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Research Papers

Scaling the Speed Limitations for Axial-Piston Swash-Plate Type Hydrostatic Machines

[+] Author and Article Information
Noah D. Manring

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

Viral S. Mehta

Caterpillar Inc.,
Peoria, IL 61656
e-mail: Mehta_Viral@cat.com

Bryan E. Nelson

Caterpillar Inc.,
Peoria, IL 61656
e-mail: Nelson_Bryan_E@cat.com

Kevin J. Graf

Caterpillar Inc.,
Peoria, IL 61656
e-mail: Graf_Kevin_J@cat.com

Jeff L. Kuehn

Caterpillar Inc.,
Peoria, IL 61656
e-mail: Kuehn_Jeff_L@cat.com

1Corresponding author.

Contributed by the Dynamic Systems Division of ASME for publication in the JOURNAL OF DYNAMIC SYSTEMS, MEASUREMENT, AND CONTROL. Manuscript received December 11, 2012; final manuscript received November 18, 2013; published online January 29, 2014. Assoc. Editor: Nariman Sepehri.

J. Dyn. Sys., Meas., Control 136(3), 031004 (Jan 29, 2014) (8 pages) Paper No: DS-12-1417; doi: 10.1115/1.4026129 History: Received December 11, 2012; Revised November 18, 2013

This paper proposes a scaling law for estimating the speed limitations for a family of axial-piston swash-plate type hydrostatic machines. The speed limitations for this machine are considered from three mechanical perspectives: (1) cylinder-block tipping, (2) cylinder-block filling, and (3) slipper-tipping. As shown in the results of this research, each speed limitation is scaled by the inverse of the cube root of the volumetric displacement for the new machine. In other words, small machines are shown to have a higher speed capacity than larger machines. By scaling a baseline machine using the scale laws that are presented here, a new machine may be produced that obeys a simple rule related only to the volumetric displacement of the new machine. Serendipitously, and perhaps most usefully, all three speed limitations obey the same rule! The speed limitations that are derived in this research are compared to existing industry data of currently scaled products and it is shown that the proposed scale laws correspond well with this data.

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References

Manring, N. D., 2013, Fluid Power Pumps and Motors: Analysis, Design and Control, McGraw-Hill, Inc., New York.
Manring, N. D., 2000, “Tipping the Cylinder Block of an Axial-Piston Swash-Plate Type Hydrostatic Machine,” ASME J. Dyn. Syst., Meas., Control, 122, pp. 216–221. [CrossRef]
Manring, N. D., 1998, “Slipper Tipping Within an Axial-Piston Swash-Plate Type Hydrostatic Pump,” ASME International Mechanical Engineering Congress and Exposition. Anaheim CA, FPST 169-175.
Berthold, H., and Pecnik, I., 1990, “Axial Piston Pump,” US Patent No. 4,934,253.
Schaffner, L. D., Geise, L. R., and Wilcox, J. W., 1996, “Axial Piston Pump,” US Patent No. 5,538,401.
Seljastad, G. A., 1999, “Retainer Mechanism for an Axial Piston Machine,” US Patent No. 5,862,704.
Langenfeld, T. J., 2006, “Cylinder Block Brake for a Hydrostatic Drive Apparatus,” US Patent No. 7,134,276.
Johnson, A. W., Woodshank, K. J., Betz, M. A., and Otto, R. L., 2002, Reduced Oil Volume Piston Assembly for a Hydrostatic Unit,” US Patent No. 6,338,293.
Bahandare, S., and Allada, V., 2009, Scalable Product Family Design: Case Study of Axial Piston Pumps,” Int. J. Prod. Res., 47(3), pp. 585–620. [CrossRef]
Negoita, G. C., Mare, J. C., Budinger, M., and Vasiliu, N., 2012, Scaling-Laws Based Hydraulic Pumps Parameter Estimation,” U.P.B. Sci. Bull., Series D, 74(2), pp. 199–208. Available at: http://scientificbulletin.upb.ro/rev_docs_arhiva/fullcc4_892385.pdf
Damtew, F. A., 1998, “The Design of Piston Bore Springs for Over-Whelming Inertial Effects Within Axial-Piston Swash-Plate Type Hydrostatic Machines,” M.S. thesis, University of Missouri, Columbia, MO.
Norton, R. L., 2000, Machine Design: An Integrated Approach, Prentice-Hall, Inc. Upper Saddle River, NJ.
Hutchings, I. M., 1992, Tribology: Friction and Wear of Engineering Materials, CRC Press. Anne Arbor, MI.

Figures

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Fig. 1

Cross-sectional view of the axial-piston, swash-plate type machine

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Fig. 2

Partial free-body-diagram of the cylinder block

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Fig. 3

A schematic of the piston chamber filling with fluid

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Fig. 4

Partial free-body-diagrams for a piston and a slipper located at top-dead-center and operating under low pressure (a condition in which slipper tipping is most likely to occur)

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Fig. 5

Vickers aerospace machinery

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Fig. 6

Rexroth open-circuit machinery

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Fig. 7

Linde open-circuit machinery

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