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Research Papers

Efficiency of a Fixed Displacement Pump With Flow Control Using an Inlet Metering Valve

[+] Author and Article Information
Hasan H. Ali

Mechanical and Aerospace Engineering,
University of Missouri-Columbia,
Columbia, MO 65211
e-mail: hha2mf@mail.missouri.edu

Julie K. Wisch

Mechanical and Aerospace Engineering,
University of Missouri-Columbia,
Columbia, MO 65211
e-mail: wisch.j.k@gmail.com

Roger C. Fales

Mechanical and Aerospace Engineering,
University of Missouri-Columbia,
Columbia, MO 65211
e-mail: falesr@missouri.edu

Noah D. Manring

Mechanical and Aerospace Engineering,
University of Missouri-Columbia,
Columbia, MO 65211
e-mail: ManringN@missouri.edu

1Corresponding author.

Contributed by the Dynamic Systems Division of ASME for publication in the JOURNAL OF DYNAMIC SYSTEMS, MEASUREMENT,AND CONTROL. Manuscript received April 17, 2017; final manuscript received September 25, 2018; published online October 29, 2018. Editor: Joseph Beaman.

J. Dyn. Sys., Meas., Control 141(3), 031001 (Oct 29, 2018) (14 pages) Paper No: DS-17-1198; doi: 10.1115/1.4041606 History: Received April 17, 2017; Revised September 25, 2018

Axial piston pumps with variable volumetric displacement are often used to control flow and pressure in hydraulic systems. The displacement control mechanism in these pumps occupies significant space and accounts for significant cost in the pump design. Fixed displacement pumps have lower cost and a more compact design but suffer from a significant energy consumption disadvantage due to the need to control flow and pressure by throttling flow and bypassing unused flow to pressures below the discharge pressure. An inlet metering valve-controlled pump marks a recent development in pumping technology for hydraulic systems. In this design, an inlet metering valve restricts inlet flow reducing inlet pressure so that the specific volume of the fluid is increased as it enters a fixed displacement pump. By altering the specific volume of the working fluid, the inlet metering valve permits precise control over the pump discharge flow. This paper presents a theoretical model for inlet metered pump efficiency. The work considers additional sources of energy loss unique to the inlet metering system. Experimental results associated with inlet metered pump efficiency are presented. A comparison of the theoretical model and the experimental results is also included. It is determined that the current efficiency model accurately predicts efficiencies determined using experimental data.

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References

Wilson, W. E. , 1950, Positive Displacement Pumps and Fluid Motors, Pitman Publishing Corporation, New York.
Thoma, J. , 1969, “ Mathematical Models and Effective Performance of Hydrostatic Machines and Transmissions,” Hydraulic Pneumatic Power, 23, pp. 642–651.
Zeiger, G. , and Aker, A. , and 1985, “ Torque on the Swashplate of an Axial Piston Pump,” ASME J. Dyn. Syst., Meas., Control, 107(3), pp. 220–226. [CrossRef]
Lin, S. J. , Aker, A. , and Zeiger, G. , 1985, “ The Effect of Oil Entrapment in an Axial Piston Pump,” ASME J. Dyn. Syst., Meas., Control, 107(4), pp. 246–251. [CrossRef]
Manring, N. D. , and Yihong, Z. , 2001, “ The Improved Volumetric-Efficiency of an Axial-Piston Pump Utilizing a Trapped-Volume Design,” ASME J. Dyn. Syst., Meas., Control, 123(3), pp. 479–487. [CrossRef]
Shi, Z. , Parker, G. , and Granstrom, J. , 2010, “ Kinematic Analysis of a Swash-Plate Controlled Variable Displacement Axial-Piston Pump With a Conical Barrel Assembly,” ASME J. Dyn. Syst., Meas., Control, 132(1), p. 011002.
Manring, N. D. , Mehta, V. S. , Nelson, B. E. , Graf, K. J. , and Kuehn, J. L. , 2014, “ Scaling the Speed Limitations for Axial-Piston Swash-Plate Type Hydrostatic Machines,” ASME J. Dyn. Syst., Meas., Control, 136(3), p. 031004. [CrossRef]
Manring, N. D. , 2016, “ Mapping the Efficiency for a Hydrostatic Transmission,” ASME J. Dyn. Syst., Meas., Control, 138(3), p. 031004. [CrossRef]
Tomlinson, S. P. , and Burrows, C. R. , 1992, “ Achieving a Variable Flow Supply by Controlled Unloading of a Fixed-Displacement Pump,” ASME J. Dyn. Syst., Meas., Control, 114(1), pp. 166–171. [CrossRef]
Zhang, H. , 2014, “ Cavitation Effect to the Hydraulic Piston Pump Flow Pulsation,” Appl. Mech. Mater., 599-601, pp. 230–236. [CrossRef]
Eisenberg, P. , 1950, “ On the Mechanism and Prevention of Cavitation,” Navy Department, Washington, DC, David Taylor Model Basin Report 712.
Vacca, A. , Klop, R. , and Ivantysynova, M. , 2010, “ A Numerical Approach for the Evaluation of the Effects of Air Release and Vapour Cavitation on Effective Flow Rate of Axial Piston Machines,” Int. J. Fluid Power, 11(1), pp. 33–45.
Dular, M. , and Coutier-Delgosha, O. , 2009, “ Numerical Modelling of Cavitation Erosion,” Int. J. Numer. Methods Fluids, 61(12), pp. 1388–1410.
Wang, Y. , Daruta, G. , Poirierb, T. , Stellac, J. , Liaoa, H. , and Planche, M.-P. , 2017, “ Ultrasonic Cavitation Erosion of as-Sprayed and Laser-Remelted Yttria Stabilized Zirconia Coatings,” J. Eur. Ceram. Soc., 37(11), pp. 3623–3630. [CrossRef]
Bordeasu, I. , Popoviciu, M. O. , Salcianu1, L. C. , Ghera, C. , Micu, L. M. , Badarau, R. , Iosif, A. , Pirvulescu, L. D. , and Podoleanu, C. E. , 2017, “ A New Concept for Stainless Steels Ranking Upon the Resistance to Cavitation Erosion,” IOP Conf. Ser.: Mater. Sci. Eng., 163, p. 012002.
Gibson, I. H. , 1994, “ Variable-Speed Drives as Flow Control Elements,” ISA Trans., 33(2), pp. 165–169.
Çalışkan, H. , Balkan, T. , and Platin, B. E. , 2009, “ Hydraulic Position Control System With Variable Speed Pump,” ASME Paper No. DSCC2009-2693.
Brown, F. T. , 1984, “ The Use of Fluid Inertia for D/A Conversion in Hydraulic PWM Circuits With Seating Valves—Part I: Concepts,” ASME Paper No. 84-WA/DSC-4.
Brown, F. T. , Tentarelli, S. C. , and Ramachandran, S. , 1988, “ A Hydraulic Rotary Switched-Inertasice Servo-Transformer,” Trans. ASME, 110(2), pp. 144–150.
Pan, M. , Johnston, N. , and Hillis, A. , 2013, “ Active Control of Pressure Pulsation in a Switched Inertance Hydraulic System,” Proc.-Inst. Mech. Eng., 227(7), pp. 610–620.
Merrill, K. J. , Breidi, F. Y. , and Lumkes, J. , 2013, “ Simulation Based Design and Optimization of Digital Pump/Motors,” ASME Paper No. FPMC2013-4475.
Breidi, F. , Helmus, T. , and Lumkes, J. , 2015, “ High Efficiency Digital Pump/Motor,” Fluid Power Innovation & Research Conference (FPIRC15), Chicago, IL, Oct. 14–16.
Wisch, J. K. , Manring, N. D. , and Fales, R. C. , 2017, “ Dynamic Characteristics of a Pressure-Compensated Inlet-Metered Pump,” ASME J. Dyn. Syst., Meas., Control, 139(6), p. 064502. [CrossRef]
Wisch, J. K. , 2016, “ Dynamic and Efficiency Characteristics of an Inlet Metering Valve Controlled Fixed Displacement Pump,” Ph.D. dissertation, University of Missouri, Columbia, MO. https://mospace.umsystem.edu/xmlui/handle/10355/60423

Figures

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Fig. 1

Inlet metering valve and fixed displacement single piston pump system (Note: the test results in this paper are given for a realistic setup where there are three pistons rather than just one with a double-lobe cam as shown so that there are six piston strokes per revolution)

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Fig. 3

Piston volume and pressure

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Fig. 2

Valve opening area versus voltage

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Fig. 12

Nondimensional torque versus nondimensional valve opening for 25 MPa discharge pressure and 2 MPa inlet pressure where the solid lines represent the model due to Eq. (31) and the markers represents the data.

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Fig. 13

Nondimensional Torque versus nondimensional valve opening for 2500 rpm discharge pressure and 2 MPa inlet pressure where the solid lines represent the model and the markers represent the data

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Fig. 5

Test rig experimental setup

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Fig. 6

Valve input voltage versus time

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Fig. 7

Flow and pressure measurements: (a) Instantaneous inlet flow with return flow and discharge flow versus time (note that the inlet flow includes 2LPM return flow due to a feature built into the pump) and (b) discharge pressure versus time

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Fig. 8

Instantaneous torque versus time

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Fig. 9

Nondimensional pump discharge flow versus nondimensional valve opening for 2 MPa inlet pressure and 25 MPa discharge pressure where the solid lines represent the model using Eq. (29) and the markers represent the data.

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Fig. 10

Nondimensional pump discharge flow versus nondimensional valve opening for 2 MPa inlet pressure and 2500 rpm speed where the solid lines represent the model and the markers represent the data

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Fig. 11

Nondimensional pump discharge flow versus nondimensional valve opening for 25 MPa discharge pressure and 1000 rpm speed where the solid lines represent the model and the markers represent the data

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Fig. 14

Overall pump efficiency versus valve nondimensional area for an inlet pressure of 2 MPa, pump shaft speed of 2500 rpm, and listed discharge pressures and the markers represent the data

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Fig. 15

Overall pump efficiency versus valve nondimensional area for 2 MPa inlet pressure and 25 MPa discharge pressure and the markers represent the data

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Fig. 16

Overall pump efficiency versus nondimensional valve opening for 25 MPa discharge pressure and 1000 rpm and the markers represent the data

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