CN211421210U

CN211421210U - Hydraulic breaking hammer structure

Info

Publication number: CN211421210U
Application number: CN201922175555.0U
Authority: CN
Inventors: 罗斌; 邱东峰
Original assignee: Ma'anshan Anrui Machinery Co ltd
Current assignee: Anhui Anrui Intelligent Construction Machinery Co.,Ltd.
Priority date: 2019-12-08
Filing date: 2019-12-08
Publication date: 2020-09-04
Anticipated expiration: 2029-12-08

Abstract

The utility model discloses to the phenomenon that hydraulic hammer piston and cylinder body fitting surface are easily pulled, the oil blanket is short-lived, provide a hydraulic breaking hammer structure. The hydraulic hammer is characterized in that an annular oil return groove (14) is additionally arranged between a buffer ring (13) and an oil seal (15), and an annular oil return groove (14) is arranged between the two oil seals (15); a lubricating groove (12) is arranged at the matching surface of the front oil groove (20) with the largest diameter of the piston (4) and the cylinder body (3), the distance from the lubricating groove (12) to the lower cavity (C) is 40-50 mm, and the width of the lubricating groove (12) is 20-30 mm; an annular oil reservoir (19) is provided on the mating surface of the piston ring (2) and the piston (4). The oil return effectively reduces the damage of the hydraulic pulsation to the sealing ring caused by the piston in the process of impacting the drill rod, and effectively prolongs the service life; the oil supplementing structure effectively increases the oil quantity between the piston and the cylinder body, avoids the phenomenon of poor lubrication, and can effectively relieve cylinder drawing of the hydraulic hammer.

Description

Hydraulic breaking hammer structure

Technical Field

The utility model relates to an engineering machine tool accessory especially relates to a hydraulic breaking hammer structure.

Background

To break stone, concrete and other building materials, the hydraulic hammer may be attached to various machines, such as an excavator, a backhoe or other similar machines. The hydraulic hammer is mounted to the arm of the machine and is connected to a hydraulic system. High pressure fluid in the hydraulic system is supplied to the hydraulic hammer to drive a piston in contact with the work tool to reciprocate and strike the work tool, completing the crushing task.

The hammer core of the existing hydraulic breaking hammer mainly comprises: nitrogen chamber 1, piston ring 2, cylinder 3, piston 4, drill rod seat 5, inner sleeve 6, drill rod 7, outer sleeve 8, valve group 9, accumulator 10, flat pin 11, etc. The nitrogen chamber 1, the piston ring 2 (including a sealing element thereon), the cylinder body 3 and the piston 4 form a closed space A (a nitrogen storage chamber), nitrogen is filled into the space A (the inside of the nitrogen chamber 1), the piston 4 moves upwards to compress the nitrogen along with the storage and release of the nitrogen energy in the space A in the process of the piston 4 moving back and forth along the axial direction, the energy is stored, the piston 4 moves downwards, the hydraulic pressure and the nitrogen do work together, and the piston 4 is pushed to strike the drill rod 7 to finish the crushing task; the cylinder body 3, the piston 4 and the piston ring 2 (including a sealing element thereon) form a closed space (an upper cavity B), and the upper cavity B intermittently connects high pressure and oil return under the control of the valve group 9; the cylinder 3, the piston 4 and the sealing rings at the position D (main sealing area) form a closed lower cavity C, and the lower cavity C is communicated with an oil supply system of a host and is in a normal-pressure and high-pressure state; in the drill rod seat 5, a drill rod 7 for breaking rock, an outer sleeve 8 for guiding, a flat pin 11 for limiting the drill rod 7 and an inner sleeve 6 for limiting and guiding are arranged, and the inner sleeve 6 and the outer sleeve 8 have the function of protecting the drill rod seat 5 from being abraded.

Because the piston 4 and the cylinder body 3 are sealed by a gap, the surface of the kinematic pair is easy to be scratched in the reciprocating motion process of the piston, the hydraulic hammer cannot normally work after the scratch, the cylinder body 3 must be reground to form an inner hole matched with the piston 4, and the piston 4 is scrapped.

Regrinding the cylinder block 3 causes the following problems: in order to ensure the fit clearance, an enlarged piston and an oil seal are needed (the sealing ring in the area D cannot use standard parts and is not universal, and the operation cost is increased).

The cylinder body 3 is scrapped (because the low carbon steel material adopted by the cylinder body 3 needs to be carburized, the surface hardness is increased, secondary grinding is carried out after strain so that the carburized layer becomes thin or the hardness is reduced, and once the matching surface has insufficient hardness, the cylinder body is scrapped).

The cylinder body strain is the main reason for scrapping the large hydraulic hammer cylinder body, which is the common fault of the large hydraulic hammer, wastes manpower, financial resources and resources, and increases the construction cost.

Because piston 4 reciprocating motion strikes drill rod 7, will cause hydraulic system's pressure unstable certainly for oil blanket buffer ring and the oil blanket of main seal D department bear different pressure, make life-span reduction, the oil leak.

Disclosure of Invention

The utility model discloses to the hydraulic hammer piston and the easy strain of cylinder body fitting surface, the fragile phenomenon of oil blanket provides a novel hydraulic pressure quartering hammer structure.

Structure of primary seal D region: an annular oil return groove is additionally arranged between the buffer ring and the oil seal, and the oil return groove is directly communicated with the oil return of the main machine, so that pressure change caused by rapid change of speed when the piston impacts the drill rod is avoided, oil passing through the buffer ring can be discharged in time, and the oil seal is prevented from being damaged by pressure rise; set up one annular oil gallery between twice oil blanket, the effect of this oil gallery is lubricated and prevents that the oil blanket from losing sealing effect because the effect of backpressure, if do not add this structure, oilless or the too high phenomenon of oil pressure accumulation can appear between the twice oil blanket, under the oilless condition, dry friction between oil blanket and the piston, wearing and tearing are serious, calorific capacity is big, reduce life, the too high condition of backpressure can make the pressure differential of oil blanket left and right sides be close, make the oil blanket to the power of hugging closely of piston reduce, lose sealing effect, lead to the oil leak.

The phenomenon of poor lubrication is inevitably caused due to the high-speed reciprocating motion of the piston, an annular lubrication groove is arranged at the matching surface of the front oil groove with the maximum diameter of the piston and the middle cylinder, the lubrication groove is communicated with the lower cavity of the hydraulic hammer and is in a normal high pressure state, the phenomenon of poor lubrication caused by the quick reciprocating motion of the piston is avoided, and cylinder pulling can be effectively relieved.

Because the sealing elements on the piston ring are more, and the surface of the piston is smooth, dry friction between the sealing element and the piston is easily caused, and the sealing element is damaged, an annular oil storage groove is arranged on the surface where the piston ring is matched with the piston and used for lubricating, reducing abrasion and generating heat.

Drawings

Fig. 1 shows a hydraulic breaker.

Fig. 2 is a partially enlarged view of the hydraulic breaking hammer.

FIG. 3 is a schematic illustration of a piston ring assembly construction.

Fig. 4 is a piston structure view.

Detailed Description

Embodiments of the present invention will be described in detail with reference to the accompanying drawings.

Description of some reference numerals:

1 nitrogen chamber 2 piston ring 3 cylinder 4 piston 5 drill rod seat 6 internal sleeve 7 drill rod 8 external sleeve 9 valve bank 10 energy accumulator 11 flat pin 12 lubrication groove 13 buffer ring 14 oil return groove 15 oil seal 16 gas seal 17 steckel 18O-ring 19 oil storage groove A nitrogen gas storage chamber B upper chamber C lower chamber D main seal area.

Structure of primary seal D region: an annular oil return groove 14 is additionally arranged between the buffer ring 13 and the oil seal 15, the oil return groove 14 is directly communicated with the oil return of a host, so that the pressure change caused by the rapid change of the speed when the piston 4 impacts the drill rod 7 is avoided, the oil passing through the buffer ring 13 can be discharged in time, and the oil seal 15 is prevented from being damaged by the pressure rise; set up one annular oil gallery 14 between twice oil blanket 15, this oil gallery 14's effect is lubricated and prevents oil blanket 15 because the effect of backpressure loses sealing effect, if do not add this structure, oilless or the too high phenomenon of oil pressure accumulation can appear between twice oil blanket 15, under the oilless condition, dry friction between oil blanket 15 and the piston 4, wearing and tearing are serious, calorific capacity is big, reduce life, the too high condition of backpressure can make the pressure differential of the 15 left and right sides of oil blanket approximate, make 15 power of holding tightly to the piston of oil blanket reduce, lose sealing effect, lead to oil leakage.

Because the piston 4 reciprocates at a high speed, poor lubrication is inevitably caused, an annular lubrication groove 12 is arranged at the matching surface of the front oil groove 20 with the largest diameter of the piston 4 and the cylinder body 3, the lubrication groove 12 is communicated with the lower cavity C of the hydraulic hammer and is in a normal high pressure state, the poor lubrication caused by the rapid reciprocating motion of the piston 4 is avoided, and cylinder pulling can be effectively relieved; distance L1 from lubrication groove 12 to lower cavity C (40 < L1< 50), width L2 of lubrication groove 12 (20 < L2< 30).

Because the sealing elements on the piston ring 2 are more and the surface of the piston 4 is smooth, dry friction among the Stent seal 17, the gas seal 16 and the piston 4 is easily caused, and the sealing elements are damaged, an annular oil storage groove 19 is arranged on the matched surface of the piston ring 2 and the piston 4 for lubricating and reducing abrasion and heating.

The hydraulic hammer reduces faults in the working process through a proper oil return and oil supplement structure. The oil return effectively reduces the damage of the hydraulic pulsation to the sealing ring caused by the piston 4 in the process of impacting the drill rod 7, and effectively prolongs the service life; the effectual oil mass that has increased between piston 4 and the cylinder body 3 of benefit oil structure has avoided lubricated bad phenomenon, can effectively alleviate hydraulic hammer and draw the jar.

Claims

1. A hydraulic demolition hammer construction comprising: nitrogen chamber (1), piston ring (2), cylinder body (3), piston (4), drill rod seat (5), endotheca (6), drill rod (7), overcoat (8), valves (9), energy storage ware (10), cotter (11), buffer ring (13), oil blanket (15), atmoseal (16), steckel (17), O type circle (18), its characterized in that: an annular oil return groove (14) is additionally arranged between the buffer ring (13) and the oil seal (15), and an annular oil return groove (14) is arranged between the two oil seals (15); a lubricating groove (12) is arranged at the matching surface of the front oil groove (20) with the largest diameter of the piston (4) and the cylinder body (3), the distance from the lubricating groove (12) to the lower cavity (C) is 40-50 mm, and the width of the lubricating groove (12) is 20-30 mm; an annular oil reservoir (19) is provided on the mating surface of the piston ring (2) and the piston (4).