KR101984316B1 - Piston slipper for hydraulic pump - Google Patents

Piston slipper for hydraulic pump Download PDF

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Publication number
KR101984316B1
KR101984316B1 KR1020130060457A KR20130060457A KR101984316B1 KR 101984316 B1 KR101984316 B1 KR 101984316B1 KR 1020130060457 A KR1020130060457 A KR 1020130060457A KR 20130060457 A KR20130060457 A KR 20130060457A KR 101984316 B1 KR101984316 B1 KR 101984316B1
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KR
South Korea
Prior art keywords
piston
hydraulic pump
slipper
inlet
length
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KR1020130060457A
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Korean (ko)
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KR20140140184A (en
Inventor
오석주
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두산인프라코어 주식회사
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Priority to KR1020130060457A priority Critical patent/KR101984316B1/en
Publication of KR20140140184A publication Critical patent/KR20140140184A/en
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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

Piston slippers for the hydraulic pump according to the present invention is located on the upper portion of the main body portion 10 and the main body portion 10 coupled to the piston (2) and the longitudinal section is formed in a circular shape, the upper surface 30 is wet In the piston slipper (1) for the hydraulic pump including the eastern portion (20), the upper surface 30 of the sliding part (20) comprises a hole (31) for the introduction of the hydraulic fluid to the center point; A recess 40 for forming a flow passage of the working oil introduced from the hole 31; And an outer portion 50 formed along the outer circumferential direction of the recess portion 42 and having a plurality of inclined grooves 60, wherein each of the inclined grooves 60 is formed in the outer portion ( An inlet 61 located on the inner circumferential surface of 50; And an outlet 62 positioned on an outer circumferential surface of the outer shell 50, wherein the length of the inlet 61 is smaller than the length of the outlet 62.

Description

Piston slipper for hydraulic pump

The present invention relates to a piston slipper for a hydraulic pump, and more particularly, for a hydraulic pump that can prevent the piston slipper from being damaged by improving the frictional performance and the lubricating performance of the piston slipper even when the hydraulic pump is started or at a low speed. Relates to piston slippers.

In general, the hydraulic pump is a driving device that converts the piston into mechanical energy such as rotation of the drive shaft by reciprocating the piston using fluid energy called hydraulic pressure, and is widely used in heavy equipment such as construction equipment requiring high power due to its excellent power density. .

Figure 1 shows a perspective view of a conventional piston slipper for the hydraulic pump is fastened to the piston. As shown in FIG. 1, a conventional piston slipper 1 for a hydraulic pump includes a main body 10 and a sliding part 20.

One end of the body portion 10 is coupled to the piston 2. The sliding part 20 is located above the main body 10 and has a longitudinal cross section. The upper surface 30 of the sliding portion 20 is in contact with a swash plate, so that the upper surface 30 of the sliding portion 20 rotates on the swash plate according to the driving of the piston 2.

The upper surface 30 of the sliding portion 20 is rotated in contact with the swash plate, wherein the sliding portion 20 of the piston slipper is a positive pressure in order to reduce wear caused by friction between the upper surface of the sliding portion 20 and the swash plate. It is formed to have only the characteristics of the bearing.

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

However, the conventional piston pump slippers for the hydraulic pump having only the characteristics of the hydrostatic bearings are subjected to excessive wear on the upper surface 30 of the piston slipper sliding part 20 at the start of the hydraulic pump is stopped and operated or at the low speed driving of the hydraulic pump. There was a problem that occurred.

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

Moreover, the conventional piston slippers for hydraulic pumps have a problem that the overall durability of the hydraulic pump is reduced and the mechanical efficiency of the hydraulic pump is reduced as friction increases.

Republic of Korea Patent Publication No. 10-2003-0074936

The present invention is to solve the above problems, an object of the present invention is to form an oil film on the upper end surface of the sliding portion at the start of the hydraulic pump, low-speed drive or stop, and by the fluid dynamic pressure effect To improve the frictional performance and lubrication performance of the piston slippers to prevent damage to the piston slippers, and to increase the efficiency of the hydraulic pump.

In order to achieve the object of the present invention, the hydraulic pump piston slipper according to the present invention includes a hydraulic part including a main body coupled to a piston and a sliding part having a circular cross section and having an upper end surface in contact with a swash plate. In the piston slipper for pump, the upper surface of the sliding part is a hole for the inflow of the hydraulic oil to the center point; A recess part for forming a flow path of the hydraulic oil introduced from the hole; And an outer portion formed along the outer circumferential direction of the recess portion, the outer portion having a plurality of inclined grooves, each inclined groove disposed on an inner circumferential surface of the outer portion; And an outlet located on an outer circumferential surface of the outer portion, wherein the length of the inlet is smaller than the length of the outlet.

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

Further, in another preferred embodiment of the hydraulic pump slipper according to the present invention, each inclined groove is formed to have a predetermined downward inclination angle from the other end of the inlet toward one end of the inlet with respect to the tangent to the reference line. Can be.

In addition, in another preferred embodiment of the hydraulic pump slipper according to the present invention, each of the inclined grooves may be formed so that the reference line is spaced by a predetermined angle along the circumferential direction of the outer portion.

Further, in another preferred embodiment of the hydraulic pump slipper according to the present invention, the ratio of the length of the inlet to the length of the outlet, that is, the length of the inlet length divided by the outlet length is 0.1 to 0.5, and the length of the inlet of the inclined groove The length of the outlet can be formed.

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

In addition, in another preferred embodiment of the slipper for the hydraulic pump according to the present invention, the angle of the reference line spaced along the circumferential direction of the outer portion may be 45 degrees to 72 degrees.
In addition, in another preferred embodiment of the slipper for the hydraulic pump according to the present invention, the hole is formed through the center of the upper surface of the sliding portion, the recess portion is arranged at equal intervals with respect to the convex portion and the recess portion A plurality of convex portions are formed along the circumferential direction of the virtual concentric circle, each of the plurality of convex portions is formed in an annular shape at least one end of the opening, the open ends of each of the convex portions are different concave portions Passages are formed to communicate with each other, and the passages formed in the plurality of convex portions may be disposed radially spaced apart from each other about the hole.

The piston slipper for the hydraulic pump according to the present invention forms an oil film at the start, stop, or low speed of the hydraulic pump, thereby generating a hydrodynamic effect, thereby reducing the wear of the piston slipper.

In addition, the piston slipper for the hydraulic pump according to the present invention has the effect of reducing the wear caused by the friction of the piston slipper by the hydrodynamic effect, and finally prevent the piston slipper from being damaged.

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

In addition, the piston slipper for the hydraulic pump according to the present invention has the effect of improving the frictional performance and the lubricating performance of the piston slipper to improve the durability of the hydraulic pump and minimize the frictional loss to increase the mechanical efficiency of the hydraulic pump.

Figure 1 shows a perspective view of a conventional piston slipper for the hydraulic pump is fastened to the 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 shows a side view of a piston slipper for a hydraulic pump according to a preferred embodiment of the present invention.
Figure 5 shows an enlarged view of the inclined groove of the piston slipper for the hydraulic pump according to a preferred embodiment of the present invention.
FIG. 6 is a conceptual view illustrating a downward inclination angle of the inclined groove shown in FIG. 4.

Preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. First, in adding reference numerals to components of each drawing, the same components are designated by the same reference numerals.

2 shows a perspective view of a piston slipper 1 for a hydraulic pump according to a preferred embodiment of the present invention. 3 shows 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 the inclined groove 40 of the piston slipper 1 for the hydraulic pump according to the preferred embodiment of the present invention. FIG. 6 shows a conceptual diagram for explaining a downward inclination angle α of the inclined groove 40 shown in FIG. 4.

2 to 6 will be described a piston slipper (1) for a hydraulic pump according to an embodiment of the present invention. The piston slipper 1 for the hydraulic pump according to the 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 is a hole 31, An outer portion 33 having a recess 32 and a plurality of inclined grooves 40.

One end of the body portion 10 is coupled to the piston 2. According to one embodiment of the present invention, although not necessarily limited thereto, one end of the piston 2 includes a ball joint, and one end of the body portion 10 may accommodate a ball joint of the piston 2. With one end, one end of the body portion 10 is coupled to the piston 2 by ball joint coupling or the like.

The sliding part 20 is located above the main body 10 and has a longitudinal cross section. The upper surface 30 of the sliding portion 20 is in contact with a swash plate, so that the upper surface 30 of the sliding portion 20 rotates on the swash plate according to the driving of the piston 2.

The hole 31 is formed through the center point of the upper end surface 30 of the sliding part 20, and performs a function of introducing the hydraulic fluid flowing in the hydraulic pump into the sliding part 20.

The recess 32 forms a flow passage of the working oil introduced from the hole 31. According to an exemplary embodiment of the present invention, the recess 32 is not necessarily limited thereto, and the recess 32 has the upper surface 30 of the sliding part 20 in consideration of a virtual concentric circle. A flow passage formed by a plurality of convex portions and concave portions spaced apart and intersected at regular intervals along the circumferential direction of virtual concentric circles having different radii, and thus formed by a plurality of convex portions and concave portions spaced and intersected at regular intervals. The hydraulic oil introduced through the hole 31 flows to be discharged to the outside of the sliding part 20.
The plurality of convex portions of the recessed portion 32 are alternately arranged with the plurality of concave portions, and the concave portions formed between the plurality of convex portions form a flow passage for guiding the movement of the hydraulic oil. Specifically, the convex portions may be arranged in plural to be radially spaced apart from each other about the hole 31. In addition, the convex portion may be formed in an annular shape with one end open. Thus, a passage can be formed at the open end of the convex portion. For example, the convex portion may be formed in a “C” shape which is an annular shape with one open end. In addition, the plurality of recesses communicate with each other through such a passage to form a flow passage of the working oil.
The plurality of convex openings once formed may be disposed radially spaced apart from each other with respect to the hole 31, and only one may be disposed at one reference line O (see FIG. 3). That is, the hydraulic oil introduced through the hole 31 may be discharged to the outside of the sliding portion 20 through the passage between the plurality of recesses. In other words, the passages formed in the open ends of the plurality of convex portions may be radially spaced apart from each other about the hole 31.

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

Each inclined groove 40 includes an inlet 41 located on the inner circumferential surface of the outer portion 33 and an outlet 42 located on the outer circumferential surface of the outer portion 33. The length L I of the inlet 41 is smaller than the length L O of the outlet 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 reference line O.

That is, as shown in FIGS. 3 and 5, the inclined groove 40 is based on the reference line O, which is an imaginary line of the radial direction of the upper surface 30 of the sliding part 20, with the hole 31 as the center point. The length L I of the inlet 41 is formed in a trapezoidal shape smaller than the length L O of the outlet 42.

According to another preferred embodiment of the present invention, the ratio (L I / L O ) of the length L I of the inlet 41 and the length L O of the outlet 42 of the inclined groove 40 is 0.1 to It is formed to be 0.5.

Table 1 shows the downward inclination angle α of the inclined groove 0.5 degrees and the length L I of the inlet 41 and the length L of the outlet 42 in the state where six inclined grooves 40 are formed at regular intervals. O) it is a friction torque value experimental data according to the ratio (L I / L O) of the.

<Ratio of inlet length (L I ) and outlet length (L O ) (L I / L O ) and friction torque> Ratio of length of inlet (L I ) to length of outlet (L O ) (L I / L O ) 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 hydraulic oil introduced through the hole 31 moves along the recessed part 32, and the hydraulic oil flows into the inlet 41 of the inclined groove 40 to the outside of the piston slipper 1 through the outlet 42. Is discharged.

As can be seen in Table 1, when the ratio (L I / L O ) of the length (L I ) of the inlet (41) and the length (L O ) of the outlet 42 is inclined groove 40 Since the flow rate of the hydraulic oil flowing into the) is too small to form an oil film like the conventional piston slippers, it is not possible to additionally generate a hydrodynamic effect in the end, thereby increasing the friction torque.

In addition, when the ratio L I / L O between the length L I of the inlet 41 and the length L O of the outlet 42 is 1 or more, the flow rate of the hydraulic oil discharged to the outside of the piston slipper 1 Too much of the oil film cannot be formed, and finally, the hydrodynamic effect cannot be additionally generated, thereby increasing the friction torque.

Therefore, the ratio L I / L O between the length L I of the inlet 41 and the length L O of the outlet 42 is formed to be 0.1 to 0.5, most preferably 0.3. .

As shown in FIGS. 5 and 6, according to another preferred embodiment of the present invention, the inclined groove 40 of the piston slipper 1 has an inlet opening based on a tangent P (see FIG. 3) with respect to the reference line O. It is formed to have a predetermined downward inclination angle α from one end of the inlet 41 toward the one end of the inlet 41.

That is, the inclined groove 40 has the same reference line from the other end of the inlet 41 (or the other end of the outlet 42) whose longitudinal section is not adjacent to the reference line O based on the tangent P with respect to the reference line O. It is formed to have a downward inclination angle α toward one end (or one end of the outlet 42) located on O).

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

Table 2 shows that six inclined grooves 40 are formed at regular intervals, and the ratio L I / L O of the length L I of the inlet 41 and the length L O of the outlet 42 is 0.3. Experimental data of the friction torque value according to the downward inclination angle α in the state.

<Downward tilt angle (α) and friction torque of the inclined groove> Downward tilt angle (α) Friction torque (Nm) Conventional Piston Slippers - 15.55 Comparative Example 1 0.1 degree 15.01 Example 1 0.2 degrees 10.22 Example 2 0.5 degree 7.51 Example 3 1 degree 11.15 Comparative Example 2 1.5 degree 14.67

As can be seen from Table 2, when the downward inclination angle α of the inclined groove 40 is less than 0.2 degrees, there is almost no hydrodynamic effect, and thus friction torque is reduced because no pressure is formed in the oil film. You will not.

In addition, when the downward inclination angle α of the inclined groove 40 is greater than 1 degree, the friction torque does not decrease due to the cavitation phenomenon in which bubbles are generated due to a sudden pressure change in the oil film.

Accordingly, the downward inclination angle α of the inclined groove 40 is formed to be 0.2 degree to 1 degree, and most preferably 0.5 degree.

In addition, the inclined 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 portion 33. . That is, the inclined groove 40 is formed to be spaced apart by a predetermined angle (C) on the outer portion (33).

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 portion 33 is 45 degrees to 72 degrees. That is, the angle C at which the reference line O is spaced along the circumferential direction of the outer portion 33 is formed to be selected from 45 degrees or more and 72 degrees or less. According to one embodiment of the present invention, if the angle (C) of the reference line (O) spaced along the circumferential direction of the outer portion 33 is 45 degrees, the inclined groove 40 in the outer portion 33 is 45 Eight angles are formed at an angle of 60 degrees, and in the case of 60 degrees, six inclined grooves 40 are formed in the outer portion 33, and in the case of 72 degrees, the inclined grooves 40 are formed in the outer portion 33. Five will be formed at an angle.

Table 3 is a ratio (L I / L O ) of the length (L I ) of the inlet (41) and the length (L O ) of the outlet 42 with reference to Table 1 and Table 2 is 0.3, the slope of the groove 40 Experimental data measuring the friction torque for about 5 minutes by varying the angle C at which the reference line O is spaced along the circumferential direction of the outer portion 33 at a downward inclination angle α of 0.5 degrees and a rated driving speed of 2600 rpm. to be.

<An angle C and friction torque at which the reference line O is spaced along the circumferential direction of the outer portion 33> Angle C at which the reference line O is spaced along the circumferential direction of the outer 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 in Table 3, when the angle (C) from which the reference line (O) is spaced along the circumferential direction of the outer portion (33) is greater than 72 degrees, the pressure of the oil film is hardly formed and the inclined groove 40 There is no difference from the friction torque of the conventional piston slipper without a).

In addition, when the angle C at which the reference line O is spaced along the circumferential direction of the outer portion 33 is smaller than 45 degrees, the hydraulic fluid is excessively discharged to the outside of the sliding part 20 so that the fluid dynamic effect is not generated. As a result, frictional torque is not reduced, and a lot of money is consumed for processing.

Therefore, the angle C at which the reference line O is spaced along the circumferential direction of the outer portion 33 is formed to be selected at 45 degrees or more and 72 degrees or less, and most preferably in terms of friction reducing effect and production cost. It is formed to be 60 degrees.

As described above, the piston slipper 1 according to the preferred embodiments of the present invention includes a plurality of inclined grooves 40 in which an outer portion 33 constituting the sliding portion 20 is formed along the circumferential direction. The length of the inlet of the inclined groove 40 is smaller than the length of the outlet. The inclined groove 40 is formed to have a downward inclination angle α, and is along the circumferential direction of the outer portion 33. Inclined grooves are formed to have an angle C spaced at regular intervals, and unlike the conventional piston slippers for hydraulic pumps, friction torque generated at the start, stop, or low speed operation of the hydraulic pump is achieved through the fluid dynamic effect by the oil film. It can be reduced by at least 15% and as much as 50%.

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

The invention is not limited to the embodiments shown in the figures 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, 20: sliding part,
30: top surface, 31: hole,
32: recessed portion, 33: outer portion,
40: inclined groove.

Claims (8)

In the piston slipper for a hydraulic pump comprising a main body coupled to the piston and a sliding portion in which the upper end surface is formed in a circular shape and the top surface is in contact with the swash plate,
The upper surface of the sliding portion,
A hole for the introduction of hydraulic oil to the center point;
A recess part for forming a flow path of the hydraulic oil introduced from the hole; And
And an outer portion formed along the outer circumferential direction of the recess and having a plurality of inclined grooves.
Each of the inclined grooves,
An inlet located on an inner circumferential surface of the outer portion; And
And an outlet located on an outer circumferential surface of the outer portion.
Piston slipper for the hydraulic pump, characterized in that the length of the inlet is formed smaller than the length of the outlet.
The method of claim 1,
One end of the inlet and one end of the outlet is a piston slipper for a hydraulic pump, characterized in that located on the same reference line. The method of claim 2,
Each of the inclined grooves,
The piston slipper for the hydraulic pump, characterized in that it is formed to have a predetermined downward inclination angle toward the one end direction of the inlet from the other end of the inlet on the basis of the tangent to the reference line.
The method of claim 2,
Each of the inclined grooves,
The piston slipper for a hydraulic pump, characterized in that the reference line is formed to be spaced apart by a predetermined angle in the circumferential direction of the outer portion.
The method of claim 2,
The ratio of the length of the inlet and the length of the outlet is a piston slipper for a hydraulic pump, characterized in that 0.1 to 0.5.
The method of claim 3,
The downward inclination angle of the piston pump slipper, characterized in that 0.2 to 1 degree.
The method of claim 4, wherein
The angle of the piston slipper for the hydraulic pump, characterized in that 45 to 72 degrees. The method according to any one of claims 1 to 7,
The hole is formed through the center of the upper surface of the sliding portion,
The recess portion is formed in a plurality along the circumferential direction of the imaginary concentric circle in which the convex portion and the concave portion are arranged at equal intervals around the hole,
Each of the plurality of convex portions is formed in an annular shape, at least one end of which is open, and each open end of each of the convex portions is formed with a passage through which different concave portions of the plurality of concave portions communicate with each other.
Passages formed in the plurality of convex portions are piston slippers for the hydraulic pump, characterized in that arranged radially spaced from each other around the hole.
KR1020130060457A 2013-05-28 2013-05-28 Piston slipper for hydraulic pump KR101984316B1 (en)

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Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101757971B1 (en) 2015-04-28 2017-07-19 유원산업(주) Piston shoe of hydraulic pump
KR102321840B1 (en) * 2017-03-23 2021-11-05 현대두산인프라코어(주) Piston shoe and shoe plate for hydrauric piston pump

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101012817A (en) 2007-02-01 2007-08-08 华中科技大学 Plunger piston slippery boots assembly
CN101196182B (en) 2006-12-04 2010-10-13 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

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3703610B2 (en) * 1997-08-06 2005-10-05 カヤバ工業株式会社 Axial piston pump or motor
KR100468088B1 (en) 2002-03-14 2005-01-26 한국기계연구원 Piston shoe of hydraulic motor and pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101196182B (en) 2006-12-04 2010-10-13 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

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