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Research Papers

Modeling and Characterization of Rotary Electrohydrostatic Actuators

[+] 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

Nicola Amati

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

1Corresponding author.

Contributed by the Technical Committee on Vibration and Sound of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received May 30, 2015; final manuscript received September 30, 2015; published online November 19, 2015. Assoc. Editor: Patrick S. Keogh.

J. Vib. Acoust 138(1), 011016 (Nov 19, 2015) (8 pages) Paper No: VIB-15-1193; doi: 10.1115/1.4031756 History: Received May 30, 2015; Revised September 30, 2015

Electrohydrostatic actuators are increasingly finding applications in different fields due to their numerous advantages with respect to electromechanical and conventional hydraulic systems. To understand their behavior, potentialities, limitations, and design aspects, the present paper deals with the modeling of such devices. The discussed phenomena are experimentally validated through the stationary and dynamic characterization tests of a rotary electrohydrostatic prototype. Results emphasize the role of mechanical and hydraulic dissipative effects and the fluid bulk modulus.

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References

Figures

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Fig. 1

Rotary EHA constituted by (1) input motor, (2) temperature sensor, (3) input pump, (4) accumulator, (5) protection, circuit valve array, (6) output pump, (7) pressure sensors, (8) pipelines, and (9) output motor

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Fig. 3

Rotary EHA model scheme

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Fig. 4

Mechanical equivalent model of the hydraulic circuit present in the rotary EHA

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Fig. 5

Effects of the fluid internal damping variation on the frequency response magnitude of Gτ. The behaviors where cf = 1 × 109 N s/m5 (solid line), cf = 1 × 1011 N s/m5 (dashed line), and cf =1 × 1013  N s/m5 (dashed-dotted line) are shown; cin = cout = 0 in all cases.

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Fig. 6

Effects of the input and output damping variation on the frequency response magnitude of Gτ. The behaviors where cin = 1 × 10−3 N·m s/rad (solid line), cin = 0.1 N·m s/rad (dashed line), and cin = 1 N·m s/rad (dashed-dotted line) are shown; cin = cout and cf = 0 in all cases.

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Fig. 7

Frequency response magnitude of GY for cin = 1 × 10−3 N·m s/rad, cf = 1 × 1011 N s/m5 (solid line); cin = 0.1 N·m s/rad, cf = 1 × 1011 N s/m5 (dashed line); and cin = 1 × 10−3 N·m s/rad, cf = 1 × 1012 N s/m5 (dashed-dotted line); cin = cout in all cases

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Fig. 8

Stationary damping response of the rotary EHA at preload pressures of 15 bar (dot), 35 bar (square), and 50 bar (triangle). Experimental results were linearly fitted (solid line) to obtain the parameters listed in Table 3.

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Fig. 9

Effects of the preload pressure on the rotary EHA startup torque. Experimental results (dot) were linearly fitted (solid line).

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Fig. 10

Frequency response magnitude of Gτ at a preload pressure of 15 bar and temperature of 45 °C. Experimental data (dot) are compared to response 1 (dashed line), response 2 (dashed-dotted line), and response 3 (solid line). See Table 4 for information regarding the parameters of each simulation.

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Fig. 11

Frequency response magnitude of Gτ at a preload pressure of 50 bar and temperature of 65 °C. Experimental data (dot) are compared to response 1 (dashed line), response 2 (dashed-dotted line), and response 3 (solid line). See Table 4 for information regarding the parameters of each simulation.

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