Disturbance Observers 131

Francisco Beltran-Carbajal, Esteban Chavez-Conde, Gerardo Silva Navarro, Benjamin Vazquez Gonzalez and Antonio Favela Contreras

VI Contents

Chapter 8 Semi-Active Control of Civil Structures Based

on the Prediction of the Structural Response:

Integrated Design Approach 151

Kazuhiko Hiramoto, Taichi Matsuoka and Katsuaki Sunakoda Chapter 9 Seismic Response Control Using Smart Materials 173

Sreekala R, Muthumani K, Nagesh R Iyer

Chapter 10 Whys and Wherefores of Transmissibility 197

N M M Maia, A P V Urgueira and R A B Almeida Chapter 11 Control Design Methodologies for Vibration

Mitigation on Wind Turbine Systems 217

Ragnar Eide and Hamid Reza Karimi Chapter 12 Active Isolation and Damping of Vibrations for

High Precision Laser Cutting Machine 243

Andrea Tonoli, Angelo Bonfitto and Mario Silvagni Chapter 13 Bearings Fault Detection Using Inference Tools 263

Miguel Delgado Prieto, Jordi Cusidó i Roura and Jose Luis Romeral Martínez

Chapter 14 Vibration Analysis of an Oil Production Platform

Submitted to Dynamic Actions Induced by Mechanical Equipment 281

José Guilherme Santos da Silva, Ana Cristina Castro Fontenla Sieira, Luciano Rodrigues Ornelas de Lima and Bruno Dias Rimola

Chapter 15 MIMO Vibration Control for a Flexible Rail Car Body:

Design and Experimental Validation 309

Alexander Schirrer, Martin Kozek and Jürgen Schöftner Chapter 16 Changes in Brain Blood Flow on Frontal Cortex Depending

on Facial Vibrotactile Stimuli 337

Hisao Hiraba, Takako Sato, Satoshi Nishimura, Masaru Yamaoka, Motoharu Inoue, Mitsuyasu Sato, Takatoshi Iida, Satoko Wada, Tadao Fujiwara and Koichiro Ueda

Preface

This book focuses on the very important and diverse field of vibration analysis and control The sixteen chapters of the book written by selected experts from international scientific community cover a wide range of interesting research topics related to original and innovative design methodologies of passive, semi-active and active vibration control schemes, dynamic vibration absorbers, vehicle suspension systems, structural vibration, identification, vibration control devices, smart materials, fault detection, finite element analysis and several other recent practical applications and theoretical studies of this fascinating field of vibration analysis and control The book is addressed not only to both academic and industrial researchers and practitioners of this field, but also to undergraduate and postgraduate engineering students and other experts and newcomers in a variety of disciplines seeking to know more about the state of the art, challenging open problems, innovative solution proposals and new trends and developments in this area

The book is organized into 16 chapters A brief description of every chapter follows Chapter 1 presents the basic design principles of adaptive tuned vibration absorbers (ATVA) and a comprehensive review of the various design concepts that have been presented for the ATVA, including the latest innovations contributed by the author Chapter 2 introduces a design approach for active vibration absorption schemes in linear mass-spring-damper mechanical systems subject to exogenous harmonic vibrations, which can simultaneously be used for vibration attenuation and desired reference trajectory tracking tasks Chapter 3 deals with the seismic response control of eccentric structures using Circular Tuned Liquid Column Dampers (CTLCD) The optimal control parameters are derived from the motion equation of the CTLCD-structure system and supposing that ground motion is a stochastic process Chapter 4 presents the practical implementation of an active mass damper to cancel excessive vertical vibrations on an in-service office floor and on an in-service footbridge In Chapter 5, the authors describe the formulation and experimental evaluation of various vibration control strategies for semi-active vehicle suspension system with magnetorheological (MR) dampers The design of a back-stepping control scheme for semi-active vehicle suspension systems with MR dampers is the focus of Chapter 6 Chapter 7 proposes a robust control scheme based on the real-time estimation of perturbation signals for active nonlinear or linear vehicle suspension systems subject

to unknown exogenous disturbances due to irregular road surfaces Chapter 8

of the proposed schemes is to reduce the torque variations by using speed control with collective blade pitch adjustments Chapter 12 focuses on the evaluation of an active isolation and vibration damping device on the working cell of a micro-mechanical laser center, using active electromagnetic actuators Chapter 13 presents an overview of multisensory inference approaches used to characterize motor ball bearings, and their application to a set of motors with distributed fault failure The results show that a multivariable design contributes positively to damage monitoring of bearings Chapter

14 investigates the dynamic behavior of an oil production platform submitted to impacts produced by rotating machinery A computational model is developed for the structural system dynamic analysis The peak acceleration values and maximum displacements and velocities are employed to evaluate the structural model performance in terms of human comfort, maximum tolerances of the mechanical equipment and vibration serviceability limit states of the structural system Chapter 15 proposes LQG and weighted H2 MIMO control design methods for the vibration control of lightweight rail car body structures These designs are studied and compared to achieve vibration reduction and passenger ride comfort improvement in a highly flexible metro rail car body The metro car body structure is directly actuated via locally mounted Piezo stack actuators Chapter 16 concludes the book, describing a study on vibrotactile stimuli on the submandibular glands stimulated by vibration with one motor and two motors Finally, I would like to express my sincere gratitude to all the authors for their excellent contributions, which I am sure will be valuable to the readers I would also like to thank the editorial staff at InTech for their great effort and support in the process of edition and publication of the book

I truly hope that this book can be useful and inspiring for contributing to the development of technology, new academic and industrial research and many inventions and innovations in the field of vibration analysis and control

Francisco Beltrán Carbajal

Energy Department

Azcapotzalco Unit of the Autonomous Metropolitan University

Mexico

1

Adaptive Tuned Vibration Absorbers:

Design Principles, Concepts and

is defined as its undamped natural frequency with its base (point of attachment) blocked The TVA can be used in two distinct ways, resulting in different optimal tuning criteria and design requirements (von Flotow et al., 1994):

a It can be tuned to suppress (dampen) the modal contribution from a specific troublesome

natural frequency Ωs of the host structure over a wide band of excitation frequencies

b It can be tuned to suppress (neutralise) the vibration at a specific troublesome excitation

frequency ω, in which case it acts like a notch filter

When used for application (a), the TVA referred to as a “tuned mass damper” (TMD) ωa is optimally tuned to a value slightly lower than that of the targeted mode Ω and an optimal slevel of damping needs to be designed into the absorber When used for application (b), the TVA is referred to as a “tuned vibration neutraliser” (TVN) (Brennan, 1997, Kidner & Brennan, 1999) or “undamped TVA” The optimal tuning condition is in this case is ωa= ω

and the TVN suppresses the vibration over a very narrow bandwidth centred at the tuned frequency Total suppression of the vibration at this frequency is achieved when there is no damping in the TVN

Deviation from the tuned condition (mistuning) degrades the performance of either variant

of the TVA (von Flotow et al., 1994) and it can be shown that a mistuned vibration neutraliser could actually increase the vibration of its host structure (Brennan, 1997) To avoid mistuning, smart or adaptive tunable vibration absorbers (ATVAs) have been developed Such devices are capable of retuning themselves in real time Adaptive technology is especially important in the case of the TVN since the low damping requirement in the spring element can raise the host structure vibration to dangerous levels

Vibration Analysis and Control – New Trends and Developments

2

in the mistuned condition In this case, mistuning can occur either due to a drift in the forcing frequency or due to a drift in tuned frequency caused by environmental factors (e.g temperature change) Hence, a TVN needs to be adaptive to be practically useful

At the heart of an ATVA is a means for adjusting the tuned frequency ωa in real time This is frequently done through the variation of the effective mechanical stiffness of the ATVA, although other means are possible Whatever the retuning method used, the device should be tunable over an adequate range of frequencies, and the adjustment should be rapid and with minimum power requirement The device must also be cheap and easy to manufacture To maximise vibration attenuation, the retuning mechanism should add as little as possible to the redundant mass of the device and, in the case of the neutraliser, have a low structural damping (Brennan, 1997) The technical challenge is to design an adaptive device with such attributes

This chapter continues with a quantitative illustration of the basic design principles of both variants of the TVA It will then present a comprehensive review of the various design concepts that have been presented for the ATVA, including the latest innovations contributed by the author This section will cover the use of piezoelectric actuators, shape-memory alloys and servo-actuators within the smart structure of the ATVA Control algorithms and their implementation through MATLAB® with SIMULINK® will also be discussed

2 Basic design principles of TVA

With reference to Fig 1a, the above-defined frequency ωa coincides exactly with the lowest anti-resonance frequency of the attachment point receptance frequency response function (FRF) of the undamped “free-body” TVA structure, r AA( )ω =Y F A , where Y and F are A

complex amplitudes of y and the interface force A f t , for harmonic vibration at circular ( )

frequency ω It is for this reason that, for the TVN, the condition ωa= defines optimal ω

tuning For excitation frequencies ω below the first non-zero resonance frequency ωm of

,

a a a eff

k =ω m and a damping element In the case of a TMD, where damping is deliberately designed into the device, it is preferable to represent it by viscous damper of frequency-independent coefficient c a In the case of a TVN, where the damping is an unwanted inherent feature of the spring element, it is best represented by a structural damping mechanism of loss factor

a

η , for which the equivalent viscous damping coefficient is k a aη ω The method for deriving the equivalent two-degree-freedom is detailed in Section 4.1

2.1 Tuned mass damper

The purpose of the TMD is to dampen a particular resonance peak of the FRF r AP( )ω

connecting the response at A to an external force f t p( ) applied to the host structure at some arbitrary point P It is useful for applications where the excitation has a broad frequency spectrum containing the targeted mode The damping in the original host structure (i.e the

Adaptive Tuned Vibration Absorbers: Design Principles, Concepts and Physical Implementation 3 structure prior to the addition of the TMD) is commonly assumed to be negligible relative to

that introduced by the TMD Suppose the TMD is targeted at the sth mode of the original host structure Let Ωs be the frequency of this mode and ψA( )s denote the value of the corresponding mass-normalised mode-shape at the degree of freedom being targeted (e.g the vertical displacement at A in Fig 1) Then, from standard modal theory (Ewins, 1984), the contribution of the targeted mode to the dynamics of the original host structure at the targeted degree of freedom can be represented as the simple mass-spring system of mass

to account for the addition of the redundant absorber mass to the host structure The harmonic analysis of the systems in Figs 2(a,b) (i.e analysis with f P=Re{F Pejωt}) then gives a modal approximation of r AP( )ω , denoted by ( )s ( )

AP

r ω , which is accurate for frequencies ωin the vicinity of Ωs

Fig 1 Generic TVA

Fig 2 Dynamic modal model of the host structure without/with TMD for frequencies ω in the vicinity of Ωs

( )s A

( ) ( )s f P( )t

A

s P

ψ ψ

a

eff a

A

s P

ψ ψ

(a) Host structure (b) Host structure with TMD