Research Papers

Modeling, Control, and Validation of Electrohydrostatic Shock Absorbers

[+] Author and Article Information
Renato Galluzzi

Department of Mechanical and
Aerospace Engineering,
Politecnico di Torino,
Corso Duca degli Abruzzi, 24,
Turin 10129, Italy
e-mail: renato.galluzzi@polito.it

Andrea Tonoli

Associate Professor
Department of Mechanical and
Aerospace Engineering,
Politecnico di Torino,
Corso Duca degli Abruzzi, 24,
Turin 10129, Italy
e-mail: andrea.tonoli@polito.it

Nicola Amati

Assistant Professor
Department of Mechanical and
Aerospace Engineering,
Politecnico di Torino,
Corso Duca degli Abruzzi, 24,
Turin 10129, Italy
e-mail: nicola.amati@polito.it

1Corresponding author.

Contributed by the Technical Committee on Vibration and Sound of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received April 15, 2014; final manuscript received August 11, 2014; published online November 12, 2014. Assoc. Editor: Mohammed Daqaq.

J. Vib. Acoust 137(1), 011012 (Feb 01, 2015) (7 pages) Paper No: VIB-14-1138; doi: 10.1115/1.4028310 History: Received April 15, 2014; Revised August 11, 2014; Online November 12, 2014

The implementation of variable damping systems to increase the adaptability of mechanical structures to their working environment has been gaining increasing scientific interest, and numerous attempts have been devoted to address vibration control by means of active and semi-active devices. Although research results seem promising in some cases, the proposed solutions are often not able to fulfill requirements in terms of compactness and simplicity on one hand, and dynamic performance on the other. In this context, the present paper discusses the modeling and control of an electrohydrostatic actuation (EHA) system for its implementation as a damping device. A model of the device is proposed and analyzed for design purposes. Subsequently, a damping control strategy is presented. Finally, a case study introduces and validates an EHA prototype for helicopter rotor blade lead–lag damping.

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Fig. 1

Model of the EHA system for linear motion

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Fig. 2

Mechanical equivalent model of the EHA system for linear motion

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Fig. 3

Conceptual representation of the magnitude frequency response of Gv(s) and GF(s) in the three indicated limit conditions: (a) ωe>>ωeq (b) ωe≪ωeq, (c) |ωe-ωeq|  <  2ke/meq

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Fig. 4

Block diagram of the EHA device control strategy

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Fig. 5

Adaptive lead-lag damping requirements. High (dashed) and low (solid) damping responses are compared.

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Fig. 6

Prototype CAD exploded view. (1) Pump side cover, (2) pump journal bearings, (3) pump gears, (4) damper inlet plug (×2), (5) pressure sensor (× 2), (6) electric motor, (7) drain interface, (8) EHA manifold, (9) motor side cover, (10) electric wirings connector, (11) Hall sensors and magnetic disk, (12) damper case, and (13) damper fluid inlets.

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Fig. 7

Prototype installed on the test bench. (1) Load cell fixed to the test bench frame, (2) EHA pressure sensors, (3) cooling fan and vent, (4) driving ram, (5) damper case, and (6) EHA device

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Fig. 8

Force-velocity response of the damper at (a) f = 1.26 Hz and (b) f = 4.75 Hz. Data obtained with open-circuited motor windings (square), short-circuited motor windings (triangle), and active control (circle) are compared to the high-damping (dashed) and low-damping (solid) curves. Simulation data are presented in solid markers while experimental data are presented in hollow markers.



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