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Research Papers

Pressure, Flow, Force, and Torque Between the Barrel and Port Plate in an Axial Piston Pump

[+] Author and Article Information
J. M. Bergada

Fluid Mechanics Department, ETSEIAT UPC, Colon 11, Terrassa 08222, Spainbergada@mf.upc.edu

J. Watton

Cardiff School of Engineering, Cardiff University, Queen’s Buildings, P.O. Box 925, Cardiff, CF24 0YF Wales, UKwattonj@cardiff.ac.uk

S. Kumar

Fluid Mechanics Department, ETSEIAT UPC, Colon 11, Terrassa 08222, Spainsushil@iitg.ac.in

J. Dyn. Sys., Meas., Control 130(1), 011011 (Jan 08, 2008) (16 pages) doi:10.1115/1.2807183 History: Received February 21, 2006; Revised June 08, 2007; Published January 08, 2008

This paper analyzes the pressure distribution, leakage, force, and torque between the barrel and the port plate of an axial piston pump. A detailed set of new equations is developed, which takes into account important parameters such as tilt, clearance and rotational speed, and timing groove. The pressure distribution is derived for different operating conditions, together with a complementary numerical analysis of the original differential equations, specifically written for this application and used to validate the theoretical solutions. An excellent agreement between the two approaches is shown, allowing an explicit analytical insight into barrel/port plate operating characteristics, including consideration of cavitation. The overall mean force and torques over the barrel are evaluated and show that the torque over the XX axis is much smaller than the torque over the YY axis, as deduced from other nonexplicit simulation approaches. A detailed dynamic analysis is then studied, and it is shown that the torque fluctuation over the YY axis is typically 8% of the torque total magnitude. Of particular novelty is the prediction of a double peak in each torque fluctuation resulting from the more exact modeling of the piston/port plate/timing groove pressure distribution characteristic during motion. A comparison between the temporal torque fluctuation pattern and another work shows a good qualitative agreement. Experimental and analytical results for the present study demonstrate that barrel dynamics do contain a component primarily directed by the torque dynamics.

Copyright © 2008 by American Society of Mechanical Engineers
Topics: Torque , Pressure , Leakage , Pistons , Pumps
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References

Figures

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Figure 1

Barrel/port plate configuration

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Figure 2

Theoretical pressure distribution along the main and small grooves for a set of different parameters. Maximum tilt.

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Figure 3

Pressure distribution along the main and small grooves for a set of different parameters. Maximum tilt, numerical and analytical solutions.

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Figure 4

Leakage between the barrel and plate for different central clearances and for maximum α at each clearance. The internal pressure is 25MPa. (a) Main groove. (b) Timing groove.

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Figure 5

Mean force over the pump barrel for a set of pressure differentials, numerical solution, and theory

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Figure 6

Mxx torque due to the main and timing groove effects, maximum tilt, 25MPa. (a) Main groove. (b) Timing groove.

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Figure 7

Myy torque due to the (a) main and (b) timing groove effects, maximum tilt, 25MPa.

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Figure 8

Temporal changes in the torques generated due to cylinder pressure effects during motion, 1440rpm, 18MPa, and 25MPa. (a) XX axis, 25MPa. (b) XX axis, 18MPa. (c) YY axis, 25MPa. (d) YY axis, 18MPa.

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Figure 9

Dynamic torque variation about each axis, 1440rpm, 18MPa, and 25MPa, h0=4μm, α=0.006104deg (a) YY axis, 25MPa. (b) YY axis, 18MPa. (c) XX axis, 25MPa. (d) XX axis, 18MPa.

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Figure 10

Qualitative comparison of torques acting on the barrel and on the swash plate. (a) Present study, analytical, 25MPa. (b) Ivantysynova (23), computer model.

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Figure 11

Scheme of the test rig, showing the transducer’s position

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Figure 12

Barrel dynamic gap measurements obtained from the position transducer located over the YY axis. Outlet pressure of 18MPa.

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Figure 13

Computed gap position dynamics, XX axis. Frictional torque 3Nm. (a) Damping coefficient, 25Nm∕rads−1. (b) Damping coefficient 30Nm∕rads−1.

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Figure 14

Experimental position dynamics, XX axis, 18MPa

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Figure 15

Experimental barrel position dynamics XX axis, measured by Yamaguchi (6)

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