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Research Papers

Active Control of Fluid Pressure Pulsation in Hydraulic Pipe System by Bilateral-Overflow of Piezoelectric Direct-Drive Slide Valve

[+] Author and Article Information
Guan Changbin

School of Automation Science
and Electrical Engineering,
Beihang University,
Beijing 100191, China
Beijing Institute of Control Engineering,
Beijing 100080, China

Jiao Zongxia

School of Automation Science
and Electrical Engineering,
Beihang University,
Beijing 100191, China
Science and Technology on Aircraft
Control Laboratory,
Beihang University,
Beijing 100191, China
e-mail: zxjiao@buaa.edu.cn

Wu Shuai, Shang Yaoxing

School of Automation Science
and Electrical Engineering,
Beihang University,
Beijing 100191, China
Science and Technology on Aircraft
Control Laboratory,
Beihang University,
Beijing 100191, China

Zheng Fanggang

Aviation Key Laboratory of Science and Technology on Aero
Electromechanical System Integration,
Nanjing 211106, China

Contributed by the Dynamic Systems Division of ASME for publication in the JOURNAL OF DYNAMIC SYSTEMS, MEASUREMENT, AND CONTROL. Manuscript received March 11, 2013; final manuscript received December 8, 2013; published online March 11, 2014. Assoc. Editor: Shankar Coimbatore Subramanian.

J. Dyn. Sys., Meas., Control 136(3), 031025 (Mar 11, 2014) (20 pages) Paper No: DS-13-1113; doi: 10.1115/1.4026343 History: Received March 11, 2013; Revised December 08, 2013

In this paper, a novel active control of fluid pressure pulsation (ACFPP) is proposed, which meets the need of the high-pressure and high-speed hydraulic pipe system. A piezoelectric direct-drive slide valve (PDDSV) is designed and used as the active vibration absorber. Two ports of the PDDSV both connect to a bypass near the pump outlet and the other two ports both connect to the oil tank. By the bilateral-overflow through the shoulder of the PDDSV, the overflow wave generated in one cycle of spool motion can cancel two cycles of flow ripple. An adaptive-optimum control method based on the rotate-vector optimization method (RVOM) is adopted to adjust the control parameters in order to minimize the amplitude of the pressure pulsation. The biggest advantage of the proposed ACFPP is that it can eliminate the pressure pulsation when PDDSV only works at half of the pressure pulsation's frequency. The simulation and experimentation both verify the proposed ACFPP. By the proposed ACFPP, the suppression for the single-frequency component and dual-frequency components of the pressure pulsation have been both realized.

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References

Figures

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Fig. 1

Schematic of the ACFPP proposed by Jiao

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Fig. 2

Schematic of one spool movement cycle

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Fig. 3

Flow relationship during Jiao's ACFPP

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Fig. 4

Schematic of the ACFPP by bilateral-overflow of the PDDSV

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Fig. 5

Principle of bilateral-overflow by the PDDSV: (a) left half cycle and (b) right half cycle

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Fig. 6

Frequency corresponding relationship between the spool displacement and flow ripple

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Fig. 7

Schematic of the hydraulic pipe system

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Fig. 8

Schematic of axial-piston pump's valve plate and piston chamber: (a) valve plate and (b) single-piston chamber (TDC: Top dead center; BDC: Bottom dead center)

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Fig. 9

Graphical representation of the variation of Akd

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Fig. 10

The characteristic line algorithm

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Fig. 11

Simulated flow ripple of the piston pump: (a) flow ripple in time domain and (b) frequency spectrum of flow ripple

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Fig. 12

Simulated pressure pulsation of hydraulic pipe system: (a) pressure pulsation in time domain and (b) frequency spectrum of pressure pulsation

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Fig. 13

Measured pressure pulsation of the hydraulic pipe system: (a) pressure pulsation in time domain and (b) frequency spectrum of pressure pulsation

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Fig. 14

Schematic of the PDDSV

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Fig. 15

Photograph of the PDDSV

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Fig. 16

Spool-driving mechanism with the power amplifier

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Fig. 17

Mechanical model of the spool-driving mechanism

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Fig. 18

Comparison of the amplitude characteristics between the power amplifier and the second-order system

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Fig. 19

Dynamic block diagram of the PDDSV with power amplifier

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Fig. 20

Amplitude–frequency characteristic of the spool displacement

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Fig. 21

No-load flow of the PDDSV

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Fig. 22

Structural diagram of the adaptive-optimum control for single-frequency component

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Fig. 23

The step-by-step adaptive-optimum control for dual-frequency components

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Fig. 24

The convergence procedure of the RVOM

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Fig. 25

Flowchart of the adaptive-optimum control for single-frequency component

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Fig. 26

Simulation block for the proposed ACFPP

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Fig. 27

Pressure during ACFPP for fundamental frequency component in simulation

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Fig. 28

FFT of the simulated pressure pulsation before and after ACFPP for fundamental frequency component: (a) before control and (b) after control

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Fig. 29

Simulated spool displacement in ACFPP for fundamental frequency component: (a) spool displacement and (b) frequency spectrum of xs

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Fig. 30

Simulated pressure during ACFPP for dual-frequency components

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Fig. 31

Harmonic amplitudes of the pressure pulsation in step 2 of the simulation

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Fig. 32

Simulated spool displacement in ACFPP for dual-frequency components: (a) spool displacement and (b) frequency spectrum of xs in step 2

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Fig. 33

Test rig for the proposed ACFPP

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Fig. 34

Measured pressure during ACFPP for fundamental frequency component

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Fig. 35

FFT of the measured pressure before and after ACFPP for fundamental frequency component: (a) before control and (b) after control

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Fig. 36

The control parameters during the ACFPP for fundamental frequency component: (a) amplitude and (b) phase

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Fig. 37

Measured spool displacement during the ACFPP for fundamental frequency component: (a) spool displacement and (b) frequency distribution

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Fig. 38

Waveform corresponding relationship between pressure pulsation and spool displacement in ACFPP for fundamental frequency component

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Fig. 39

Measured pressure during ACFPP for second harmonic component

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Fig. 40

FFT of the measured pressure before and after ACFPP for second harmonic component: (a) before control and (b) after control

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Fig. 41

The control parameters during the ACFPP for second harmonic component: (a) amplitude and (b) phase

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Fig. 42

Measured spool displacement during the ACFPP for second harmonic component: (a) spool displacement and (b) frequency distribution

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Fig. 43

Waveform corresponding relationship between pressure pulsation and spool displacement in ACFPP for second harmonic component

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Fig. 44

Measured pressure during ACFPP for dual-frequency components

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Fig. 45

FFT of the measured pressure pulsation during the ACFPP for dual-frequency components: (a) before control, (b) step 1, and (c) step 2

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Fig. 46

Measured spool displacement during the ACFPP for dual-frequency components: (a) spool displacement and (b) spool displacement when step 2 gets steady state

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Fig. 47

Frequency distribution of spool displacement in ACFPP for dual-frequency components: (a) step 1 and (b) step 2

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Fig. 48

Convergence procedure of the control parameters in step 1: (a) amplitude and (b) phase

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Fig. 49

Convergence procedure of the control parameters in step 2: (a) amplitude and (b) phase

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Fig. 50

Vector rotating scheme

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