CN218148613U - Hydraulic breaking hammer capable of achieving idle striking function based on hydraulic hammer effect and damping holes - Google Patents

Abstract

The utility model discloses a hydraulic breaking hammer based on empty function of beating is realized to hydraulic hammer effect and damping hole, include: piston, cylinder body, drill rod seat, endotheca, overcoat and drill rod. The piston reciprocates in the cylinder body to strike the drill rod; the drill rod seat is internally provided with a drill rod for breaking rocks, an inner sleeve and an outer sleeve which play a role in guiding, and the inner sleeve and the outer sleeve have the function of protecting the drill rod seat from being abraded. A floating valve is arranged between the buffer cavity and system high-pressure oil, and the floating valve core realizes the opening and closing of the floating valve by means of a hydraulic hammer effect and pressure difference generated by the damping hole. The problem of the in-process that hydraulic breaking hammer worked must compress tightly the drill rod is solved, the work efficiency of hydraulic breaking hammer has been improved.

Description

Hydraulic breaking hammer capable of achieving idle striking function based on hydraulic hammer effect and damping holes

Technical Field

The utility model relates to an engineering machine tool accessory especially relates to a hydraulic breaking hammer based on empty function of beating is realized to hydraulic hammer effect and damping hole.

Background

The hydraulic breaking hammer is an impact machine for converting hydraulic energy into mechanical energy, and is characterized by that it has two basic moving elements of piston and reversal valve, and they are mutually feedback-controlled, i.e. the reciprocating movement of valve core can control the reversal of piston, and the piston can implement reversal of valve core by means of opening or closing control oil circuit of reversal valve at the beginning and end of every stroke, so that they can implement circular operation. The basic working principle of the hydraulic breaking hammer is as follows: through the feedback control of the piston and the valve core, the piston can rapidly reciprocate under the drive of hydraulic pressure or hydraulic pressure and air pressure, and the drill rod is struck to do work outwards.

To break stone, concrete and other building materials, hydraulic breaking hammers can be attached to various machines, such as excavators, backhoes or other similar machines. The hydraulic breaking 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 breaker hammer to drive a piston in contact with the work tool to reciprocate and strike the work tool, completing the breaking task.

The hammer core (fig. 1 and 2) of the existing hydraulic breaking hammer mainly comprises: nitrogen chamber 1, piston ring 2, piston 3, cylinder 4, drill rod seat 5, inner sleeve 6, outer sleeve 7, drill rod 8, reversing valve 9 and energy accumulator 10. When the return motion starts (fig. 1), the high-pressure oil P of the system enters the front cavity 12 through the 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 fig. 1. At the moment, the front cavity 12 is communicated with system high-pressure oil P, the rear cavity 13 is communicated with an oil return T through an oil port a1, the piston 3 is driven by the system high-pressure oil P in the front cavity 12 to accelerate return stroke and compress nitrogen gas in the nitrogen chamber 1 to store energy (if gas is not filled in the nitrogen chamber 1, a pure hydraulic breaking hammer is adopted), the energy accumulator 10 stores oil, when the piston 3 moves to the front cavity 12 in a return stroke and is communicated with the control oil port a3, the system high-pressure oil P reaches the upper end of the valve core, the upper end and the lower end of the valve core are communicated with the system high-pressure oil at the moment, the valve core is reversed to a state shown in a figure (2) under the action of the high-pressure oil, the front cavity and the rear cavity are communicated with the high-pressure oil P at the moment, the energy accumulator 10 discharges oil to supplement a hydraulic system, and the piston 3 accelerates a stroke and outputs impact energy under the action of the nitrogen pressure (except the pure hydraulic breaking hammer) and the oil pressure. When the piston 3 passes over the striking point, the control ports a2 and a3 are communicated and communicated with the return oil T, the upper end of the valve core of the reversing valve 9 is decompressed, the valve core is quickly reversed to the state shown in the figure (1) under the action of oil pressure at the lower end, the initial state is recovered, the piston 3 starts to return, the next striking cycle is started, and the process is repeated. In the drill rod seat 5, a drill rod 8 for breaking rocks, an inner sleeve 6 and an outer sleeve 7 which play a role in guiding are arranged, and meanwhile, the inner sleeve 6 and the outer sleeve 7 play a role in protecting the drill rod seat 5 from being abraded.

The problems existing in the prior art are as follows: when the maximum diameter of the piston 3 enters the buffer cavity 14 (fig. 3), the hydraulic breaking hammer cannot work at this time because the lower end face of the maximum diameter of the piston 3 does not have high-pressure oil P; before the hydraulic breaking hammer is started, the piston 3 needs to be ejected out of the buffer cavity 14 by the drill rod 8, and the drill rod 8 needs to be in a pressing state in the working process of the hydraulic breaking hammer, so that the piston 3 is prevented from entering the buffer cavity 14, and the hydraulic breaking hammer can continuously work.

Due to the above technical problems, it is difficult to satisfy the following conditions.

(1) For the secondary crushing of the material, the material is subjected to primary crushing (for example, blasting crushing), the weight is light, the volume is small, the material is easy to shift in the process of being pressed by a hydraulic crushing hammer, the material cannot be pressed tightly by a drill rod 8, the piston 3 is difficult to be ejected out of the buffer cavity 14, and the hydraulic crushing hammer cannot work normally; in the work, the material needs to be repeatedly tried to be compacted to complete the crushing operation, and the efficiency is inevitably seriously influenced by the process.

(2) The surface attachment is cleaned and crushed to avoid damaging structures inside the attachment (for example, the rotary cement kiln refractory brick is dismantled, only the refractory brick needs to be crushed to avoid damaging a kiln wall below the refractory brick, and an inner liner of a steel ladle is prevented from being damaged in the process of removing steel slag by the steel ladle).

In order to solve the problem that a drill rod needs to be pressed tightly in the working process of the hydraulic breaking hammer, the specification of the Chinese invention patent CN 113700074A/Chinese utility model patent CN215715667U discloses a hydraulic hammer which can work when the drill rod is in a non-pressing state. The technical scheme is as follows: an idle valve is arranged between the buffer cavity and the system high-pressure oil, when the piston enters the buffer cavity, the idle valve is opened, and the high-pressure oil enters the buffer cavity to push out the piston; when the piston leaves the buffer cavity, the idle valve is closed; the idle valve consists of an idle valve core and an idle valve sleeve, and the idle valve core slides in the idle valve sleeve along the axial direction; the end surface area of the valve core of the idle driving valve communicated with the buffer cavity is larger than the end surface area of the valve core of the idle driving valve communicated with the high-pressure oil of the system, namely the areas of the two end surfaces of the valve core of the idle driving valve are different, the hydraulic pressure applied to the two end surfaces is compared, the moving direction of the valve core of the idle driving valve is determined, and then whether the buffer cavity is communicated with the high-pressure oil of the system is determined. The problems that exist are that: 1. the idle valve needs to be connected with return oil, an oil return channel is constructed, the structural size of the idle valve can be increased, the structure is complex, the processing difficulty is increased, and the structural size and the processing difficulty of parts matched with the idle valve can also be increased. 2. The idle valve can be opened only when the pressure of the buffer cavity is lower than the pressure of the high-pressure oil of the system (the reason is that the area of the end surface of the valve core of the idle valve communicated with the buffer cavity is larger than that of the end surface of the valve core of the idle valve communicated with the high-pressure oil of the system).

In order to solve the problem that a drill rod must be pressed tightly in the working process of the hydraulic breaking hammer, the specification of the Chinese invention patent CN 114908833A/Chinese utility model patent CN217379055U discloses an air-beating type hydraulic breaking hammer based on a Tesla valve. The technical scheme is as follows: a Tesla valve is arranged between the buffer cavity and system high-pressure oil, the hydraulic oil in the buffer cavity flows out through the Tesla valve and flows out in the reverse direction, and the hydraulic oil flows into the buffer cavity through the Tesla valve and flows in the forward direction; tesla valves may provide a higher pressure drop in one direction than the other, allowing fluid to flow smoothly in one direction (i.e., forward) and flow in the other direction to be difficult (i.e., reverse). The problems that exist are that: there is a need for a sufficient flat surface mounting tesla valves.

SUMMERY OF THE UTILITY MODEL

To the above prior art, the utility model discloses following technical problem will be solved.

1. The other technical scheme is provided, the problem that a drill rod must be pressed in the working process of the existing hydraulic breaking hammer is solved, and the idle driving function is realized.

2. The idle valve needs to receive return oil, and has the problems of large and complex structure size and difficult processing.

3. The idle valve can be opened only when the pressure of the buffer cavity is lower than the pressure of high-pressure oil of the system.

4. Tesla valves require adequate mounting plane issues.

In order to solve the technical problem, the utility model provides a hydraulic breaking hammer based on empty function of beating is realized to hydraulic hammer effect and damping hole. The method comprises the following steps: piston, cylinder body, drill rod seat, endotheca, overcoat and drill rod. The piston reciprocates in the cylinder body to strike the drill rod; the drill rod seat is internally provided with a drill rod for breaking rocks, an inner sleeve and an outer sleeve which play a role in guiding, and the inner sleeve and the outer sleeve have the function of protecting the drill rod seat from being abraded. A floating valve is arranged between the buffer cavity and the system high-pressure oil P, and comprises a valve body, a floating valve core and a plug; the areas of two end surfaces of the floating valve core are equal, one end close to the plug is communicated with the buffer cavity, and the other end of the floating valve core is communicated with system high-pressure oil P; the floating valve core is internally provided with damping holes, and when hydraulic oil flows through the damping holes, the hydraulic oil can pass through the damping hole structure which is communicated in a way that the axes are perpendicular to each other. Before the maximum diameter of the piston enters the buffer cavity, the hydraulic pressure on the two end faces of the floating valve core is equal, and the floating valve core is in a balanced state, namely a floating state (ignoring the influence of gravity). When the maximum diameter of the piston enters the buffer cavity, the following two conditions exist: and (1) when the pressure of the buffer cavity is higher than the pressure of the system high-pressure oil P. In the first state, if the damping holes on the two end surfaces of the floating valve core are communicated through the annular grooves on the valve body, hydraulic oil in the buffer cavity flows to system high-pressure oil P through the damping holes in the floating valve core; because the axes of the damping holes which are communicated with each other are mutually vertical, when hydraulic oil flows through the damping holes, a liquid hammer effect is generated due to the rapid change of the flow direction; due to the action of the damping hole, pressure drop exists when the hydraulic oil in the buffer cavity flows to the system high-pressure oil P; at the moment, under the action of a liquid hammer effect and the pressure difference between two end faces of the floating valve core, the floating valve is closed, an oil way is cut off, and a good buffering effect is achieved on the piston. In the second state, if the damping holes on the two end faces of the floating valve core are not communicated through the annular groove on the valve body, at the moment, because the pressure of the buffer cavity is higher than the pressure of high-pressure oil P of the system, the floating valve core works only by the pressure difference, the floating valve is stabilized in a closed state, the oil way is cut off, and a good buffer effect is achieved on the piston. (2) In the second condition, the pressure of the buffer cavity is lower than the pressure of the high-pressure oil P of the system. In the first state, if the damping holes on the two end surfaces of the floating valve core are communicated through the annular groove on the valve body, system high-pressure oil P flows to the buffer cavity through the damping holes in the floating valve core; because the axes of the damping holes which are communicated with each other are vertical to each other, when hydraulic oil flows through the damping holes, a liquid hammer effect is generated due to the rapid change of the flow direction; due to the action of the damping hole, pressure drop exists when system high-pressure oil P flows to the buffer cavity; at the moment, under the action of a liquid hammer effect and pressure difference between two end faces of the floating valve core, the floating valve is completely opened or is stabilized in an opening state, an oil way is communicated, and the piston is pushed out of the buffer cavity, so that the hydraulic breaking hammer works continuously. In the second state, if the damping holes on the two end faces of the floating valve core are not communicated through the annular grooves on the valve body, at the moment, the pressure of the buffer cavity is lower than the pressure of high-pressure oil P of the system, the floating valve core only works by the pressure difference, the floating valve is opened, an oil way is communicated, the piston is pushed out of the buffer cavity, and the hydraulic breaking hammer continuously works.

Has the advantages that: after the piston enters the buffer cavity, the floating valve core realizes the opening and closing of the floating valve by means of the hydraulic hammer effect and the pressure difference generated by the damping hole, the problem that a drill rod needs to be pressed in the working process of the hydraulic breaking hammer is solved, and the idle driving function of the hydraulic breaking hammer is realized; compared with the idle-beating valve in the prior art, the floating valve core of the floating valve works by depending on the hydraulic hammer effect and the pressure difference generated by the damping hole, oil return does not need to be connected, and the damping hole is small in structural size, so that the floating valve is small and simple in structure; the floating valve core has small mass and high response speed, and is particularly suitable for a high-frequency hydraulic breaking hammer; compared with the Tesla valve in the prior art, the Tesla valve avoids the problem that the Tesla valve needs enough installation plane.

As a further improvement of the utility model, the plane of the contact surface of the piston and the drill rod seat is perpendicular to the axis of the piston.

Has the advantages that: the phenomenon that the matching surface of the piston and the cylinder body is damaged by radial force generated when the piston contacts the drill rod seat is avoided.

Drawings

Fig. 1 is a schematic diagram of a conventional hydraulic breaking hammer.

Fig. 2 is a schematic diagram of a conventional hydraulic breaking hammer.

Figure 3 is a schematic view of the piston entering the cushion chamber.

Fig. 4 the utility model discloses hydraulic breaking hammer structure schematic diagram.

Fig. 5 the utility model discloses hydraulic breaking hammer structure schematic diagram.

FIG. 6 is a cross-sectional view of the float valve.

FIG. 7 is a view showing a structure of a contact surface of a piston and a shank holder.

Reference numerals: 1 nitrogen chamber 2 piston ring 3 piston 4 cylinder 5 rod seat 6 internal sleeve 7 8 drill rod 9 change valve 10 accumulator 11 main seal 12 front cavity 13 rear cavity 14 buffer cavity 15 floating valve 16 plug 17 floating valve core 18 valve body 19 screw thread 20 ring groove 21 damping hole.

Detailed Description

The following describes embodiments of the present invention in further detail with reference to the drawings (fig. 4, 5, 6, and 7).

A hydraulic breaking hammer based on a hydraulic hammer effect and a damping hole to realize a blank beating function comprises: the device comprises a nitrogen chamber 1, a piston ring 2, a piston 3, a cylinder body 4, a drill rod seat 5, an inner sleeve 6, an outer sleeve 7, a drill rod 8, a reversing valve 9 and a floating valve 15. The reversing valve 9 controls the piston 3 to reciprocate in the cylinder 4 to strike the drill rod 8; the drill rod seat 5 is provided with a drill rod 8 for breaking rock, an inner sleeve 6 and an outer sleeve 7 which play a role in guiding, and the inner sleeve 6 and the outer sleeve 7 have the function of protecting the drill rod seat 5 from being abraded. A floating valve 15 is arranged between the buffer cavity 14 and the system high-pressure oil P, and the floating valve 15 comprises a plug 16, a floating valve core 17 and a valve body 18; the plug 16 is connected with the valve body 18 through threads; the valve body 18 is provided with an external thread 19 for being arranged on the cylinder body 4; the areas of two end surfaces of the floating valve core 17 are equal, one end close to the plug 16 is communicated with the buffer cavity 14, and the other end is communicated with system high-pressure oil P; the floating valve core 17 is internally provided with a damping hole 21, and when hydraulic oil flows through the damping hole 21, the hydraulic oil passes through the damping hole 21 structure with mutually vertical and communicated axes. Before the maximum diameter of the piston 3 enters the buffer cavity 14, the hydraulic pressure on the two end faces of the floating valve core 17 is equal, and the floating valve core is in a balanced state, namely a floating state (ignoring the influence of gravity). When the maximum diameter of the piston 3 enters the buffer chamber 14, the following two conditions exist: (1) The buffer chamber 14 is at a higher pressure than the system high pressure oil P. In the first state, if the damping holes 21 on the two end surfaces of the floating valve core 17 are communicated through the annular groove 20 on the valve body 18, the hydraulic oil in the buffer cavity 14 flows to the system high-pressure oil P through the damping holes 21 in the floating valve core 17; because the axes of the damping holes 21 which are communicated (communicated) with each other are vertical to each other, when hydraulic oil flows through the damping holes 21, a liquid hammer effect is generated due to the rapid change of the flow direction; due to the action of the damping hole 21, pressure drop exists when the hydraulic oil in the buffer cavity 14 flows to the system high-pressure oil P; at this time, the float valve 15 is closed by the liquid hammer effect and the pressure difference across the end faces of the float valve body 17, and the oil path is cut off, thereby providing a good cushion effect for the piston 3. In the second state, if the damping holes 21 on the two end faces of the floating valve core 17 are not communicated through the annular groove 20 on the valve body 18, at this time, because the pressure of the buffer cavity 14 is higher than the pressure of the high-pressure oil P of the system, the floating valve core 17 works only by the pressure difference, the floating valve 15 is stabilized in the closed state, the oil way is cut off, and a good buffer effect is achieved on the piston 3. (2) In the second case, the pressure of the buffer chamber 14 is lower than the pressure of the high-pressure oil P in the system. In the first state, if the damping holes 21 on the two end surfaces of the floating valve core 17 are communicated through the annular groove 20 on the valve body 18, system high-pressure oil P flows to the buffer cavity 14 through the damping holes 21 in the floating valve core 17; because the axes of the damping holes 21 which are communicated (communicated) with each other are vertical to each other, when hydraulic oil flows through the damping holes 21, a liquid hammer effect is generated due to the rapid change of the flow direction; due to the action of the damping hole 21, pressure drop exists when system high-pressure oil P flows to the buffer cavity 14; at this time, under the action of the liquid hammer effect and the pressure difference between two end faces of the floating valve core 17, the floating valve 15 is completely opened or stabilized in an opening state, an oil path is communicated, the piston 3 is pushed out of the buffer cavity 14, and the hydraulic breaking hammer continuously works. In the second state, if the damping holes 21 on the two end faces of the floating valve core 17 are not communicated through the annular groove 20 on the valve body 18, at this time, because the pressure of the buffer cavity 14 is lower than the pressure of the high-pressure oil P of the system, the floating valve core 17 only works by the pressure difference, the floating valve 15 is opened, the oil path is communicated, the piston 3 is pushed out from the buffer cavity 14, and the hydraulic breaking hammer continuously works.

Preferably (figure 7) the plane of the contact surface of the piston 3 and the rod seat 5 is perpendicular to the axis of the piston 3.

The present invention is not limited to the above embodiments, and all other embodiments obtained without creative work by those of ordinary skill in the art are all included in the protection scope of the present invention based on the embodiments of the present invention.

Claims (3)

1. A hydraulic breaking hammer for realizing a blank beating function based on a hydraulic hammer effect and a damping hole comprises a piston (3), a cylinder body (4), a drill rod seat (5), a drill rod (8) and a reversing valve (9); the reversing valve (9) controls the piston (3) to reciprocate in the cylinder body (4) to strike the drill rod (8); the drill rod (8) is arranged inside the drill rod seat (5), and is characterized in that: a floating valve (15) is arranged between the buffer cavity (14) and system high-pressure oil; the floating valve (15) comprises a plug (16), a floating valve core (17) and a valve body (18); the plug (16) is connected with the valve body (18) through threads; the valve body (18) is provided with an external thread (19) for being arranged on the cylinder body (4); the areas of two end surfaces of the floating valve core (17) are equal, one end close to the plug (16) is communicated with the buffer cavity (14), and the other end is communicated with system high-pressure oil; damping holes (21) are formed in the floating valve core (17), and hydraulic oil passes through the damping holes (21) which are vertically communicated with each other through the axis when flowing through the damping holes (21).

2. The hydraulic breaking hammer based on the hydraulic hammer effect and the damping hole to realize the idle striking function as claimed in claim 1, wherein: when damping holes (21) on two end surfaces of the floating valve core (17) are communicated through an annular groove (20) on the valve body (18), the floating valve (15) is in an open state; when damping holes (21) on two end surfaces of the floating valve core (17) are not communicated through an annular groove (20) on the valve body (18), the closed state of the floating valve (15) is realized.

3. The hydraulic breaking hammer based on the hydraulic hammer effect and the damping holes and used for achieving the idle striking function as claimed in claim 1 or 2, wherein: the plane of the contact surface of the piston (3) and the drill rod seat (5) is vertical to the axis of the piston (3).

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