KR0161564B1 - Apparatus for damping the shock of the piston in hydraulic breaker - Google Patents

Abstract

The present invention relates to a hydraulic breaker ball shock absorbing device, and provides a ball damping room (24) and a fluid drained downward from the ball damping room (24) installed so that an impact is not applied to the breaker body when the piston is idle. A buffering installation groove 31 is formed in the middle between the drain oil chambers 27 to be collected and drained into the low pressure line, and a buffer ring 32 is provided in the buffering installation groove 31. 32), when the piston is in idle operation, forcibly interrupts the flow of fluid flowing from the idle buffer room 24 to the drain oil chamber 27 at the lower side so that the back pressure to the piston is increased, thereby lowering the piston's idle motion. To control.

Description

Hydraulic Breaker Ball Shock Absorber

1 is a schematic cross-sectional view showing the internal structure of the hydraulic breaker bolster shock absorber according to the present invention.

2 is an enlarged cross-sectional view showing an operation state around the ball-hit room when a ball strike occurs in a hydraulic breaker equipped with a ball shock absorber according to the present invention, and a shear flow acting on the top gap and the bottom gap of the ball-wound buffer type when a ball strike occurs. And cross-sectional view showing the relationship between side flow.

Figure 3 is an enlarged cross-sectional view showing the operating relationship between the buffer and the piston installed in the cylinder in accordance with the present invention.

Figure 4 is an enlarged cross-sectional view of another embodiment of the present invention.

Figure 5 is an enlarged cross-sectional view of another embodiment of the present invention.

6 is a whole inside cross-sectional view of a conventional general hydraulic breaker.

7 is a sectional view of the hydraulic breaker shown in FIG.

8 is a cross-sectional view of the hydraulic breaker shown in FIG.

FIG. 9 is an enlarged cross-sectional view of a periphery of a vacant shock chamber in the conventional hydraulic breaker shown in FIG.

FIG. 10 is a cross-sectional view showing a case in which a ball strike occurs in a conventional hydraulic breaker in the same form as FIG. 2, and a cross-sectional view showing a relationship between shear flow and side flow in a top gap and a bottom gap of a ball strike buffer room when a strike occurs to be.

* Explanation of symbols for main parts of the drawings

5: Compressed gas seal 6: Cylinder upper chamber

7: cylinder lower chamber 24: vacant shock room

25: upper gap of the buffer chamber 26: lower gap of the buffer chamber

27: drain loss 31: buffering groove

32: buffering 38: space

39: sliding 40: lubricating oil

41: lubricant oil chamber

The present invention relates to a hydraulic breaker used for installation in heavy equipment, and in particular, the hydraulic breaker ball shock absorber to protect the breaker parts and extend the life by not impacting the hydraulic breaker itself when the piston of the hydraulic breaker is struck. Relates to a device.

Generally, the hydraulic breaker which is widely used as crushing equipment in construction and civil works is used to crush rock, concrete, asphalt, etc. by using the hydraulic source of the equipment by mounting it on the mobile equipment such as excavators. Is also increasing.

Such a hydraulic breaker is generally provided with a piston (2) for moving up and down by hydraulic pressure in a body called a cylinder (1), as shown in Figure 6, the upper and lower ends of the piston (2) and the middle By supplying the pressurized oil controlled by the valve 14 to the plurality of chambers formed in the chamber, the upper and lower ends of the piston 2 are sequentially converted to high pressure and low pressure according to their positions, thereby making the piston 2 move at a high speed. The piston reciprocates, and the up and down reciprocating motion of the piston 2 is transmitted to the chisel 3 to crush the to-be-damaged object.

When the breaker having such a structure breaks a to-be-damaged object such as a rock 4 or the like, it occurs when the chisel 3 directly contacting the rock 4 and the piston 2 reciprocating in the cylinder 1 collide with each other. Impact force is transmitted to the rock through the chisel (3) to break the rock, the breaking force of the breaker is determined by the weight and the speed of the piston (2).

In recent years, as the technological development of the breaker operation circuit and structure for improving the impact force of the breaker continues and the hydraulic source of the vehicle equipped with the breaker becomes high speed and high capacity, the hydraulic breaker becomes smaller and lighter, and also high capacity and high efficiency. .

In addition, with the above-mentioned efforts, development of high-quality materials and heat treatment technologies for components that are directly impacted, such as pistons and chisels, has been made.

On the other hand, when the piston strikes the chisel 3 in the normal hitting state of the breaker, that is, the chisel 3 is in the normal position, the breaker itself does not have a large force. However, if the piston 2 moves in the direction of impact when the chisel 3 is not in the normal position, the piston will hit the other parts of the breaker without impacting the chisel, which may cause great damage to the parts. In addition, the kinetic energy of the piston is all converted into the deformation energy of the internal parts of the breaker and heat, noise, vibration, etc., which may cause serious damage to the breaker or shorten the life.

In this case, when the piston 2 does not impact the chisel 3 and vanishes, the other parts inside the breaker are hit by a breaker ball. Such breaker strike can occur constantly during daily operation. For example, in the case of breaking a rock with a breaker, if the chisel (3) is positioned on the rock (4) and the piston (2) hits the chisel several times, and the rock is broken in a moment, the chisel (3) is broken. Since it is not supported by the rock, the chisel 3 supported by the rock is lowered from the inside of the cylinder 1 so that the chisel 3 is out of the bottom dead center of the piston 2.

In this case, therefore, even if the piston 2 moves at a high speed in the downward direction, the chisel 3 cannot be impacted, and if the operator fails to stop the breaker at that moment, all subsequent hits are struck. . In most cases, hydraulic breakers operate at high speeds of four or more times per second, so one or two strikes can't be avoided unless the operator pays special attention.

Referring to Figures 6 to 10 attached to the crushing operation of the hydraulic breaker, the compressed gas seal 5 is provided on the upper extension line of the piston (2) mounted inside the cylinder (1) And upper and lower cylinders 6 and 7, respectively, having upper and lower ends of the piston 2, and upper and lower chambers 6 and 7 having upper and lower large diameter parts formed on the piston 2. 8 and 9 and grooves 10 and 11 formed on the inner surface of the cylinder 1.

The cylinder upper and lower chambers 6 and 7 have a structure connected to the hydraulic source through the flow passages 12 and 13 and the valve 14.

When the hydraulic breaker having this structure is in a state where the piston 2 hits the chisel 3 and immediately rises again for the next hit, as shown in FIG. 6, the hydraulic oil supplied from the hydraulic source is Through the flow path 13 is introduced into the cylinder lower chamber 7 to apply pressure to the lower piston pressure receiving surface 15 formed in the lower large diameter portion 9 of the piston 2, the cylinder upper chamber 6 The upper end of the piston is brought into a low pressure state by being connected to the low extrusion port 16 through the oil passage 12 and the valve 14.

Therefore, the piston 2 is raised while further compressing the gas of the compression gas chamber 5 due to the pressure applied to the cylinder lower chamber 7.

On the other hand, as shown in FIG. 1, when the hydraulic breaker operates normally, the chisel 3 is supported on the rock 4, which is a to-be-shredded object, and the vehicle equipped with the hydraulic breaker holds down the hydraulic breaker. In this state, in this state, the chisel 3 is pushed up by the arm 4, and the upper end of the chisel 3 is fixed by the chisel stopper 17 formed in the breaker body.

At this time, the chisel pin 19 fitted in the chisel groove 18 formed on the side of the chisel 3 is located at the lower end of the chisel groove 18, and the chisel 3 in the direction in which the piston 2 is hit. In the non-constrained state, the impact force generated when the piston 2 hits the chisel 3 is applied to most of the rock 4 except the frictional loss generated at the contact surface between the chisel 3 and the breaker body. You lose.

Accordingly, in this case, when the piston 2 is moved up and down, no damage is caused to the parts other than the piston 2 and the chisel 3.

7 is a breaker state diagram immediately before the piston 2 hits the chisel 3 in the normal strike state. When the piston 2 rises to the top dead center, pressure oil is supplied to the valve switching circuit 20 in the breaker. The valve 14 is switched, whereby high pressure hydraulic oil is supplied to the cylinder upper chamber 6 so that the cylinder upper chamber 6 is converted to high pressure like the cylinder lower chamber 7.

Thus, when both the cylinder upper chamber 6 and the cylinder lower chamber 7 are maintained at high pressure, the area difference between the upper piston pressure receiving surface 21 and the lower piston pressure receiving surface 15 (diameter upper diameter of the upper diameter of the piston) The piston is formed to be smaller than the lower diameter of the lower end diameter portion of the piston, so that downward pressure is applied to the piston 2 as much as the area difference thereof.

In addition, when the piston 2 ascends, an expansion pressure that is generated while the compressed gas inside the compressed gas chamber 5 compressed as the piston 2 descends as the volume decreases is added to the piston 2. Since the lowering operation of the piston 2 is made at a higher speed, the piston 2 hits the chisel striking surface 22 of the chisel 3 with a large force.

FIG. 8 shows a state diagram when an abnormal blow, that is, a hit, occurs. In this case, the chisel 3 is not supported on the rock 4, which is a hit, and the chisel 3 is held on the breaker body. Since there is no separate support means for maintaining the state as it is, the top of the chisel (3) is pushed down from the state in contact with the chisel stop jaw (17), at this time formed in the chisel (3) Since the chisel pin 19 is caught in the chisel groove 18, the chisel 3 does not completely come out of the breaker body. However, even when the piston 2 is lowered to the bottom dead center, the chisel striking surface 22 formed at the upper end of the chisel 3 does not contact the piston striking surface 23 formed at the lower end of the piston 2.

9 is an enlarged cross-sectional view showing the position of the piston (2) and the cylinder (1) around the cylinder lower chamber (7) in the state where the piston (2) is lowered even more than the normal strike position, and just before the ball strike occurs. to be.

As shown in FIG. 9, when the stroke stroke of the piston 2 occurs, that is, when the piston 2 touches the chisel 3 and fails to exert an impact force and falls further than the normal strike position, the piston lower hydraulic pressure surface ( 15) compresses the oil flowing into the pneumatic buffer chamber 24 formed in the cylinder lower chamber 7 through the groove 11 forming the cylinder lower chamber 7, in this state the piston (2) Since the lower pressure receiving surface 15 of the cylinder lower chamber 7 completely separates the vacancy buffer room 24, the passage within which the oil inside the vacancy buffer room 24 can easily flow out is not formed. In addition, since the descending speed of the piston 2 is very fast, the oil in the vacant shock buffer 24 is compressed to a high pressure, and the pressure of the compressed pressure oil is applied to the piston lower pressure receiving surface 15 as a reaction force to the piston. Braking in (2) upward It generates a force to reduce the falling speed of the piston (2).

At this time, a detailed operation phenomenon generated while the oil is compressed between the empty shock absorbing chamber 24, the cylinder lower chamber 7 and the piston 2 will be described with reference to FIG.

As shown in FIG. 10, when the vacancy shock chamber 24 is compressed by the piston 2, the vacancy shock chamber 24 is dependent on how much fluid in the vacancy shock chamber 24 is released. The pressure generated therein is influenced, and the magnitude of this pressure is directly related to the braking performance for the pitting of the piston 2.

When the vacancy buffer room 24 is compressed, the passage of fluid pushed out of the vacancy buffer room 24 becomes a buffer chamber upper gap 25 and a buffer chamber lower gap 26, and the buffer chamber upper gap ( The fluid exiting through 25) is connected to the high pressure flow path 13 of the breaker through the cylinder lower chamber 7, and the fluid exiting the lower gap 26 of the buffer chamber is collected in the drain oil chamber 27 to drain the flow path. Exit 28 to breaker low pressure outlet.

On the other hand, the flow rate of the fluid flowing out between the contact surface of the cylinder 1 and the piston 2, that is, between the upper end of the buffer chamber 25 and the lower end of the buffer chamber 26 is the combined amount of the flow rate due to the two flow sources, In FIG. 10, the upper and lower ends of FIG. 10 show the operating cause of the fluid flow and the synthesis amount thereof in detail.

As shown in the enlarged view of FIG. 10, one of the causes of the fluid flowing between the cylinder 1 and the piston 2 as the piston 2 descends is caused by friction due to the viscosity of the fluid. Shear flow, which is inherently viscous, and when there is an object moving around the fluid, the frictional force is applied according to the relative velocity by the viscosity, and the frictional force starts the fluid to cause the fluid to move. Fluids having this characteristic are called Newtonian fluids, and hydraulic fluids also produce such shear flows.

On the other hand, one of the causes of the flow rate is the flow caused by the pressure difference, the fluid between the two points in the pipeline is forced from the high pressure to the low pressure by the pressure difference of the fluid to generate a flow, as described above Between the cylinder and the cylinder as the piston descends and compresses the pneumatic buffer room 24 to apply a pressure, the high pressure state, while the lower cylinder 7 and the drain oil chamber is relatively low pressure, Flow is generated from the high-pressure hollow buffer room 24 toward the lower cylinder chamber 7 and the drain oil chamber 27. In addition, since the gap between the upper end of the buffer chamber 25 and the lower end of the buffer chamber 26 defined in the bar is small, the generated flow can be regarded as a lateral flow between the gaps.

According to this theoretical background, the flow generated in the buffer chamber top gap 25 and the buffer chamber bottom gap 26 is sheared by the downward movement of the piston 2, as can be seen in the enlarged cross-sectional view of FIG. The combined amount of lateral flow due to the pressure difference between the flow and the vacancy buffer room 24 and the other oil chambers 7 and 27 adjacent thereto.

Here, the flow rate of the fluid in contact with the piston (2) in shear flow is the same as the speed of the piston, and proportionally decreases away from the surface of the piston (2) to flow in contact with the inner wall of the cylinder (1) Has a linear velocity profile of zero, and the lateral flow has the highest velocity at the center of the channel and a parabolic velocity profile of zero at both walls due to friction.

However, since the direction of movement of the piston 2 is downward, the shear flow generated between the two gaps 25 and 26 is all downward, but the lateral flow occurs from the place where the pressure is high to the low place. In the gap 25, the shear flow and the lateral flow are opposite to each other, so the combined flow of the two flows becomes relatively small. In the lower gap 26 of the buffer chamber, the flow of the two flows is the same, so the combined flow becomes larger. .

In addition, since the pressure in the buffer chamber is not so high at the initial stage when the piston lower hydraulic pressure surface 15 begins to compress the hollow buffer room 24, the lateral flow generated by the pressure difference is not large. This amount of compression causes the pressure inside the buffer chamber 24 to increase, resulting in an increase in the amount of lateral flow. Therefore, the flow rate that flows out through the upper and lower gaps 25 and 26 of the buffer chamber increases, so that the flow rate inside the buffer chamber 24 decreases, thereby braking the piston 2, as described above. In the lower gap 26, the direction of the side flow and the shear flow are the same, while in the lower gap 26 of the buffer chamber, the direction of the side flow and the shear flow are opposite to each other. It has a greater impact than the gap 25.

On the other hand, the fluid flowing through the lower end gap 26 of the buffer chamber when the ball is generated is collected in the drain oil chamber 27, the lower end of which is sealed by the lower oil seal (29), if the fluid in the drain oil chamber 27 is not discharged Since the pressure of the drain oil chamber 27 rises higher than the pressure of the vacancy buffer room 24 and damages the lower seal 13 installed at the lower end, the drain oil passage 28 is connected to the drain oil chamber 27 to form a piston ( When 2) descends, the pressure oil flowing out of the lower end gap 26 of the buffer chamber is drained to the low extrusion port 16.

Therefore, the pressure difference between the buffer chamber 24 and the drain oil chamber 27 is increased by connecting the drain oil chamber 27 to the low pressure outlet 16, thereby increasing the lateral flow generated in the lower end gap 26 of the buffer chamber. On the other hand, while preventing the pressure formation of the vacant shock buffer room 24, but inevitably to protect the oil seal 29 is installed on the bottom of the drain oil chamber 27, the drain oil chamber 27 as described above It is inevitable to have a structure directly connected to the low extrusion port 16.

Therefore, as in the conventional hydraulic breaker as described above, there is a restriction to obtain sufficient piston braking characteristics with only the empty shock absorbing chamber 24.

As a method for solving this problem, there may be a method of reducing the flow contact surface clearance between the piston (2) and the cylinder (1), thereby improving the braking characteristics by reducing the flow rate exiting through the clearance, but the piston The flow contact surface of (2) and the cylinder (1) requires a certain minimum clearance due to machining accuracy of each part and problems such as impact and vibration during operation, lubrication, thermal deformation, and oil contamination. Therefore, since the clearance of the flow contact surface is determined to a certain extent depending on the size of the piston, it is difficult to solve the above problems by using the clearance.

In addition, although the braking characteristic may be improved by lengthening the length of the pulsation damping chamber 24, the length of the pulsation damping chamber 24 is increased so that the entire stroke of the piston 2 becomes long. Becomes longer and heavier.

Due to this reason, the conventional ball buffer room has a problem in that it does not serve as a sufficient role in the ball buffer of the piston.

Accordingly, the present invention, when the piston of the hydraulic breaker is struck, the pressure of the vacancy buffer room is maintained at a predetermined value or more so that the brake can be braked by this pressure, the hydraulic breaker struck buffer to improve the ball struck function The purpose is to provide a device.

The apparatus of the present invention for achieving the above object is installed in the cylinder so that the piston can move freely up and down, the high pressure and low pressure oil pressure is applied to the cylinder lower chamber and the cylinder upper chamber provided at the upper and lower ends of the piston By the force introduced selectively and the pressure generated by the pressure difference and the reaction force generated as the gas of the compression gas seal provided on the upper end of the piston is compressed according to the upward movement of the piston, In the ballast shock absorber of the hydraulic breaker equipped with a shock absorber to reduce the impact of the piston by applying a back pressure to the piston when the piston does not strike the chisel, when the piston does not strike the chisel. A buffering groove is formed in the flow contact surface between the cylinder lower chamber and the vacant shock chamber. And, consists of a buffer structure is installed in the installation depressed buffering.

The apparatus of the present invention having such a structure is provided with resistance by the buffering when the hydraulic oil pressurized in the vacancy buffer chamber when the piston is struck and lowered out of the vacancy buffer chamber, thereby falling out of the vacancy buffer chamber. It is slower than the flow rate of outgoing pressure oil, so that a sufficient braking force can be applied to the rapidly descending piston.

Therefore, in the hydraulic breaker provided with the apparatus according to the present invention, even when the piston is idle, the abnormal breaker is not applied to the breaker body, thereby protecting the internal parts of the hydraulic breaker.

Hereinafter, with reference to the accompanying drawings, the present invention will be described in detail.

1 is a cross-sectional view showing the whole inside of the hydraulic breaker to which the apparatus according to the present invention is applied, and its detailed configuration and basic operation process have already been described in detail in the above description, and thus, the same parts are used here to avoid duplication. Description will be omitted, and description of the features of the present invention will be described based on this.

In the ball cushioning device according to the present invention, an annular buffering mounting groove 31 is formed on the inner surface of the cylinder 1 between the ball buffering chamber 24 and the drain oil chamber 27, and buffered in the buffering mounting groove 31. (32) has a built-in structure.

Here, the buffer ring 32 is preferably installed to be as close as possible to the outer surface of the piston (2).

FIG. 2 is a detailed view of FIG. 1, which describes the process in which the buffer ring 32 improves the shock absorbing function of the piston 2.

As the piston 2 is struck and compressed, the vacancy buffer room 24, the fluid exiting through the lower end gap 26 of the buffer chamber reaches the buffering installation groove 31 provided on the inner surface of the cylinder. At this time, the buffering 32 serves to block the passage so that the fluid does not go down any more, thereby preventing the fluid from escaping toward the drain oil chamber 27.

As a result, due to the shear flow generated when the piston (2) is lowered, the fluid of the vacancy buffer room 24 is introduced into the buffering installation groove 31, and thus the internal pressure of the buffering installation groove 31 is It rises and becomes higher than the pressure of the vacancy buffer room 24.

The lateral flow caused by the pressure difference generated in this way is generated in the opposite direction to the shear flow, and the fluid descending to the buffering installation groove 31 is returned to the vacant buffer room 24. The situation of this flow is shown in FIG.

That is, as shown in FIG. 3, since the buffering installation groove 31 is formed as described above and the buffering 32 is installed in the buffering installation groove 31, the piston 2 may be vacantly lowered. When the oil is lowered from the vacancy buffer room 24 toward the drain oil chamber 27, the oil is lowered to the piston 2 in the lower end gap 26 of the buffer chamber communicating the vacant shock buffer room 24 and the drain oil chamber 27. The fluid flowing toward the buffer chamber 24 flows toward the buffering installation groove 31, and the fluid flowing toward the cylinder 1 flows toward the buffer chamber 24 from the buffering installation groove 31.

And some of the fluid flowing into the buffering installation groove 31 is discharged toward the drain oil chamber 27 through the buffering contact surface gap (26a) formed between the buffer ring 32 and the piston (2), which is the piston The flow rate generated by the dynamic fluid lubrication caused by the relative motion between (2) and the buffering 32 is very small.

On the other hand, when the hydraulic oil flows into the buffering installation groove 31, the buffering ring 32 is brought into close contact with the buffering installation groove 31 downward, which is applied to the upper surface 33 of the buffering 31. Since the pressure is greater than the pressure distributed in the buffering bottom surface 34, the buffering ring 32 is forced downward to be in close contact with the bottom surface 35 of the buffering installation groove 31, and thus to the buffering bottom surface 34. Oil leakage through the bottom surface 35 is prevented.

In order to achieve this function perfectly, it is preferable to form the upper and lower widths of the buffering installation grooves 31 smaller than the upper and lower widths of the buffering 32.

In addition, since the outer diameter surface 36 of the buffer ring 32 has a larger diameter than the inner diameter surface 37, the hydraulic pressure area is also large, so that when the pressure of the fluid is applied from the vacancy buffer room 24 as described above, The buffer ring 32 is subjected to a force of retraction in the radially inward direction. The contraction of the buffer ring 32 helps to minimize the flow contact surface gap 26a between the buffer ring 32 and the piston 2. .

In order to facilitate this operation and to prepare for radial vibration or deformation of the piston, the buffer ring 32 is formed so that a sufficient space 38 is formed between the buffered outer diameter surface 33 and the buffering installation groove 31. It is preferable to form the upper and lower height h of the lower than the upper and lower height H of the buffering installation groove 31.

On the other hand, in the present invention, since the fluid inside the vacant buffer room 24 does not flow toward the drain oil chamber 27 by installing and using the above-mentioned gating buffer ring 32, it is shown in FIG. 7 and FIG. As described above, most of the fluid in the vacant shock chamber 24 exits the buffer chamber upper gap 25. As described above, the flow in the buffer chamber upper gap 25 is a shear flow and a lateral flow. Since these are opposite to each other, the fluid in the vacancy buffer room 24 is hard to escape.

Therefore, since the back pressure generated in the vacant shock buffer 24 is formed high, the braking characteristic is improved by applying a greater force to the piston lower pressure receiving surface 15.

In addition, the flow rate exited to the upper gap 25 of the buffer chamber is returned to the lower cylinder chamber 7 or the high pressure flow path 13, thereby reducing the flow rate loss of the breaker and increasing the efficiency.

On the other hand, since the high pressure is applied to the buffer ring 32 to operate as described above, the strength of the material itself to withstand high pressure, and the relative movement with the piston (2) should be excellent in wear characteristics.

Therefore, when using the buffering of a single material as shown in Figure 3, it can be made using high-strength and excellent wear resistance engineering plastics or composite materials, and the like of the present invention shown in Figure 4 As in another embodiment, a double structure of the buffering to combine the sliding 39 made of a material having excellent wear resistance to the buffering body (32a) made of a high-strength material in a concave-convex shape to form one complete buffering.

5 is a further embodiment of the present invention, the buffer ring 32 to the inner diameter surface 37 and the outer diameter surface (3) in the buffer ring to help lubrication of the inner diameter surface 37 in flow contact with the piston (2) By forming a lubricating oil chamber 41 in the lubricating oil passage 40 and the buffering inner diameter surface 37 penetrating through 36, the buffer ring 32 and the piston are formed in the buffering flow contact surface gap 26a when the piston is in fluid contact. The lubricant film is made thicker to prevent damage to the piston 2 and the buffering 32.

As described above, the breaker piercing buffer device according to the present invention further forms a buffering installation groove 31 between the passages through which fluid flows from the vacancy buffer room 24 to the drain oil chamber 27, and installs the buffering device. By inserting the buffer ring 32 into the groove 31, when the piston is struck, the back pressure is applied to prevent the oil from being easily drained from the vacancy buffer chamber 24 toward the drain oil chamber 27, thereby lowering the piston. Since it is possible to actively prevent the braking characteristics of the piston is improved.

As a result, even when the hydraulic breaker is idle, the breaker internal parts are not damaged and the breaker life is extended.

Claims (4)

The piston 2 is installed in the cylinder 1 so that the piston 2 can move freely up and down, and the high pressure and low pressure oil pressure is selectively applied to the cylinder lower chamber 7 and the cylinder upper chamber 6 provided at the upper and lower ends of the piston 2. The piston descends at a high speed due to the force generated by the pressure difference and the gas of the compression gas chamber 5 provided at the upper end of the piston as it is compressed according to the upward movement of the piston. While the piston is to strike the chisel (3) installed at the bottom, while the piston does not impact the chisel (3), when the ball is operated, the air stiffness room for reducing the impact of the piston hit by applying back pressure to the piston (2) (24) is provided with a hydraulic shock absorber of the shock absorber, drain oil for trapping and draining the air discharge buffer room 24 and the fluid drained in the air shock buffer room 24 to the low pressure line A buffering installation groove 31 is formed in the middle between the seals 27, and the buffering installation of the hydraulic breaker, characterized in that the buffer ring 32 is formed in a structure installed in the buffering installation groove (31). The method of claim 1, wherein the vertical height (h) of the buffer ring 32 is smaller than the vertical height (H) of the buffering installation groove 31, characterized in that the hydraulic breaker. The buffer ring (32) of claim 1, wherein the buffer ring (32) consists of a buffering body (32a) made of a high-strength material and a slide ring (39) made of a material having excellent abrasion resistance, and the sliding ring (39) of the buffering body (32a). Hydraulic breaker ball shock absorber, characterized in that coupled to the inner surface of the concave-convex shape. The lubricating oil path 40 penetrating the inner diameter surface 37 and the outer diameter surface 36 is formed in the buffer ring 32, and the lubricating oil loss 41 is formed in the buffering inner diameter surface 37. Hydraulic breaker ball shock absorber, characterized in that formed.