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Research Papers

Research on the Dynamics and Variable Characteristics of a Double-Swash-Plate Hydraulic Axial Piston Pump With Port Valves

[+] Author and Article Information
Pengcheng Qian

School of Mechanical Science and Engineering,
Huazhong University of Science and Technology,
Luoyu Road 1037,
Wuhan 430074, China
e-mail: pengchengqian@hust.edu.cn

Zengqi Ji

School of Mechanical Science and Engineering,
Huazhong University of Science and Technology,
Luoyu Road 1037,
Wuhan 430074, China
e-mail: jizengqi@hust.edu.cn

Bihai Zhu

School of Mechanical Science and Engineering,
Huazhong University of Science and Technology,
Luoyu Road 1037,
Wuhan 430074, China
e-mail: zhubihai@hust.edu.cn

1Corresponding author.

Contributed by the Dynamic Systems Division of ASME for publication in the JOURNAL OF DYNAMIC SYSTEMS, MEASUREMENT,AND CONTROL. Manuscript received August 15, 2017; final manuscript received July 26, 2018; published online September 10, 2018. Assoc. Editor: Yang Shi.

J. Dyn. Sys., Meas., Control 141(1), 011006 (Sep 10, 2018) (18 pages) Paper No: DS-17-1411; doi: 10.1115/1.4041012 History: Received August 15, 2017; Revised July 26, 2018

Axial piston pumps with port valves are widely used in applications that require high pressure and high power. In the present research, a new type of double-swash-plate hydraulic axial piston pump (DSPHAPP) with port valves is presented. The structure and working principle of the pump are discussed, and the balance characteristics of the pump are analyzed. A mathematical model of the pump flow distribution mechanism considering the leakage is established, based on which the effects of centrifugal forces acting on the port valves, working pressure, and rotational speed on the flow distribution characteristics are studied. A new method of varying the displacement of the pump that changes the phase relation of the two swash plates is proposed, and the principle and regulating characteristics of the variable method are studied. A detailed analysis of the forces and moments acting on the cylinder and the bearing reaction forces is presented. Finally, the relationship between volumetric efficiency and working pressure, and rotational speed and variable angle, is presented. It is revealed through an analysis that the working principle of the pump is feasible, and that the variable method can meet the requirements of varying the displacement of the pump. The characteristics of static balance and dynamic balance of the double-swashplate pump have the advantage of reducing vibration and noise. The research results also show that the reasonable matching of the working pressure and rotational speed can increase the pump's working performance to its optimum level.

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References

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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. [CrossRef]
Edge, K. A. , and Brett, P. N. , 1990, “ The Pumping Dynamics of a Positive Displacement Pump Employing Self-Acting Valves,” ASME J. Dyn. Syst. Meas. Control, 112(4), pp. 748–754. [CrossRef]
Liu, Y. S. , Wu, D. F. , Long, L. , and Cao, S. P. , 2009, “ Research on the Port Valve of a Water Hydraulic Axial Pump,” Proc. Inst. Mech. Eng., Part E, 223(3), pp. 155–166. [CrossRef]
The Oilgear Company, 2010, “ Bulletin 46005-A,” The Oilgear Company, Milwaukee, WI, accessed July 24, 2018, https://oilgear.com/engineered-products/pumps/high-pressure-check-valve/
Zhu, B. , Wu, X. , Niu, Z. , He, X. , and Liu, Y. , 2013, “ Experimental Research on the Water Hydraulic Axial Piston Canned Motor Pump With Double Swash Plate,” J. Mech. Eng., 49(2), pp. 146–150. [CrossRef]
Achten, P. A. J. , Van den Brink, T. L. , Paardenkooper, T. , Platzer, T. , Potma, H. W. , Schellekens, M. P. A. , and Vael, G. E. M. , 2003, “ Design and Testing of an Axial Piston Pump Based on the Floating Cup Principle,” The Eighth Scandinavian International Conference on Fluid Power (SICFP), Tampere, Finland, May 7–9, pp. 805–820.
Achten, P. A. J. , Van den Brink, T. L. , and Potma, J. W. , 2005, “ Design of a Variable Displacement Floating Cup Pump,” The Ninth Scandinavian International Conference on Fluid Power (SICFP), Linköping, Sweden, June 1–3.
Manring, N. D. , Mehta, V. S. , Raab, F. J. , and Graf, K. J. , 2007, “ The Shaft Torque of a Tandem Axial-Piston Pump,” ASME J. Dyn. Syst. Meas. Control, 129(3), pp. 367–371. [CrossRef]
Yang, X. , Gong, G. , Yang, H. , Jia, L. , and Zhou, J. , 2017, “ An Investigation in Performance of a Variable-Speed-Displacement Pump-Controlled Motor System,” IEEE/ASME Trans. Mechatronics, 22(2), pp. 647–656. [CrossRef]
Kaliafetis, P. , and Costopoulos, T. H. , 1995, “ Modelling and Simulation of an Axial Piston Variable Displacement Pump With Pressure Control,” Mech. Mach. Theory, 30(4), pp. 599–612. [CrossRef]
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Figures

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Fig. 1

The structure diagram of DSPHAPP

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Fig. 2

The balance analysis diagram of DSPHAPP's structure: (a) component forces diagram and (b) resultant forces diagram

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Fig. 3

The diagram of piston motion analysis

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Fig. 4

The simplified physical model of poppet valves: (a) inlet valve and (b) outlet valve

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Fig. 5

The diagram of fluid leakage

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Fig. 6

Influences of precompression of the inlet valve spring under the condition of centrifugal force: (a) pressure in piston chamber, (b) displacement of port valves, and (c) instantaneous flow rate of port valves

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Fig. 7

Influences of centrifugal forces acting on the outlet valves: (a) pressure in piston chamber, (b) displacement of port valves, and (c) instantaneous flow rate of port valves

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Fig. 8

Influences of working pressure: (a) pressure in piston chamber, (b) displacement of port valves, and (c) instantaneous flow rate of port valves

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Fig. 9

Influences of rotational speed: (a) pressure in piston chamber, (b) displacement of port valves, and (c) instantaneous flow rate of port valves

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Fig. 10

The variable principle diagram of DSPHAPP

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Fig. 11

The variable principle calculation diagram of DSPHAPP

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Fig. 12

The curves of the relationship between the piston velocity of both sides and the rotation angle of pump

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Fig. 13

The balance analysis diagram of DSPHAPP's cylinder block assembly when it works as a variable displacement pump: (a) component forces diagram and (b) resultant forces diagram

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Fig. 14

Diagram of synthesize force F1, F2 acting on the cylinder block from the left and right swash plates when z = 8: (a) F1 varies with the variable angle θ, (b) F2 varies with the variable angle θ, (c) F1 varies with the rotation angle φ when θ = 0 deg, and (d) F2 varies with the rotation angle φ when θ = 0 deg

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Fig. 15

Diagram of additional moment M1, M2 from the left and right swash plates when z = 8: (a) M1 varies with the variable angle θ and (b) M2 varies with the variable angle θ

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Fig. 16

Diagram of bearing support forces FM, FN when z = 8: (a) FM varies with the variable angle θ, (b) FN varies with the variable angle θ, (c) FM varies with the rotation angle φ when θ = 0 deg, and (d) FN varies with the rotation angle φ when θ = 0 deg

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Fig. 17

Diagram of synthesize force F1, F2 acting on the cylinder block from the left and right swash plates when z = 9: (a) F1 varies with the variable angle θ, (b) F2 varies with the variable angle θ, (c) F1 varies with the rotation angle φ when θ = 0 deg, and (d) F2 varies with the rotation angle φ when θ = 0 deg

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Fig. 18

Diagram of additional moment M1, M2 from the left and right swash plates when z = 9: (a) M1 varies with the variable angle θ and (b) M2 varies with the variable angle θ

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Fig. 19

Diagram of bearing support forces FM, FN when z = 9: (a) FM varies with the variable angle θ, (b) FN varies with the variable angle θ, (c) FM varies with the rotation angle φ when θ = 0 deg, and (d) FN varies with the rotation angle φ when θ = 0 deg

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Fig. 20

The relationship of the displacement and volumetric efficiency of the pump between the rotational speed and variable angle when the working pressure is 5 MPa: (a) displacement of the pump and (b) volumetric efficiency of the pump

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Fig. 21

The relationship of the displacement and volumetric efficiency of the pump between the rotational speed and variable angle when the working pressure is 10 MPa: (a) displacement of the pump and (b) volumetric efficiency of the pump

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Fig. 22

The relationship of the displacement and volumetric efficiency of the pump between the rotational speed and variable angle when the working pressure is 20 MPa: (a) displacement of the pump and (b) volumetric efficiency of the pump

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Fig. 23

The relationship of the displacement and volumetric efficiency of the pump between the working pressure and variable angle when the rotational speed is 300 rpm: (a) displacement of the pump and (b) volumetric efficiency of the pump

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Fig. 24

The relationship of the displacement and volumetric efficiency of the pump between the working pressure and variable angle when the rotational speed is 900 rpm: (a) displacement of the pump and (b) volumetric efficiency of the pump

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Fig. 25

The relationship of the displacement and volumetric efficiency of the pump between the working pressure and variable angle when the rotational speed is 1500 rpm: (a) displacement of the pump and (b) volumetric efficiency of the pump

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Fig. 26

The matching diagram of the rotational speed and the working pressure

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Fig. 27

The diagram of leakage of eccentric annular clearance between the piston and the cylinder bore

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