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TECHNICAL PAPERS

On Using Unstable Electrohydraulic Valves for Control

[+] Author and Article Information
Kailash Krishnaswamy, Perry Y. Li

Department of Mechanical Engineering, University of Minnesota, 111 Church St. SE, Minneapolis, MN 55455e-mail: {kk,pli}@me.umn.edu

J. Dyn. Sys., Meas., Control 124(1), 183-190 (Feb 09, 2001) (8 pages) doi:10.1115/1.1433801 History: Received February 09, 2001
Copyright © 2002 by ASME
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References

Hebert E. Merritt, 1967, Hydraulic Control Systems, Wiley, NY.
D. McCloy and H. R. Martin, 1973, The Control of Fluid Power, Wiley, NY.
J. F. Blackburn, G. Reethof, and L. L. Shearer 1960, Fluid Power Control, MIT Press, Cambridge, MA.
Lee,  S-Y., and Blackburn,  J. F., 1952, “Contributions to hydraulic control 2-transient flow forces and valve instability,” ASME Machine Design Division, Vol.74, pp. 1013–1016.
M. Borghi, M. Milani, and R. Paoluzzi, 1998, “Transient flow force estimation on the pilot stage of a hydraulic valve,” Proceedings of the ASME-IMECE FPST-Fluid Power Systems & Tech., Vol. 5 , pp. 157–162.
D. Wang, R. Dolid, M. Donath, and J. Albright, 1995, “Development and verification of a two-stage flow control servovalve model,” Proceedings of the ASME-IMECE FPST-Fluid Power Systems & Tech., Vol. 2 , pp. 121–129.
Funk,  J. E., Wood,  D. J., and Chao,  S. P., 1972, “The transient response of orifices and very short lines,” ASME J. Basic Eng., 94, No. 2, pp. 483–491.
Martin,  D. J., and Burrows,  C. R., 1976, “The dynamic characteristics of an electrohydraulic servovalve,” ASME J. Dyn. Syst., Meas., Control, 98, No. 4, pp. 395–406.
Won,  M., and Hedrick,  J. K., 1996, “Multiple-surface sliding control of a class of uncertain nonlinear systems,” Int. J. Control, 64, pp. 693–706.

Figures

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A single-stage critical-centered spool valve connected to a double-ended actuator
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Valve configuration and transient flow forces when dQ/dt>0 and Q>0. (a) Unstable transient flow force occurs when flow is metered into the valve chamber; (b) stable transient flow force occurs when flow is metered out of the valve chamber. Figures (a) and (b) correspond to the upper and lower chambers in the spool configuration in Fig. 1
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Actuator-valve setup considered in the simulation studies
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Optimal step responses for the stable (L=0.0254 m (+1 in)) and unstable configuration (L=−0.0254 m (−1 in)) with upper actuator constraint ū of 222.4 N (50 lb) (top) and 889.6 N (200 lb) (bottom)
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Optimal control effort for stable and unstable valve configurations
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Phase Plots, xν v/s ẋν
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Power Consumed by the valves
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Damping length versus rise times
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Sinusoidal tracking at 10 Hz
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Sinusoidal tracking at 140 Hz
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Effort and power needed to track a 10 Hz sinusoidal trajectory
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Effort and power needed to track a 140 Hz sinusoidal trajectory
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Maximum positive power consumed by the stable and unstable valves at various frequencies
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Maximum negative power consumed by the stable and unstable valves at various frequencies

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