Hydraulic breaking hammer of static pressure suspension type

Abstract

This invention discloses a hydrostatic suspension type hydraulic breaker, including a piston (3) and a cylinder (4). The piston (3) reciprocates within the cylinder (4). The piston (3) is composed of a suspension sleeve (18) and an impact rod (19). The suspension sleeve (18) is coaxially mounted on the impact rod (19). Two rings of hydrostatic suspension chambers (21) are provided on the suspension sleeve (18), and ≥3 hydrostatic suspension chambers (21) are provided at equal intervals in each ring to support the piston (3). The piston (3) is floated in the cylinder (4) by the hydrostatic suspension support. The mating surfaces of the piston (3) and the cylinder (4) are separated by hydraulic oil to avoid contact and prevent damage.

Description

Technical Field

[0001] This invention relates to an engineering machinery attachment, and more particularly to a hydrostatic suspension type hydraulic breaker. Background Technology

[0002] A hydraulic breaker is an impact tool that converts hydraulic energy into mechanical energy. It has two basic moving elements—a piston and a directional valve—which are mutually controlled through feedback. The reciprocating motion of the valve core controls the piston's direction, and at the beginning and end of each stroke, the piston, through the opening or closing of the directional valve's control oil circuit, reverses the valve core's direction, thus creating a cyclical operation. The basic working principle of a hydraulic breaker is as follows: through this feedback control of the piston and valve core, the piston achieves rapid reciprocating motion under hydraulic or hydraulic-pneumatic pressure, striking the chisel to perform work.

[0003] Hydraulic breakers can be attached to various machines, such as excavators, backhoes, or other similar machines, for breaking stone, concrete, and other building materials. The hydraulic breaker is mounted on the machine's boom and connected to a hydraulic system. High-pressure fluid from the hydraulic system is supplied to the hydraulic breaker to drive a piston that reciprocates in contact with the workpiece, striking the workpiece to complete the breaking task.

[0004] Existing hydraulic breaker hammer core ( Figure 1 , Figure 2 The main components include: 1. Nitrogen chamber; 2. Piston rings; 3. Piston; 4. Cylinder block; 5. Chisel holder; 6. Inner sleeve; 7. Outer sleeve; 8. Chisel; 9. Reversing valve; 10. Accumulator. The return stroke begins... Figure 1High-pressure oil P enters the front chamber 12 through oil port a4 and acts on the lower end of the valve core of the reversing valve 9, so that the valve core is stably in the state shown in Figure (1). At this time, the front chamber 12 is connected to high-pressure oil P, and the rear chamber 13 is connected to return oil T through oil port a1. Under the drive of high-pressure oil P in the front chamber 12, the piston 3 accelerates its return stroke and compresses the nitrogen in the nitrogen chamber 1 to store energy (if the nitrogen chamber 1 is not filled with gas, it is a pure hydraulic hammer). The accumulator 10 stores oil. When the piston 3 returns to the front chamber 12 and the control oil port a3, the high-pressure oil P reaches the upper end of the valve core. At this time, the upper and lower ends of the valve core are connected to the high-pressure oil. Since the effective area of ​​the upper end of the valve core is larger than the effective area of ​​the lower end in the design, the valve core is reversed to the state shown in Figure (2) under the action of high-pressure oil. At this time, the front and rear chambers are connected to high-pressure oil P. The accumulator 10 discharges oil to supplement the hydraulic system. Under the action of nitrogen pressure (except for pure hydraulic hammer) and oil pressure, the piston 3 accelerates its stroke, strikes the chisel 8, and outputs impact energy. When piston 3 passes the impact point, control ports a2 and a3 are connected and connected to the return oil T. The upper end of the valve core of the reversing valve 9 is depressurized, and the lower end of the valve core is quickly reversed to the state shown in Figure (1) under the action of oil pressure, and then returns to the initial state. Piston 3 begins to return and enters the next impact cycle, and so on. In the drill rod seat 5, there is a drill rod 8 for breaking rocks, an inner sleeve 6 and an outer sleeve 7 that play a guiding role. At the same time, the inner sleeve 6 and the outer sleeve 7 have the function of protecting the drill rod seat 5 from wear.

[0005] Due to wear, clearances, dimensional accuracy of the parts, and operating conditions during the use of the hydraulic breaker, the striking surfaces of piston 3 and chisel 8 are not perpendicular to the axis of piston 3 (impact: relative sliding), and the striking point is not at the center of piston 3 (impact: deflection tendency). After piston 3 strikes chisel 8, radial impact (lateral impact) is inevitable. The radial impact force and friction will damage the mating surface between piston 3 and cylinder 4 (i.e., cylinder scoring). Since piston 3 and cylinder 4 are sealed by a clearance, damage to the mating surface increases internal leakage, preventing the hydraulic breaker from working properly. Damage to the surface of piston 3 will also damage the coaxially mounted oil seal, leading to oil leakage.

[0006] The book "Design Theory, Calculation Methods and Applications of Hydraulic Breakers," edited by Yang Xiangbi and Luo Ming, describes the cylinder scoring problem on page 6. Cylinder scoring is a technical problem that people have long sought to solve but have yet to achieve success in.

[0007] To address the issue of cylinder scoring, Chinese invention patent CN106703105B discloses a hydrostatic support and lubrication structure for a hydraulic breaker piston. The technical solution involves four equally spaced oil chambers circumferentially arranged in the area where the cylinder body and piston head mate to support the piston head; hydraulic oil enters these chambers through oil passages within the cylinder body. Similarly, four equally spaced oil chambers circumferentially arranged at the piston's maximum diameter (near the tail section) provide support at this point; hydraulic oil enters these chambers through axial and radial holes inside the piston. The problem is that when overload, contaminated hydraulic oil, or other factors cause scoring on the mating surfaces of the four oil chambers at the piston's maximum diameter and the cylinder body, the sealing surfaces around the oil chambers (including circumferential and axial sealing surfaces) lose their sealing function, compromising the supporting force of the oil chambers on the piston, exacerbating the scoring, and ultimately rendering the piston unusable. 2. The presence of axial, radial, and oil chambers on the piston inevitably reduces its mechanical strength. However, the piston's reciprocating motion impacts the chisel, subjecting it to immense impact force, making it prone to damage (the piston's high hardness makes it easily broken). 3. The axial and radial oil chambers on the piston are both long and narrow, making machining difficult, inefficient, and inconvenient for cleaning and maintenance. 4. With four oil chamber supports at the piston's maximum diameter, these chambers will exert hydraulic pressure on the cylinder in four directions, causing cylinder deformation. Since the piston and cylinder are sealed by a small clearance, this deformation will lead to piston seizure and damage, i.e., cylinder scoring. To reduce deformation, the cylinder's structural dimensions and weight must be increased, requiring a high-tonnage main engine. Increasing the main engine's tonnage without increasing efficiency is a waste of resources. 5. During the piston's reciprocating motion, when the four oil chambers at the piston's maximum diameter (near the tail) are connected to the annular oil groove in the cylinder, there is no support at this stage. 6. Insufficient buffering distance and leakage in the buffer chamber caused the piston to strike the drill rod seat. 7. If a capillary tube is directly machined onto the piston as a throttling orifice to supply oil to the oil chamber, existing machining methods would struggle to meet the capillary tube's requirements for diameter (micro-orifice), length (determined by the piston diameter), dimensional accuracy, and surface roughness. If a throttling orifice is installed, it would inevitably increase connecting threads, further reducing the piston's strength and making it prone to loosening (due to high-frequency vibration and temperature changes). Once loosened, cylinder scoring would occur. Summary of the Invention

[0008] The technical problem to be solved by the present invention in view of the above-mentioned prior art is as follows.

[0009] 1. Scoring of the mating surfaces of the four oil chambers on the piston's maximum diameter and the cylinder block caused the entire piston to be scrapped.

[0010] 2. Machining the four oil chambers on the piston's maximum diameter requires placing the entire piston on a four-axis linkage machine tool, which places high demands on the machine tool.

[0011] 3. The installation of axial oil passages, radial oil passages, oil chambers, etc. on the piston can lead to piston breakage.

[0012] 4. The piston has axial and radial oil passages, both of which are narrow holes, making machining difficult and resulting in low production efficiency.

[0013] 5. The hydraulic pressure in the oil chamber causes the cylinder block to deform and the piston to seize up, which inevitably leads to cylinder scoring.

[0014] 6. The four oil chambers on the piston's maximum diameter are connected to the annular oil groove in the cylinder, resulting in a lack of support.

[0015] 7. Directly machining a capillary tube onto the piston cannot meet the requirements for use as a throttling orifice.

[0016] 8. Problem of piston striking the drill rod seat.

[0017] To solve the above-mentioned technical problems, this invention provides a hydrostatic suspension type hydraulic breaker. It includes: a piston, a cylinder, a chisel holder, an inner sleeve, an outer sleeve, and a chisel. The piston reciprocates within the cylinder, striking the chisel. The chisel holder houses the chisel for rock breaking, the inner sleeve, and the outer sleeve, which also protect the chisel holder from wear. The piston consists of a suspension sleeve and an impact rod. The suspension sleeve is coaxially mounted on the impact rod with an interference fit of 0.002mm–0.08mm. (During piston operation, the suspension sleeve experiences a maximum axial force directed towards the piston head, the magnitude of which is the resultant force of inertial force and hydraulic pressure in the rear chamber. Axial forces in other states are much smaller than the maximum axial force. Under maximum axial force, the impact rod provides positioning via a step, making the interference fit between the suspension sleeve and impact rod reasonable. Furthermore, the interference fit effectively prevents deformation of the suspension sleeve due to hydraulic pressure.) When the suspension sleeve is damaged, it is replaced, preventing the entire piston from being scrapped.

[0018] As a further improvement of the present invention, two rings of hydrostatic suspension chambers are provided on the suspension sleeve, with ≥3 hydrostatic suspension chambers evenly spaced in each ring, for supporting the piston. High-pressure oil P enters the hydrostatic suspension chambers after being throttled through the capillary tube on the suspension sleeve. The piston is floated in the cylinder by the hydrostatic suspension support, ensuring that the piston and the cylinder body mating surfaces are separated by hydraulic oil under a certain load and at any speed (including when stationary), avoiding contact and damage. The principle of the hydrostatic suspension support: High-pressure oil enters the hydrostatic suspension chamber (referred to as: oil chamber) after being throttled through the capillary tube. When the piston is not under load (e.g., ignoring its own weight), the oil pressure in each oil chamber is the same, maintaining balance, and the piston is in the center of the cylinder bore. At this time, the gap between the sealing surface of each oil chamber and the piston is the same (h); if a radial load F is applied to the piston (e.g., considering the piston's own weight), the piston will generate an eccentricity e. At this point, the gap between the piston and cylinder in the load direction (e.g., the direction of gravity) decreases to he, while the gap on the opposite side of the load increases to h+e. Because the resistance is greater where the gap is smaller, the flow rate decreases, thus reducing the pressure drop through the capillary tube. Since the oil supply pressure in each hydrostatic suspension chamber is the same (constant), the pressure in that chamber will increase. Conversely, on the opposite side of the load, because the resistance is smaller where the gap is larger, the flow rate increases, thus increasing the pressure drop through the capillary tube, and therefore reducing the pressure in that chamber. This pressure difference change balances the external load. For example, if the effective radial bearing area of ​​the oil chamber is A, and ΔP is the pressure difference between the two oil chambers, then F = ΔP × A. As the eccentricity e increases, ΔP will further increase, suspending the piston within the cylinder.

[0019] Beneficial effects: Two rings of hydrostatic suspension chambers are set on the suspension sleeve, with ≥3 hydrostatic suspension chambers evenly spaced in each ring, for piston support. High-pressure oil P enters the hydrostatic suspension chambers after being throttled through the capillary tubes on the suspension sleeve. This avoids the piston breakage caused by directly setting axial oil passages, radial oil passages, oil chambers, etc. on the piston; it solves the problem that existing machining methods are difficult to meet the requirements of capillary tube diameter (micro-hole), length (determined by piston diameter), dimensional accuracy, and surface roughness when directly machining capillary tubes on the piston; it avoids the problem of machining oil chambers on the piston's maximum diameter, requiring the entire piston to be placed on a four-axis linkage machine tool, reducing the requirements for machine tools, improving production efficiency, and reducing production costs.

[0020] As a further improvement of the present invention, the adjacent two rings of hydrostatic suspension cavities are staggered in their projections on a plane perpendicular to the piston axis, and the interval or overlap between adjacent projections is the same.

[0021] Beneficial effect: It can avoid the technical defect of uneven distribution of hydraulic pressure in the cylinder body bore, which leads to severe deformation of the cylinder body and piston seizure.

[0022] As a further improvement of the present invention, the circumferential oil sealing surfaces of two adjacent hydrostatic suspension cavities overlap or partially overlap in projection onto a plane perpendicular to the piston axis.

[0023] Beneficial effects: When high-pressure oil passes through the sealing surface of the hydrostatic suspension chamber, a pressure decrease phenomenon will occur. By adopting the layout described in this technical solution, the amount of overlap of the projections of two adjacent hydrostatic suspension chambers in the plane perpendicular to the piston axis is further limited. This ensures that the resultant force of the hydraulic pressure on all hydrostatic suspension chambers in the plane perpendicular to the piston axis is basically the same in magnitude and distributed radially around the inner bore of the cylinder. In other words, the hydraulic pressure on the cylinder in the plane perpendicular to the piston axis is basically the same, thus preventing the hydraulic pressure from pressing the inner bore of the cylinder and piston into a non-circular hole.

[0024] As a further improvement of the present invention, an annular groove is provided on the impact rod for supplying oil to the hydrostatic suspension chamber on the suspension sleeve. The annular groove is connected to the end face with the largest diameter near the head through a hole.

[0025] Beneficial effects: It avoids the problem of piston breakage caused by setting too many oil passages on the piston; since the hole connecting the annular groove and the end face of the piston with the largest diameter near the head is only used for oil supply to the oil chamber of the suspension sleeve, and the oil needs to pass through the capillary tube with a small flow rate, the hole diameter is small and there are no requirements for dimensional accuracy or roughness, which makes it easy to process.

[0026] As a further improvement of the present invention, when the piston is at its lowest point (near the drill rod seat), the static pressure suspension chamber on the suspension sleeve and the annular oil groove in the cylinder that communicates with port a2 are prevented from communicating.

[0027] Beneficial effect: Prevents damage to the hydrostatic suspension support of the piston.

[0028] As a further improvement of the present invention, when the piston is at its uppermost position (in the direction of the nitrogen chamber), the static pressure suspension chamber on the suspension sleeve and the rear chamber 13 are prevented from communicating.

[0029] Beneficial effect: Prevents damage to the hydrostatic suspension support of the piston.

[0030] As a further improvement of the present invention, the inner diameter of the suspension sleeve is larger than the diameter of the piston tail, which facilitates installation and disassembly.

[0031] As a further improvement of the present invention, in order to increase the volume of the nitrogen chamber and increase energy storage, a cavity is provided at the tail of the piston.

[0032] As a further improvement of the present invention, a replenishing valve is provided between the buffer chamber and the high-pressure oil P. The replenishing valve includes a replenishing valve core, a replenishing valve sleeve, and a replenishing valve cover. Before the piston enters the buffer chamber, the replenishing valve core is in a floating state; when the piston enters the buffer chamber, the replenishing valve core closes the replenishing valve under the action of the liquid hammer effect; when the pressure in the buffer chamber is lower than the pressure of the high-pressure oil P, the replenishing valve opens and replenishing oil begins.

[0033] Beneficial effect: The use of a replenishing valve to replenish oil to the buffer chamber avoids the phenomenon of the piston striking the drill rod seat due to insufficient buffer distance and leakage in the buffer chamber. Attached Figure Description

[0034] Figure 1 Existing hydraulic breaker schematic diagram.

[0035] Figure 2 Existing hydraulic breaker schematic diagram.

[0036] Figure 3 Front view of the piston of an existing hydraulic breaker.

[0037] Figure 4 A piston structure diagram according to an embodiment of the present invention.

[0038] Figure 5 Structural diagram of the suspension sleeve.

[0039] Figure 6 Sectional view CC of the suspension sleeve.

[0040] Figure 7 Sectional view DD of the suspension sleeve.

[0041] Figure 8 Schematic diagram of the hydraulic breaker of this invention.

[0042] Figure 9 Schematic diagram of the hydraulic breaker of this invention.

[0043] Figure 10 Diagram showing the oil replenishment valve in the closed state.

[0044] Figure 11 Diagram showing the oil replenishment valve in open position.

[0045] Figure labels: 1 Nitrogen chamber 2 Piston ring 3 Piston 4 Cylinder block 5 Drill rod seat 6 Inner sleeve 7 Outer sleeve 8 Drill rod 9 Reversing valve 10 Accumulator 11 Main seal 12 Front chamber 13 Rear chamber 14 Head 15 Maximum diameter 16 Tail 17 Large front section 18 Suspension sleeve 19 Impact rod 20 Capillary tube 21 Static pressure suspension chamber 22 Circumferential oil sealing surface 23 Axial oil sealing surface 24 Annular groove 25 Hole 26 Lubrication groove 27 Oil replenishing valve 28 Oil replenishing valve cover 29 Oil replenishing valve core 30 Oil replenishing valve sleeve 31 Buffer chamber Implementation

[0046] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings.

[0047] This invention provides a hydrostatic suspension type hydraulic breaker, mainly comprising: a piston 3, a cylinder 4, a chisel holder 5, an inner sleeve 6, an outer sleeve 7, and a chisel 8. The piston 3 reciprocates within the cylinder 4, striking the chisel 8. The chisel holder 5 houses the chisel 8 for rock breaking, the inner sleeve 6, and the outer sleeve 7, which serve as guides. Simultaneously, the inner sleeve 6 and outer sleeve 7 protect the chisel holder 5 from wear. Figure 4 The piston 3 consists of a suspension sleeve 18 and an impact rod 19. The suspension sleeve 18 is coaxially mounted on the impact rod 19 with an interference fit of 0.002mm–0.08mm. (During the operation of the piston 3, the suspension sleeve 18 experiences a maximum axial force directed towards the head 14 of the piston 3, the magnitude of which is the resultant force of inertia and hydraulic pressure in the rear chamber 13. Axial forces in other states are much smaller than the maximum axial force. When subjected to the maximum axial force, the piston is positioned by a step on the impact rod 19. Therefore, the interference fit between the suspension sleeve 18 and the impact rod 19 is reasonable. Furthermore, the interference fit effectively prevents deformation of the suspension sleeve 18 due to hydraulic pressure.) If the suspension sleeve 18 is damaged, it should be replaced to prevent the entire piston 3 from being scrapped.

[0048] As a further improvement to the present invention, such as Figure 4 , Figure 5 , Figure 6 , Figure 7As shown, two rings of hydrostatic suspension chambers 21 are provided on the suspension sleeve 18, with ≥3 hydrostatic suspension chambers 21 evenly spaced in each ring (Note: In this embodiment, 6 hydrostatic suspension chambers 21 are evenly spaced in each ring) to support the piston 3. High-pressure oil P enters the hydrostatic suspension chambers 21 after being throttled through the capillary tube 20 on the suspension sleeve 18. The hydrostatic suspension support floats the piston 3 in the cylinder 4, ensuring that the mating surfaces of the piston 3 and the cylinder 4 are separated by hydraulic oil under a certain load and at any speed (including when stationary), avoiding contact and damage. The principle of the hydrostatic suspension support: High-pressure oil enters the hydrostatic suspension chambers 21 (referred to as: oil chambers) after being throttled through the capillary tube 20. When the piston 3 is not under load (e.g., ignoring its own weight), the oil pressure in each oil chamber is the same, maintaining balance, and the piston 3 is in the center of the hole in the cylinder 4. At this point, the gaps between the sealing surfaces of each oil chamber (including the circumferential sealing surface 22 and the axial sealing surface 23) and the piston 3 are the same (both are h). If a radial load F is applied to the piston 3 (e.g., considering the piston's own weight), the piston 3 will generate an eccentricity e. At this point, the gap between the piston 3 and the cylinder 4 decreases to he in the load direction (e.g., the direction of gravity), and increases to h+e on the opposite side of the load. Since the resistance is greater when the oil flows through the smaller gap, the flow rate decreases, and thus the pressure drop through the capillary tube 20 decreases. The oil supply pressure of each static pressure suspension chamber 21 is the same (constant), so the pressure of that oil chamber will increase. Conversely, on the opposite side of the load, since the resistance is smaller when the oil flows through the larger gap, the flow rate increases, and thus the pressure drop through the capillary tube 20 increases, so the pressure of that oil chamber will decrease. This pressure difference change can balance the external load. For example, if the effective radial bearing area of ​​the oil chamber is A, and ΔP is the pressure difference between the two oil chambers, then F = ΔP × A. As the eccentricity e increases, ΔP will further increase, suspending the piston 3 in the cylinder 4.

[0049] As a further improvement to the present invention, such as Figure 5 , Figure 6 , Figure 7 As shown, the projections of two adjacent static pressure suspension cavities 21 onto a plane perpendicular to the axis of piston 3 are staggered, and the interval or overlap between adjacent projections is the same.

[0050] As a further improvement to the present invention, such as Figure 5 , Figure 6 , Figure 7 As shown, the circumferential oil sealing surfaces 22 of two adjacent hydrostatic suspension chambers 21 overlap or partially overlap on the plane perpendicular to the axis of piston 3.

[0051] As a further improvement to the present invention, such as Figure 4 As shown, an annular groove 24 is provided on the impact rod 19 for supplying oil to the hydrostatic suspension chamber 21 on the suspension sleeve 18. The annular groove 24 is connected to the end face of the maximum diameter 15 near the head 14 through the hole 25.

[0052] As a further improvement to the present invention, such as Figure 4 As shown, a lubrication groove 26 is provided on the large front section 17 of the piston 3.

[0053] As a further improvement to the present invention, such as Figure 8 As shown, when piston 3 is at its lowest point (near the chisel seat 5), it prevents the static pressure suspension chamber 21 on the suspension sleeve 18 from communicating with the annular oil groove in the cylinder 4 that communicates with port a2, i.e., L1>0.

[0054] As a further improvement to the present invention, such as Figure 9 As shown, when piston 3 is at its highest point (near nitrogen chamber 1), the static pressure suspension chamber 21 on suspension sleeve 18 is prevented from communicating with the rear chamber 13, i.e., L2>0.

[0055] As a further improvement to the present invention, such as Figure 4 The inner diameter of the suspension sleeve 18 is larger than the diameter of the tail portion 16 of the piston 3.

[0056] As a further improvement to the present invention, such as Figure 4 As shown, in order to increase the volume of the nitrogen chamber 1 and increase energy storage, a cavity is provided on the tail 16 of the piston 3.

[0057] As a further improvement to the present invention, such as Figure 9 As shown, a replenishing valve 27 is installed between the buffer chamber 31 and the high-pressure oil P. The replenishing valve 27 includes a replenishing valve cover 28, a replenishing valve core 29, and a replenishing valve sleeve 30. Before the piston 3 enters the buffer chamber 31, the replenishing valve core 29 is in a floating state (the pressure on both ends of the replenishing valve core 29 is equal, and the replenishing valve 27 may be open or closed). When the piston 3 enters the buffer chamber 31, the replenishing valve core 29 closes the replenishing valve 27 under the action of the hydraulic hammer effect, as shown. Figure 10 As shown; when the pressure in the buffer chamber 31 is lower than the pressure of the high-pressure oil P, the oil replenishment valve 27 opens, and oil replenishment begins, as shown. Figure 11 As shown.

[0058] This invention is not limited to the above-described embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the protection scope of this invention.

Claims

1. A hydrostatic suspension type hydraulic breaker, comprising a piston (3) and a cylinder (4), wherein the piston (3) reciprocates within the cylinder (4), characterized in that: The piston (3) is composed of a suspension sleeve (18) and an impact rod (19). The suspension sleeve (18) is coaxially mounted on the impact rod (19) and is an interference fit. Two rings of static pressure suspension chambers (21) are set on the suspension sleeve (18), and ≥3 static pressure suspension chambers (21) are set at equal intervals in each ring to support the piston (3). High pressure oil enters the static pressure suspension chamber (21) after being throttled through the capillary tube (20) on the suspension sleeve (18). The projections of two adjacent rings of static pressure suspension chambers (21) on the plane perpendicular to the axis of the piston (3) are staggered, and the interval or overlap between adjacent projections is the same. The circumferential oil sealing surfaces (22) of two adjacent rings of static pressure suspension chambers (21) on the plane perpendicular to the axis of the piston (3) overlap or partially overlap.

2. The hydrostatic suspension type hydraulic breaker according to claim 1, characterized in that: An annular groove (24) is provided on the impact rod (19) for supplying oil to the hydrostatic suspension chamber (21) on the suspension sleeve (18). The annular groove (24) is connected to the end face of the maximum diameter (15) near the head (14) through the hole (25).

3. The hydrostatic suspension type hydraulic breaker according to claim 1, characterized in that: Avoid the static pressure suspension cavity (21) and the rear cavity (13) on the suspension sleeve (18) from communicating.

4. The hydrostatic suspension type hydraulic breaker according to claim 1, characterized in that: A cavity is provided at the tail (16) of the piston (3).

5. A hydrostatic suspension type hydraulic breaker according to claim 1, characterized in that: A replenishing valve (27) is set between the buffer chamber (31) and the high-pressure oil P. The replenishing valve (27) includes a replenishing valve cover (28), a replenishing valve core (29), and a replenishing valve sleeve (30). Before the piston (3) enters the buffer chamber (31), the replenishing valve core (29) is in a floating state, that is, the pressure on both ends of the replenishing valve core (29) is equal, and the replenishing valve (27) may be open or closed. When the piston (3) enters the buffer chamber (31), the replenishing valve (27) closes. When the pressure in the buffer chamber (31) is lower than the pressure of the high-pressure oil P, the replenishing valve (27) opens and begins to replenish oil.

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