KR20140140184A - Piston slipper for hydraulic pump - Google Patents

Piston slipper for hydraulic pump Download PDF

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Publication number
KR20140140184A
KR20140140184A KR1020130060457A KR20130060457A KR20140140184A KR 20140140184 A KR20140140184 A KR 20140140184A KR 1020130060457 A KR1020130060457 A KR 1020130060457A KR 20130060457 A KR20130060457 A KR 20130060457A KR 20140140184 A KR20140140184 A KR 20140140184A
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KR
South Korea
Prior art keywords
piston
hydraulic pump
length
slipper
outer frame
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Application number
KR1020130060457A
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Korean (ko)
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KR101984316B1 (en
Inventor
오석주
Original Assignee
두산인프라코어 주식회사
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Priority to KR1020130060457A priority Critical patent/KR101984316B1/en
Publication of KR20140140184A publication Critical patent/KR20140140184A/en
Application granted granted Critical
Publication of KR101984316B1 publication Critical patent/KR101984316B1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

A piston slipper for a hydraulic pump according to the present invention includes a main body 10 coupled to a piston 2, a cylindrical body 10 having a longitudinal section formed in a circular shape and having a top surface 30 contacting the swash plate, In a piston slipper (1) for a hydraulic pump including an eccentric portion (20), the upper end surface (30) of the sliding portion (20) has a hole (31) A recess portion (40) for forming a flow path of the hydraulic fluid introduced from the hole (31); And an outer frame 50 formed along an outer circumferential direction of the recess portion 42 and having a plurality of oblique grooves 60. Each of the oblique grooves 60 is formed in the outer frame portion An inlet port 61 located on the inner circumferential surface of the first chamber 50; And an outlet 62 positioned on an outer circumferential surface of the outer portion 50. The length of the inlet 61 is smaller than the length of the outlet 62. [

Description

[0001] Piston slipper for hydraulic pump [0002]

The present invention relates to a piston slipper for a hydraulic pump, and more particularly, to a piston slipper for a hydraulic pump, which comprises a plurality of sloped grooves formed along the circumferential direction of a sliding portion constituting a sliding portion, A piston slipper for a hydraulic pump capable of preventing the piston slipper from being damaged by improving the friction performance and lubrication performance of the piston slipper even when the hydraulic pump is started or at a low speed due to the fluid dynamic pressure effect generated further. .

Generally, a hydraulic pump is a driving device that converts a piston into mechanical energy called rotation of a drive shaft by reciprocating the piston using fluid energy called hydraulic pressure, and is widely used for heavy equipment such as construction equipment requiring a large power with excellent output density .

1 is a perspective view showing a state where a piston slipper for a conventional hydraulic pump is fastened to a piston. As shown in Fig. 1, a conventional piston slipper 1 for a hydraulic pump includes a body portion 10 and a sliding portion 20.

One end of the main body 10 is coupled to the piston 2. The sliding portion 20 is located at the upper portion of the main body portion 10 and has a longitudinal section formed in a circular shape. The upper end surface 30 of the sliding portion 20 is brought into contact with the swash plate so that the upper end surface 30 of the sliding portion 20 is rotated on the swash plate as the piston 2 is driven.

The upper end surface 30 of the sliding portion 20 rotates in contact with the swash plate portion 20 so that the sliding portion 20 of the piston slipper 20 reduces the wear due to the friction between the swash plate 20 and the upper surface of the sliding portion 20, Only the characteristics of the bearing are formed.

That is, the upper end surface 30 of the sliding portion 20 is processed so as to have a shape parallel to the contact surface of the swash plate so that the operating oil can be uniformly discharged to the outside of the upper surface 30 of the sliding portion 20.

However, the conventional piston slipper for a hydraulic pump having only the characteristics of a hydrostatic bearing is disadvantageous in that excessive wear is applied to the upper end surface 30 of the piston slipper sliding portion 20 when the hydraulic pump is stopped or started, or when the hydraulic pump is operated at a low speed .

In addition, the piston slipper of the conventional hydraulic pump has a problem that the upper end surface of the piston slipper is damaged by abrasion on the upper surface, the replacement cost for replacing the upper end surface is increased, and the productivity is decreased.

Further, the conventional piston slippers for a hydraulic pump have problems in that the overall durability of the hydraulic pressure decreases and the mechanical efficiency of the hydraulic pump decreases as the friction increases.

Korean Patent Publication No. 10-2003-0074936

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and it is an object of the present invention to provide a slope groove formed in an outer frame portion along a circumferential direction of a sliding portion, And the longitudinal section of the inclined groove is formed to have a downward inclination angle so that an oil film is formed on the upper surface of the sliding section at the time of starting the hydraulic pump, at the time of low-speed driving or at the time of stopping, and by the fluid dynamic pressure effect by the oil film, To improve the friction performance and the lubrication performance of the piston slippers, thereby increasing the efficiency of the hydraulic pump.

In order to accomplish the object of the present invention, a piston slipper for a hydraulic pump according to the present invention comprises a body portion coupled to a piston, a hydraulic portion including a sliding portion, A piston slipper for a pump, wherein a top surface of the sliding portion has a hole for introducing hydraulic fluid to a center point thereof; A recess portion for forming a flow passage of the hydraulic fluid introduced from the hole; And an outer circumferential portion formed along an outer circumferential direction of the recess portion and having a plurality of oblique grooves, wherein each of the oblique grooves has an inlet located on an inner circumferential surface of the outer circumferential portion; And an outlet located on an outer circumferential surface of the outer casing, wherein the length of the inlet is smaller than the length of the outlet.

Further, in another preferred embodiment of the slipper for a hydraulic pump according to the present invention, one end of the inlet and one end of the outlet may be located on the same baseline.

In another preferred embodiment of the slipper for a hydraulic pump according to the present invention, each of the inclined grooves is formed so as to have a predetermined downward inclination angle from the other end of the inlet toward the one end of the inlet with respect to the tangent to the reference line .

Further, in another preferred embodiment of the slipper for a hydraulic pump according to the present invention, each of the inclined grooves may be formed such that the reference line is spaced apart by a predetermined angle along a circumferential direction of the outer frame.

In another preferred embodiment of the slipper for a hydraulic pump according to the present invention, the length of the inlet and the length of the outlet, that is, the length of the inlet port divided by the length of the outlet port is 0.1 to 0.5, The length of the outlet can be formed.

In another preferred embodiment of the slipper for a hydraulic pump according to the present invention, the downward inclination angle of the inclined groove may be formed to be 0.2 degree to 1 degree.

In another preferred embodiment of the slipper for a hydraulic pump according to the present invention, the angle at which the reference line is spaced along the circumferential direction of the outer frame may be 45 to 72 degrees.

The piston slipper for a hydraulic pump according to the present invention has an effect of forming an oil film at the time of starting, stopping, or at a low speed of the hydraulic pump, thereby generating fluid dynamic pressure effect and reducing wear of the piston slipper.

In addition, the piston slipper for a hydraulic pump according to the present invention has an effect of reducing wear due to friction of a piston slipper by fluid dynamic pressure effect, and finally preventing breakage of the piston slipper.

Further, the piston slipper for a hydraulic pump according to the present invention minimizes the damage of the piston slipper and reduces the cost and time for replacing the piston slipper, thereby reducing the production cost and improving the productivity.

In addition, the piston slipper for a hydraulic pump according to the present invention improves the friction performance and lubrication performance of the piston slipper, thereby improving the durability of the hydraulic pump and minimizing the friction loss, thereby increasing the mechanical efficiency of the hydraulic pump.

1 is a perspective view showing a state where a piston slipper for a conventional hydraulic pump is fastened to a piston.
2 is a perspective view of a piston slipper for a hydraulic pump according to a preferred embodiment of the present invention.
3 is a plan view of a piston slipper for a hydraulic pump according to a preferred embodiment of the present invention.
4 is a side view of a piston slipper for a hydraulic pump according to a preferred embodiment of the present invention.
5 is an enlarged view of an inclined groove of a piston slipper for a hydraulic pump according to a preferred embodiment of the present invention.
Fig. 6 is a conceptual diagram for explaining the downward inclination angle of the oblique groove shown in Fig. 4. Fig.

Preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the drawings, like reference numerals are used to refer to like elements throughout.

2 shows a perspective view of a piston slipper 1 for a hydraulic pump according to a preferred embodiment of the present invention. 3 is a plan view of a piston slipper 1 for a hydraulic pump according to a preferred embodiment of the present invention. 4 shows a side view of a piston slipper 1 for a hydraulic pump according to a preferred embodiment of the present invention. 5 shows an enlarged view of an inclined groove 40 of a piston slipper 1 for a hydraulic pump according to a preferred embodiment of the present invention. Fig. 6 is a conceptual diagram for explaining the downward tilt angle [alpha] of the tilt groove 40 shown in Fig.

2 to 6, a piston slipper 1 for a hydraulic pump according to a preferred embodiment of the present invention will be described. A piston slipper 1 for a hydraulic pump according to a preferred embodiment of the present invention includes a main body 10 and a sliding portion 20. The upper surface 30 of the sliding portion 20 includes a hole 31, A recess 32, and an outer frame 33 having a plurality of oblique grooves 40.

One end of the main body 10 is coupled to the piston 2. According to an embodiment of the present invention, one end of the piston 2 is provided with a ball joint, and one end of the main body 10 is connected to a groove (not shown) which can receive the ball joint of the piston 2, And one end of the main body 10 is coupled to the piston 2 by ball joint engagement or the like.

The sliding portion 20 is located at the upper portion of the main body portion 10 and has a longitudinal section formed in a circular shape. The upper end surface 30 of the sliding portion 20 is brought into contact with the swash plate so that the upper end surface 30 of the sliding portion 20 is rotated on the swash plate as the piston 2 is driven.

The hole 31 is formed at a central point of the upper end surface 30 of the sliding portion 20 and functions to introduce hydraulic fluid flowing in the hydraulic pump into the sliding portion 20. [

The recess portion (32) forms a flow passage of the hydraulic fluid introduced from the hole (31). According to a preferred embodiment of the present invention, the recessed portion 32 is formed on the upper surface 30 of the sliding portion 20 in consideration of a virtual concentric circle with the hole 31 as a center point, A plurality of convex portions spaced apart at regular intervals along the circumferential direction of the imaginary concentric circles having different radii and formed in the form of a plurality of intersecting convex portions and concave portions, The hydraulic fluid flowing through the holes 31 flows through the holes 31 and is discharged to the outside of the sliding portion 20. [

The outer frame portion 33 is formed along the outer circumferential direction of the recess portion 32. In addition, the outer portion 33 has a plurality of inclined grooves 40 on the upper surface thereof.

Each of the inclined grooves 40 includes an inlet port 41 located on the inner circumferential surface of the outer frame portion 33 and an outlet port 42 located on the outer circumferential surface of the outer circumferential portion 33. The length L I of the inlet port 41 is formed to be smaller than the length L O of the outlet port 42.

According to another preferred embodiment of the present invention, one end of the inlet 41 and one end of the outlet 42 are located on the same baseline O.

3 and 5, the inclined groove 40 is formed with reference to the reference line O which is a virtual line of the radius eccentricity of the upper end surface 30 of the sliding portion 20 with the hole 31 as a center point The length L I of the inlet port 41 is formed in a trapezoidal shape smaller than the length L O of the outlet port 42.

According to another preferred embodiment of the invention, the ratio of the length (L I) to the length (L O) of the outlet 42 of the inlet 41 of the oblique groove (40) (L I / L O) is in the range of 0.1 to 0.5.

Table 1 shows the relationship between the length L I of the inlet port 41 and the length L of the outlet port 42 in the state where the downward inclination angle α of the oblique groove is 0.5 ° and six oblique grooves 40 are formed at regular intervals. O ) ratio (L I / L O ) of the friction torque.

(L I / L O ) of the length (L I ) of the inlet and the length (L O ) of the outlet and the friction torque> Ratio (L I / L O) of the length (L I) to the length (L O) of the outlet from the inlet Friction torque (Nm) Conventional piston slippers - 14.4 Example 1 0.1 13.9 Example 2 0.3 7.1 Example 3 0.5 10.2 Comparative Example 1 One 14.6

The operating oil flowing through the hole 31 moves along the recess portion 32 and this working oil flows into the inlet 41 of the inclined groove 40 and flows through the outlet 42 to the outside of the piston slipper 1 .

As can be seen from Table 1, when the ratio (L I / L O ) of the length L I of the inlet 41 to the length L O of the outlet 42 is less than 0.1, the inclined grooves 40 Is too small to form an oil film like the conventional piston slipper, and finally the fluid dynamic pressure effect can not be further generated, thereby increasing the friction torque.

When the ratio L I / L 0 of the length L I of the inlet port 41 to the length L O of the outlet port 42 is 1 or more, the flow rate of the hydraulic fluid discharged to the outside of the piston slipper 1 So that the oil film can not be formed and finally the hydrodynamic pressure effect can not be further generated, thereby increasing the friction torque.

The ratio L I / L 0 of the length L I of the inlet port 41 to the length L O of the outlet port 42 is formed to be 0.1 to 0.5 and most preferably to be 0.3 .

5 and 6, according to another preferred embodiment of the present invention, the inclined groove 40 of the piston slipper 1 is inclined with respect to the tangent line P with respect to the reference line O, Is formed to have a predetermined downward inclination angle (?) From the other end toward the one end direction of the inlet (41).

In other words, the inclined groove 40 has a vertical cross-section from the other end of the inlet 41 (or the other end of the outlet 42), which is not adjacent to the reference line O with respect to the tangential line P with respect to the reference line O, (Or one end of the outflow port 42) of the inlet port 41 located on the upstream side of the outlet port 41. The downstream inclination angle?

According to another preferred embodiment of the present invention, the downward inclination angle alpha of the inclined groove 40 is formed to be 0.2 degree to 1 degree.

In Table 2, six slope grooves 40 are formed at regular intervals, and the ratio (L I / L O ) of the length L I of the inlet 41 to the length L O of the outlet 42 is 0.3 Is the experimental data of the friction torque value according to the downward inclination angle alpha.

≪ Downward inclination angle (?) And friction torque of the inclined groove > The downward tilt angle (?) Friction torque (Nm) Conventional piston slippers - 15.55 Comparative Example 1 0.1 degree 15.01 Example 1 0.2 degree 10.22 Example 2 0.5 degree 7.51 Example 3 1 degree 11.15 Comparative Example 2 1.5 degrees 14.67

As can be seen from the above Table 2, when the downward inclination angle? Of the oblique groove 40 is less than 0.2 degrees, there is almost no fluid dynamic pressure effect. As a result, no pressure is formed in the oil film, .

When the downward inclination angle? Of the inclined groove 40 is larger than one degree, the abrasion torque is not reduced due to the cavitation phenomenon in which bubbles are generated due to a sudden pressure change in the film.

Therefore, the downward inclination angle? Of the inclined groove 40 is formed to be 0.2 degree to 1 degree, most preferably 0.5 degree.

The slope groove 40 of the piston slipper 1 according to another preferred embodiment of the present invention is formed such that the reference line O is spaced apart by a predetermined angle C along the circumferential direction of the outer frame portion 33 . That is, the inclined grooves 40 are formed on the outer frame portion 33 so as to be spaced apart by a predetermined angle C.

According to another preferred embodiment of the present invention, the angle C at which the reference line O is spaced along the circumferential direction of the outer frame portion 33 is 45 degrees to 72 degrees. That is, the angle C at which the reference line O is spaced apart along the circumferential direction of the outer frame portion 33 is selected to be 45 degrees or more and 72 degrees or less. According to an example of the preferred embodiment of the present invention, if the angle C at which the reference line O is spaced along the circumferential direction of the outer frame portion 33 is 45 degrees, the slope groove 40 is formed in the outer frame portion 33 at 45 Six inclined grooves 40 are formed at an angle of 60 degrees in the outer frame 33 when the angle is 60 degrees and six inclined grooves 40 are formed in the outer frame 33 when the angle is 72 degrees. Five angles are formed at an angle.

Table 3 shows the ratio (L I / L 0 ) of the length L I of the inlet 41 to the length L O of the outlet 42 by 0.3 and the ratio The experimental data obtained by measuring the friction torque for about 5 minutes at an angle (C) at which the reference line (O) is spaced along the circumferential direction of the outer frame (33) at a downward tilt angle (α) of 0.5 degrees and a rated running speed of 2600 rpm to be.

≪ Angle C and friction torque at which the reference line O is spaced along the circumferential direction of the outer frame portion 33 & An angle C at which the reference line O is spaced along the circumferential direction of the outer frame portion 33, Friction torque (Nm) Conventional piston slippers - 14.4 Example 1 72 11.9 Example 2 60 7.1 Example 3 45 9.0

 As can be seen from Table 3, when the angle C at which the reference line O is spaced along the circumferential direction of the outer frame portion 33 is larger than 72 degrees, the pressure of the oil film is hardly formed and the inclined grooves 40 The friction torque of the conventional piston slipper does not differ from that of the conventional piston slipper.

If the angle C at which the reference line O is spaced along the circumferential direction of the outer frame portion 33 is less than 45 degrees, the hydraulic fluid is excessively discharged to the outside of the sliding portion 20, The friction torque does not decrease and a large amount of cost is consumed in machining.

The angle C at which the reference line O is spaced apart along the circumferential direction of the outer frame 33 is selected to be 45 degrees or more and 72 degrees or less, 60 < / RTI >

As described above, the piston slipper 1 according to the preferred embodiments of the present invention has the plurality of inclined grooves 40 in which the outer frame portion 33 constituting the sliding portion 20 is formed along the circumferential direction The inclined groove 40 is formed so as to have a downward inclination angle alpha and is formed so as to extend along the circumference direction of the outer frame portion 33 along the reference line O The slope grooves are formed so as to have an angle (C) that is spaced apart from each other by a predetermined distance. Thus, unlike a conventional piston slipper for a hydraulic pump, the friction torque generated at the time of starting, And can be reduced by at least 15% to about 50%.

Further, the piston slipper 1 according to the preferred embodiments of the present invention can reduce the friction torque and thereby prevent the piston slippers from being broken, thereby improving the durability of the hydraulic pump and increasing the mechanical efficiency of the hydraulic pump .

The present invention is not limited to the modifications shown in the drawings and the embodiments described above, but may be extended to other embodiments falling within the scope of the appended claims.

1: piston slipper, 2: piston,
10: main body portion, 20: sliding portion,
30: upper surface, 31: hole,
32: recess portion, 33: outer frame portion,
40: Slope groove.

Claims (7)

A piston slipper for a hydraulic pump, comprising: a main body coupled to a piston; and a sliding portion having a longitudinal section formed in a circular shape at an upper portion of the main body and having a top surface contacting the swash plate,
The upper end of the sliding portion
A hole for allowing the hydraulic oil to flow into the center point;
A recess portion for forming a flow passage of the hydraulic fluid introduced from the hole; And
And an outer frame formed along an outer circumferential direction of the recess portion and having a plurality of oblique grooves,
Each of the inclined grooves
An inlet located on an inner circumferential surface of the outer frame; And
And an outlet disposed on an outer circumferential surface of the outer casing,
And the length of the inlet port is smaller than the length of the outlet port.
The method according to claim 1,
Wherein one end of the inlet port and one end of the outlet port are located on the same reference line. 3. The method of claim 2,
Each of the inclined grooves
And a predetermined downward inclination angle from the other end of the inlet port toward the one end of the inlet port with respect to the tangent to the reference line.
3. The method of claim 2,
Each of the inclined grooves
And the reference line is formed to be spaced apart by a predetermined angle along a circumferential direction of the outer frame.
3. The method of claim 2,
Wherein the ratio of the length of the inlet to the length of the outlet is 0.1 to 0.5.
The method of claim 3,
Wherein the downward inclination angle is in the range of 0.2 to 1 degrees.
5. The method of claim 4,
Wherein the angle is 45 to 72 degrees.
KR1020130060457A 2013-05-28 2013-05-28 Piston slipper for hydraulic pump KR101984316B1 (en)

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KR101984316B1 KR101984316B1 (en) 2019-09-03

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20160128116A (en) 2015-04-28 2016-11-07 유원산업(주) Piston shoe of hydraulic pump
KR20180107842A (en) * 2017-03-23 2018-10-04 두산인프라코어 주식회사 Piston shoe and shoe plate for hydrauric piston pump

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1150950A (en) * 1997-08-06 1999-02-23 Kayaba Ind Co Ltd Axial piston pump or motor
KR20030074936A (en) 2002-03-14 2003-09-22 한국기계연구원 Piston shoe of hydraulic motor and pump
CN101012817A (en) * 2007-02-01 2007-08-08 华中科技大学 Plunger piston slippery boots assembly
CN101196182A (en) * 2006-12-04 2008-06-11 丹福斯有限公司 Water presss
JP5184320B2 (en) * 2008-12-04 2013-04-17 日立建機株式会社 Swash plate type hydraulic rotating machine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1150950A (en) * 1997-08-06 1999-02-23 Kayaba Ind Co Ltd Axial piston pump or motor
KR20030074936A (en) 2002-03-14 2003-09-22 한국기계연구원 Piston shoe of hydraulic motor and pump
CN101196182A (en) * 2006-12-04 2008-06-11 丹福斯有限公司 Water presss
CN101012817A (en) * 2007-02-01 2007-08-08 华中科技大学 Plunger piston slippery boots assembly
JP5184320B2 (en) * 2008-12-04 2013-04-17 日立建機株式会社 Swash plate type hydraulic rotating machine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20160128116A (en) 2015-04-28 2016-11-07 유원산업(주) Piston shoe of hydraulic pump
KR20180107842A (en) * 2017-03-23 2018-10-04 두산인프라코어 주식회사 Piston shoe and shoe plate for hydrauric piston pump

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