KR20140081090A - Piston pump for reducing bending moment - Google Patents

Abstract

Disclosed is a piston pump capable of reducing bending moments. The piston pump capable of reducing bending moments includes: a casing (110) forming the exterior of the piston pump; a rotary group (R/G) including a driving shaft (120) which is arranged in the casing (110) to be able to rotate and a cylinder block (140) coupled to the driving shaft (120) by a spline; and a bending moment resisting module which is coupled to the rotary group (R/G) and resists the occurrence of a bending moment (B/M) formed on the rotary group (R/G) during the operation of the rotary group (R/G) in order to reduce the bending moment.

Description

[0001] The present invention relates to a piston pump for reducing bending moment,

The present invention relates to a bending moment reducing type piston pump, and more particularly, to a bending moment reducing type piston pump which can reduce a bending moment generated in a rotary group region including a cylinder block to a minimum, And more particularly to a bending moment reducing type piston pump capable of effectively preventing the shortening of life of a pump by improving durability.

In a construction equipment such as an excavator, a pump is driven by rotational kinetic energy provided by an engine such as an internal combustion engine.

At this time, the pump supplies operating fluid such as an actuator such as a boom, an arm, a swing motor, a traveling motor and the like, and a variable displacement type piston pump whose displacement is variable, such as an axial pump, It is common.

1 is a structural view of a conventional piston pump.

A piston pump, also referred to as an axial piston pump, rotates the cylinder block 4 at a high speed while a plurality of pistons are inserted into the cylinder (piston chamber) At the same time, the piston inserted into the cylinder reciprocates in the cylinder and is configured to suck and discharge the working fluid through each port.

Such a piston pump has been widely applied to a swash plate type swash plate having an inclined inclined swash plate 3 in a casing (not shown in FIG. 1).

As described above, in the swash plate type axial piston pump to which the swash plate 3 is applied, the flow rate of the hydraulic oil discharged from the pump can be determined according to the inclination (swing angle) of the swash plate 3.

1, the bending moment (B / M) in the direction of arrow B is frequently generated in the rotary group region including the cylinder block 4 However, there is a problem that the efficiency of the pump is lowered because no means is taken against the generation of the bending moment (B / M).

If the bending moment (B / M) is constantly generated and the strength of the bending moment (B / M) is constant, the durability of the individual parts such as the driving shaft (2) The life of the pump can be shortened.

Korean Patent Application No. 10-2004-0099069

SUMMARY OF THE INVENTION The present invention has been made in order to solve the above problems, and it is an object of the present invention to provide a hydraulic control apparatus for an internal combustion engine which can reduce a bending moment generated in a rotary group region including a cylinder block to a minimum, And to provide a bending moment reducing type piston pump capable of effectively preventing the shortening of life of the pump by improving the durability of the individual parts.

In order to achieve the above-described object, the present invention provides a casing comprising: a casing forming an appearance; A rotary group including a driving shaft rotatably disposed in the casing, and a cylinder block splined to the driving shaft; And a bending moment resistance module coupled to the rotary group to reduce the bending moment by resisting bending moment generated in the rotary group in operation of the rotary group. Lt; / RTI >

The present invention further provides the following specific embodiments with respect to the above embodiment of the present invention.

According to an embodiment of the present invention, the bending moment resistance module is coupled to the cylinder block of the rotary group.

According to an embodiment of the present invention, the bending moment resistance module includes: a supporter for supporting the metal bearing; And a metal bearing disposed between the cylinder block and the supporter to minimize frictional force.

According to an embodiment of the present invention, the bending moment resistance module is disposed at a circumference 1/6 of the cylinder block and is disposed at a plurality of locations spaced apart from each other along the longitudinal direction of the driving shaft, And an inclination angle between the outer ends of the bending moment resistance modules is 30 degrees.

According to the present invention, the bending moment generated in the rotary group region including the cylinder block can be minimized, thereby preventing the pump efficiency from being lowered and improving the durability of the individual components, thereby effectively preventing the shortening of the life of the pump A bending moment reducing type piston pump is provided.

1 is a structural view of a conventional piston pump.
2 is an internal structural view of a bending moment reducing type piston pump according to an embodiment of the present invention.
FIG. 3 is an exploded perspective view of a state in which a part of the casing or the like is removed in FIG.
4 is a schematic front view of the structure of Fig.
FIG. 5 is a view showing the direction of bending moment in FIG. 4; FIG.
6 is a cross-sectional structural view of the bending moment resistance module region.

Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.

FIG. 2 is an internal structural view of a bending moment reducing type piston pump according to an embodiment of the present invention, FIG. 3 is an incision oblique view of a state in which a part of the casing or the like is removed in FIG. 2, Fig. 5 is a view showing the direction of the bending moment in Fig. 4, and Fig. 6 is a cross-sectional view of the bending moment resistance module area.

Referring to these drawings, the bending moment reducing type piston pump according to the present embodiment includes a casing 110 forming an outer pipe, a driving shaft 120 rotatably disposed in the casing 110, A rotary block R / G including a cylinder block spline coupled to the rotary group R / G 120, a rotary block R / G coupled to the rotary group R / G, And a bending moment resistance module 160 for reducing the bending moment B / M by resisting the occurrence of a bending moment B / M formed in the R / G.

3 and 4, the structure around the outer casing 110 and the valve plate 150 is omitted to show the structure of the internal components more clearly.

More specifically, the casing 110 forms the appearance of the bending moment reducing type piston pump of the present embodiment. Since the drawings are only one example, the scope of the present invention is not limited to the shapes of the drawings.

In the casing 110, a rotary group (R / G) rotated or operated upon operation of the piston pump of the present embodiment is provided. The rotary group R / G may include a driving shaft 120, a cylinder block 140, a swash plate 130, and the like.

The driving shaft 120 is rotatably supported by a bearing 111 or the like in a central region in the casing 110. [

The swash plate 130 is slantingly installed on one side of the driving shaft 120. The flow rate of the hydraulic fluid discharged from the pump is determined according to the inclination (the gentle angle) of the swash plate 130. [

The cylinder block 140 is splined to the driving shaft 120 inside the casing 110. The cylinder block 140 is provided with a plurality of piston chambers (or cylinders) C and is co-rotated with the driving shaft 120.

In each piston chamber C, a piston 141 that is joined to the shoe 132 in which the ball 142 at one end abuts against the swash plate 130 is inserted.

The inner space of each piston chamber C while the cylinder block 140 rotates is connected to the suction port S and the discharge port T of the valve plate 150 through the opening B formed in the rear surface of the cylinder block 140 .

A valve plate 150 having a suction port S and a discharge port T is provided in a front region of the valve block 112 at the rear end of the casing 110.

The valve plate 150 is disposed in the casing 110 so that the rear surface of the valve plate 150 is brought into contact with the corresponding surface (inner surface) of the rear valve block 112 so as to face each other.

The front surface of the valve plate 150 is a sliding surface 151 on which the rear surface of the cylinder block 140, which is integrally rotated with the driving shaft 120, is in contact with and slidably engaged.

Meanwhile, when the piston pump of the present embodiment is operated, pressure fluctuations may occur in the respective piston chambers C formed in the cylinder block 140.

The process in which the pressure fluctuates in one piston chamber (C) includes a pressure rising process and a pressure falling process.

This pressure fluctuation acts as an excitation force to vibrate the entire device and, as a result, generate noise. If the pressure fluctuates suddenly during the pressure increasing process and the pressure decreasing process, not only the noise increases but also the noise The high frequency component becomes large, which may eventually generate a noise that is uncomfortable to the ear.

In addition, in the case of the swash plate type axial piston pump in which the cylinder block 140 is rotated with respect to the inclined swash plate 130 to suck and discharge the fluid, pressure pulsation due to flow pulsation occurs inevitably. Since the pressure pulsation also acts as an exciting force for exciting the structure, it has become the main cause of the hydraulic system noise. In this respect, the applicant of the present invention also applied for and applied for many improved technologies.

On the other hand, the bending moment resistance module 160 resists the generation of the bending moment B / M (see the arrow in Fig. 5) formed in the rotary group R / G during the operation of the rotary group R / (B / M) of the bending moment.

In this embodiment, the bending moment resistance module 160 is coupled to the cylinder block 140 of the rotary group R / G.

The bending moment resistance module 160 includes a supporter 161 for supporting the metal bearing 161 and a metal bearing 162 disposed between the cylinder block 140 and the supporter 161 for minimizing frictional force do.

Of course, the bending moment resistance module 160 may be applied only to the supporter 161. However, if the metal bearing 162 is provided between the cylinder block 140 and the supporter 161, frictional force can be minimized .

The bending moment resistance modules 160 may be disposed in a circumference 1/6 of the cylinder block 140 and may be disposed at a plurality of spaced apart from each other along the longitudinal direction of the driving shaft 120.

In this embodiment, two bending moment resistance modules 160 are applied to each other along the longitudinal direction of the driving shaft 120. Of course, such matters are only an example, and the scope of the present invention is not limited to the shape of the drawings.

The inclination angle between the center of the cylinder block 140 and the outer end of the bending moment resistance module 160 may be 30 degrees. 6, the angle between the center of the cylinder block 140 and the opposite ends of the bending moment resistance module 160 may be 60 degrees.

The operation of the bending moment reducing type piston pump having such a configuration will be described.

When the driving shaft 120 is rotated around the center axis O, the cylinder block 140 installed in the casing 110 is also rotated integrally.

At this time, the piston 141 reciprocates between the top dead center and the bottom dead center in the piston chamber C and sucks the fluid into the piston chamber C through the suction port S of the valve plate 150 (The piston moves from the top dead center to the bottom dead center), the fluid in the piston chamber C is pushed and discharged through the discharge port T of the valve plate 150 (when the piston moves from the bottom dead center to the top dead center ).

That is, when the driving shaft 120 and the cylinder block 140 are integrally rotated, the shoe 132 and the shoe plate 131, which support one end of the piston 141, rotate while sliding on the swash plate 130 So that the piston 141 reciprocates forward and backward by the inclination of the swash plate 130.

Since the cylinder block 140 is relatively rotated with respect to the valve plate 150 when the driving shaft 120 and the cylinder block 140 are integrally rotated, (151) in a close contact state.

At this time, the fluid is sucked into the piston chamber C when the opening B of the piston chamber C formed on the rear surface of the cylinder block 140 is connected to the suction port S of the valve plate 150, When the opening portion B of the valve body C is connected to the discharge port T of the valve plate 150,

Of course, the intake or discharge of such a fluid is performed as the piston 141 in each piston chamber reciprocates by the swash plate 130 with the piston chamber C connected to the ports T and S, respectively.

On the other hand, during the repetitive operation of the piston pump, a bending moment (B / M) is generated in the rotary group (R / G) as shown by the arrow in FIG.

However, since the bending moment resistance module 160 is provided in the cylinder block 140 of the rotary group R / G in the piston pump of the present embodiment, the bending moment resistance module 160 is formed in the rotary group R / The bending moment B / M of the pump can be reduced by resisting the generation of the bending moment B / M.

Particularly, the metal bearing 162 on the bending moment resistance module 160 can resist the occurrence of the bending moment B / M while minimizing the frictional force, so that a more advantageous effect can be expected.

According to the bending moment reducing type piston pump of this embodiment having such a structure and action, the bending moment B / M generated in the rotary group (R / G) region including the cylinder block 140 can be reduced to a minimum The efficiency of the pump can be prevented from lowering, and the durability of the individual components can be improved, thereby effectively preventing the life of the pump from being shortened.

It will be apparent to those skilled in the art that various modifications and variations can be made in the present invention without departing from the spirit or scope of the invention. Accordingly, such modifications or variations are intended to fall within the scope of the appended claims.

110: casing 120: driving shaft
130: swash plate 140: cylinder block
150: valve plate 160: bending moment resistance module
161: Supporter 162: Metal bearing
R / G: Rotary group

Claims (4)

A casing (110) forming an appearance;
A rotary group R / G including a driving shaft 120 rotatably disposed in the casing 110, and a cylinder block 140 spline coupled to the driving shaft 120; And
And a bending moment (B / M) that is coupled to the rotary group (R / G) to resist generation of bending moment (B / M) formed in the rotary group (R / G) And a bending moment resistance module (160) for reducing the bending moment resistance (B / M).
The method according to claim 1,
Wherein the bending moment resistance module (160) is coupled to the cylinder block (140) of the rotary group (R / G).
3. The method of claim 2,
The bending moment resistance module (160)
A supporter 161 for supporting the metal bearing 161; And
And a metal bearing (162) disposed between the cylinder block (140) and the supporter (161) to minimize frictional force.
The method according to claim 2 or 3,
The bending moment resistance module 160 is disposed in a circumference 1/6 of the cylinder block 140 and is disposed at a plurality of spaced apart from each other along the longitudinal direction of the driving shaft 120,
Wherein the inclination angle between the center of the cylinder block (140) and the outer end of the bending moment resistance module (160) is 30 degrees.

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