Parametric control of structural responses using an optimal passive tuned mass damper under stationary Gaussian white noise excitations

doi:10.1007/s11709-012-0170-x

Front Struc Civil Eng

2012, Vol. 6

Issue (3) : 267-280 https://doi.org/10.1007/s11709-012-0170-x

RESEARCH ARTICLE

Parametric control of structural responses using an optimal passive tuned mass damper under stationary Gaussian white noise excitations

Min-Ho CHEY¹(

), Jae-Ung KIM²

1. School of Architecture & Art, Yanbian University of Science & Technology, Yanji 133000, China; 2. Department of Architectural Engineering, Dong-A University, Pusan, R.O. Korea

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Abstract

In this study, the structural control strategy utilizing a passive tuned mass damper (TMD) system as a seismic damping device is outlined, highlighting the parametric optimization approach for displacement and acceleration control. The theory of stationary random processes and complex frequency response functions are explained and adopted. For the vibration control of an undamped structure, the optimal parameters of a TMD, such as the optimal tuning frequency and optimal damping ratio, to stationary Gaussian white noise acceleration are investigated by using a parametric optimization procedure. For damped structures, a numerical searching technique is used to obtain the optimal parameters of the TMD, and then the explicit formulae for these optimal parameters are derived through a sequence of curve-fitting schemes. Using these specified optimal parameters, several different controlled responses are examined, and then the displacement and acceleration based control effectiveness indices of the TMD are examined from the view point of RMS values. From the viewpoint of the RMS values of displacement and acceleration, the optimal TMDs adopted in this study shows clear performance improvements for the simplified model examined, and this means that the effective optimization of the TMD has a good potential as a customized target response-based structural strategy.

Keywords tuned mass damper parametric optimization passive control white noise earthquake excitation

Corresponding Author(s): CHEY Min-Ho,Email:hnhdad@daum.net

Issue Date: 05 September 2012

Cite this article:

Min-Ho CHEY,Jae-Ung KIM. Parametric control of structural responses using an optimal passive tuned mass damper under stationary Gaussian white noise excitations[J]. Front Struc Civil Eng, 2012, 6(3): 267-280.

URL:

https://academic.hep.com.cn/fsce/EN/10.1007/s11709-012-0170-x
https://academic.hep.com.cn/fsce/EN/Y2012/V6/I3/267

Fig.1 Schematic of main system and TMD for structural control

Fig.2 Relative displacement (a) and acceleration (b) complex frequency response functions vs. frequency ( = 0.02)

Fig.3 Optimal frequency tuning and TMD damping ratios for displacement and acceleration control

Tab.1 Optimal TMD parameters, RMS and normalized RMS responses (displacement)

Tab.2 Optimal TMD parameters, RMS and normalized RMS responses (acceleration)

Fig.4 Influence of on optimal frequency tuning ratio (a) and TMD damping ratio (b) (displacement)

Fig.5 Influence of on optimal TMD stiffness (a) and TMD damping coefficient (b) (displacement)

Fig.6 Influence of on optimal freguency tuning ratio (a) and TMD damping ratio (b) (acceleration)

Fig.7 Influence of on optimal TMD stiffness (a) and TMD damping coefficient (b) (acceleration)

Fig.8 RMS (a), normalized RMS (b) and contour of normalized RMS (c) displacements of the main system vs. frequency tuning and TMD damping ratios ( = 0.02, = 0.05)

Fig.9 Influence of on RMS (a) and normalized RMS (b) displacements of the main system

Fig.10 RMS (a), normalized RMS (b) and contour of normalized RMS (c) displacements of the TMD vs. frequency tuning and TMD damping ratios ( = 0.02, = 0.05)

Fig.11 Influence of on RMS (a) and normalized RMS (b) displacements of the TMD

Fig.12 RMS (a), normalized RMS (b) and contour of normalized RMS (c) accelerations of the main system vs. frequency tuning and TMD damping ratios ( = 0.02, ξ = 0.05)

Fig.13 Influence of on RMS (a) and normalized RMS (b) accelerations of the main system

Fig.14 RMS (a), normalized RMS (b) and contour of normalized RMS (c) accelerations of the TMD vs. frequency tuning and TMD damping ratios ( = 0.02, = 0.05)

Fig.15 Influence of on RMS (a) and normalized RMS (b) accelerations of the TMD

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