CN218204634U - Hydraulic breaking hammer and engineering machinery - Google Patents

Abstract

The utility model belongs to the engineering machine tool field discloses a hydraulic breaking hammer and engineering machine tool, and hydraulic breaking hammer wherein includes: a middle cylinder body; the piston rod is arranged in the middle cylinder body; the continuous reversing loop is arranged among the crushing hammer oil inlet, the crushing hammer oil return port and the middle cylinder body and is used for controlling the piston rod to reciprocate with a primary stroke; and the variable-frequency trigger oil way is arranged between the continuous reversing loop and the middle cylinder body and is used for triggering the reversing time of the main control hydraulic reversing valve in the continuous reversing loop to change so as to adjust the piston rod to reciprocate by a non-preset stroke. The utility model discloses a hydraulic breaking hammer can adjust the reciprocating motion stroke of piston rod on a large scale, and automatically regulated strikes frequency or hitting power to can promote broken work volume, improve work efficiency, be suitable for different broken operating mode and use, need not match the lectotype again to hydraulic breaking hammer, avoid causing the wasting of resources.

Description

Hydraulic breaking hammer and engineering machinery

Technical Field

The utility model relates to an engineering machine tool technical field specifically, relates to a hydraulic breaking hammer and engineering machine tool.

Background

The hydraulic breaking hammer is a device which takes hydraulic energy as a power source and converts the hydraulic energy into mechanical striking kinetic energy in the movement process, so that a piston rod continuously impacts a drill rod to carry out breaking operation. The hydraulic breaking hammer is generally mounted on an excavator and works by using hydraulic energy provided by the excavator. The working efficiency of a breaking hammer is the kinetic energy and frequency of the drill rod impacting an object, and under the condition of determined pressure and flow, the striking force is inversely proportional to the striking frequency, and the striking frequency is inversely proportional to the stroke of a piston rod. For a traditional hydraulic breaking hammer, the stroke of a piston rod of the traditional hydraulic breaking hammer is fixed, and when the striking frequency needs to be adjusted, the oil return back pressure of the breaking hammer needs to be changed through a manual adjusting valve adjuster.

However, the adjustment range of the manner for adjusting the striking frequency is narrow, and if the striking frequency and the striking force of the breaking hammer are required to be adjusted in a large range, the breaking hammer can only be matched and selected again, so that certain resource waste is caused.

In addition, because the hardness difference of different stones is great, the striking frequency of the breaking hammer needs to be frequently and manually adjusted to improve the striking force of the breaking hammer under different breaking working conditions. When hard stones are encountered, the proper striking frequency and striking speed can be matched by several times of judgment and several times of manual debugging, so that the working efficiency is influenced.

SUMMERY OF THE UTILITY MODEL

At least one kind of defect or not enough to prior art's above-mentioned, the utility model provides a hydraulic crushing hammer and engineering machine tool can adjust the reciprocating motion stroke of piston rod on a large scale, and automatically regulated strikes the frequency to reach and promote broken work load, improve work efficiency, avoid purposes such as wasting of resources.

In order to achieve the above object, the present invention provides in a first aspect a hydraulic breaker, including:

a middle cylinder body;

a piston rod disposed in the middle cylinder body;

the continuous reversing loop is arranged among the crushing hammer oil inlet, the crushing hammer oil return port and the middle cylinder body and is used for controlling the piston rod to reciprocate with a primary stroke; and

and the variable-frequency trigger oil way is arranged between the continuous reversing loop and the middle cylinder body and is used for triggering the reversing time of the main control hydraulic reversing valve in the continuous reversing loop to change so as to adjust the piston rod to reciprocate by a non-preset stroke.

Optionally, be formed with in the well cylinder by the perisporium annular flange of piston rod separates from top to bottom and can be in well cylinder epicoele and well cylinder body cavity of producing the pressure differential under the effect of continuous reversing circuit, main control hydraulic reversing valve is including going up work valve position and down work valve position, the perisporium of well cylinder body is formed with along vertical setting gradually and can communicate the hydraulic control end between the hydraulic control end of setting the stroke hydraulic fluid port and the down work valve position of well cylinder body cavity is just established stroke hydraulic fluid port and at least one variable stroke hydraulic fluid port, continuous reversing circuit is including just establishing stroke trigger oil circuit, just establish stroke trigger oil circuit setting and be in set up the stroke hydraulic fluid port with down between the hydraulic control end of work valve position, frequency conversion trigger oil circuit sets up variable stroke hydraulic fluid port with down between the hydraulic control end of work valve position in the ascending process of piston rod, well cylinder body cavity can be through one of them stroke and corresponding trigger oil circuit with the hydraulic control end of down work valve position switches on.

Optionally, the variable stroke oil port comprises a first variable stroke oil port and a second variable stroke oil port, the variable frequency trigger oil path comprises a three-position four-way reversing valve with an O-shaped neutral position function, a first oil inlet branch, a second oil inlet branch and an oil discharge branch, the first variable stroke oil port is connected with the hydraulic control end of the downlink working valve position sequentially through the first oil inlet branch, the three-position four-way valve and the oil discharge branch, and the second variable stroke oil port is connected with the hydraulic control end of the downlink working valve position sequentially through the second oil inlet branch, the three-position four-way valve and the oil discharge branch.

Optionally, the preliminary stroke oil port, the first stroke variable oil port and the second stroke variable oil port are sequentially arranged from top to bottom.

Optionally, a check valve is arranged in the default stroke triggering oil path, one end of the oil discharge branch is connected to the three-position four-way reversing valve, and the other end of the oil discharge branch is connected to a portion, located between the check valve and a hydraulic control end of the downlink working valve, of the default stroke triggering oil path.

Optionally, the three-position four-way reversing valve is a hydraulic pilot reversing valve and is provided with a control oil port for controlling pilot pressure.

Optionally, the hydraulic breaking hammer comprises a transition valve block, the hydraulic pilot reversing valve is integrated in the transition valve block, and the control oil port is formed in the outer wall of the transition valve block.

Optionally, a lower cavity oil return port is formed in the circumferential wall of the middle cylinder body, the continuous reversing circuit includes a downlink oil return path, two ends of the downlink oil return path are respectively communicated with the lower cavity oil return port and the crushing hammer oil return port, and the lower cavity oil return port is communicated with the middle cylinder body lower cavity in a state that the middle cylinder body lower cavity is communicated with a hydraulic control end of the downlink working valve position through one of the stroke oil ports and the corresponding trigger oil path.

Optionally, an upper cavity in-and-out switching oil port communicated with the upper cavity of the middle cylinder body and a lower cavity oil inlet communicated with the lower cavity of the middle cylinder body are formed in the peripheral wall of the middle cylinder body, the lower cavity oil inlet is communicated with the breaking hammer oil inlet, and the upper cavity in-and-out switching oil port can be selectively communicated with one of the breaking hammer oil inlet and the breaking hammer oil return port through the main control hydraulic reversing valve.

Optionally, the hydraulic breaking hammer further comprises an upper cylinder body connected with the upper end of the middle cylinder body, a nitrogen cavity is formed in the upper cylinder body, and the top end of the piston rod extends into the nitrogen cavity.

Optionally, the hydraulic breaking hammer further comprises a lower cylinder connected to the lower end of the middle cylinder and a drill rod inserted into the lower cylinder, and the bottom end of the piston rod extends into the lower cylinder and can impact the top of the drill rod.

The utility model discloses the second aspect provides an engineering machine tool, and it includes foretell hydraulic breaking hammer.

Through the technical scheme, the utility model discloses a hydraulic crushing hammer can control the piston rod in order just establishing stroke reciprocating motion under the effect in continuous switching-over return circuit, when needs are adjusted the striking frequency, trigger the oil circuit through the frequency conversion and trigger the switching-over opportunity of the main control switching-over valve that surges in the continuous switching-over return circuit and change, the piston rod can be gone up to not reaching just the ascending and descending switching critical position of establishing or surpassing just the ascending and descending switching critical position's of establishing circumstances down and switch into down, the performance is piston rod with the non-stroke reciprocating motion of just establishing on the whole to realize striking frequency's automatically regulated. Change the strike frequency control mode of the oil return backpressure of quartering hammer for traditional manual regulation valve regulator, the utility model discloses a hydraulic crushing hammer has the control range that is far greater than it to be suitable for different broken operating modes and use, need not match the lectotype again to hydraulic crushing hammer, avoid causing the wasting of resources, promote broken work volume, improve work efficiency.

Other features and advantages of the present invention will be described in detail in the detailed description which follows.

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the principles of the invention and not to limit the invention. In the drawings:

fig. 1 is a working schematic diagram of a hydraulic breaking hammer according to an embodiment of the present invention;

fig. 2 is a schematic structural diagram of a hydraulic breaking hammer according to an embodiment of the present invention;

fig. 3 is a schematic view of a middle cylinder of a hydraulic breaking hammer according to an embodiment of the present invention;

fig. 4 is a schematic diagram of a transition valve block of a hydraulic breaking hammer and a three-position four-way reversing valve integrated on the transition valve block according to an embodiment of the present invention;

FIG. 5 is a schematic view of the valve cartridge of the three-position, four-way reversing valve of FIG. 4.

Description of reference numerals:

1. middle cylinder 2 piston rod

3. Master control hydraulic change valve 4 three-position four-way change valve

5. 6 transition valve blocks of check valve

7. Upper 8 lower cylinder

9. Drill rod

11. Middle cylinder upper chamber 12 middle cylinder lower chamber

13. Upper cavity inlet and outlet switching oil port 14 and lower cavity oil return port

15. The first stroke-variable oil port of the initial stroke oil port 16

17. Oil inlet of lower cavity of second stroke-changing oil port 18

L1 is established stroke primarily and is triggered first oil feed branch road of oil circuit L2

L3 second oil inlet branch L4 oil discharge branch

L5 downward oil return path

P quartering hammer oil inlet T quartering hammer oil return port

K1 First control port K2 and second control port

Detailed Description

The following describes in detail embodiments of the present invention with reference to the accompanying drawings. It is to be understood that the description herein is provided for purposes of illustration and explanation, and is not intended to limit the embodiments of the invention.

It should be noted that, in the present invention, the embodiments and features of the embodiments may be combined with each other without conflict.

In the embodiments of the present invention, unless otherwise specified, the use of directional terms such as "upper, lower, top, bottom" and "upper" are generally used with respect to the orientation shown in the drawings or the positional relationship of the components with respect to each other in the vertical, vertical or gravitational direction.

The invention will be described in detail below with reference to the drawings and in connection with exemplary embodiments.

Referring to fig. 1 to 5, a first exemplary embodiment of the present invention provides a hydraulic breaker including a middle cylinder body 1, a piston rod 2, a continuous reversing circuit, and a variable frequency triggering oil circuit.

Specifically, the piston rod 2 is disposed inside the middle cylinder 1.

The continuous reversing loop is arranged between the breaking hammer oil inlet P, the breaking hammer oil return port T and the middle cylinder body 1, external hydraulic oil can enter the middle cylinder body 1 through the breaking hammer oil inlet P and the continuous reversing loop, and the hydraulic oil in the middle cylinder body 1 can be discharged out of the hydraulic breaking hammer through the continuous reversing loop and the breaking hammer oil return port T. Under the action of the continuous reversing loop, pressure difference can be formed between the upper part and the lower part of the piston rod 2 to control the piston rod 2 to move upwards or downwards, when the piston rod 2 moves upwards to a preset up-down switching critical position, hydraulic oil in the middle cylinder body 1 is guided into a hydraulic control end of the main control hydraulic reversing valve 3 by an oil path in the continuous reversing loop, the main control hydraulic reversing valve 3 switches a working valve position, and then the piston rod 2 changes from moving upwards to moving downwards, and the whole piston rod 2 performs reciprocating motion with a preset stroke. The initial stroke is the stroke of the piston rod 2 when the variable frequency trigger oil circuit is not conducted with the middle cylinder body 1 and the continuous reversing loop and is manually preset.

The frequency conversion triggering oil circuit is arranged between the continuous reversing circuit and the middle cylinder body 1, hydraulic oil in the middle cylinder body 1 can be led into a hydraulic control end of a main control hydraulic reversing valve 3 of the continuous reversing circuit in advance or in a delayed manner, the main control hydraulic reversing valve 3 switches working valve positions in advance or in a delayed manner, and then the piston rod 2 is changed from ascending to descending, and the whole piston rod 2 does reciprocating motion with a non-preset stroke.

For example, if the stroke of the piston rod 2 is to be shortened (i.e. the striking frequency is increased), the variable-frequency trigger oil circuit can conduct the hydraulic control end of the middle cylinder body 1 and the master control hydraulic directional control valve 3 when the piston rod 2 does not go up to the preset up-down switching critical position, so as to trigger the master control hydraulic directional control valve 3 to switch the working valve position in advance, so that the piston rod 2 goes up to down in advance, and as a whole, the piston rod 2 reciprocates with a stroke smaller than the preset stroke.

If the stroke of the piston rod 2 needs to be increased (i.e. the striking frequency is reduced), when the piston rod 2 moves upwards to a preset up-down switching critical position, the oil circuit in the continuous reversing loop does not conduct the hydraulic control end of the middle cylinder body 1 and the main control hydraulic reversing valve 3, at this moment, the main control hydraulic reversing valve 3 cannot be triggered temporarily to switch the working valve position, and the piston rod 2 can continue to move upwards. When the piston rod 2 continues to move upwards to a certain position exceeding the initial up-down switching critical position, the middle cylinder body 1 is communicated with the hydraulic control end of the main control hydraulic reversing valve 3 through the variable frequency triggering oil circuit, namely, the main control hydraulic reversing valve 3 is triggered to switch the working valve position after delay, so that the piston rod 2 is changed from ascending to descending after delay, and the whole piston rod 2 performs reciprocating motion with a stroke larger than the initial stroke.

Therefore, the variable-frequency triggering oil circuit is used for triggering the reversing time of the main control hydraulic reversing valve 3 in the continuous reversing loop to change, namely the reversing time is advanced or delayed, so that the piston rod 2 can be adjusted to reciprocate in a non-preset stroke, and the adjustment of the striking frequency is realized.

It can be understood that the hydraulic control ends of the middle cylinder body 1 and the main control hydraulic reversing valve 3 which are communicated with the variable frequency trigger oil circuit can be directly determined by adjusting the position to which the piston rod 2 moves upwards, so that the reversing time of the main control hydraulic reversing valve 3 can be advanced or delayed, the stroke of the piston rod 2 can be adjusted in a large range, and the striking frequency can be adjusted in a large range.

For the strike frequency adjustment mode that traditional manual regulation valve regulator changes the oil return backpressure of quartering hammer, the hydraulic pressure quartering hammer of this example embodiment has the control range who is far greater than it to be suitable for different broken operating modes and use, need not match the lectotype again to hydraulic pressure quartering hammer, avoid causing the wasting of resources, promote broken work load, improve work efficiency.

In one embodiment, the middle cylinder 1 has a middle cylinder upper chamber 11 and a middle cylinder lower chamber 12 formed therein, which are vertically separated by a circumferential wall annular flange of the piston rod 2 and can generate a pressure difference under the action of a continuous reversing circuit, and the piston rod 2 is pushed to move upwards or downwards under the action of the pressure difference between the middle cylinder upper chamber 11 and the middle cylinder lower chamber 12. The master hydraulic directional control valve 3 includes an upstream working valve position and a downstream working valve position, for example, the left and right working valve positions of the master hydraulic directional control valve 3 in fig. 1 are the upstream working valve position and the downstream working valve position thereof, respectively. The perisporium of well cylinder body 1 is formed with along vertical setting gradually and can communicate the cylinder body cavity of resorption 12 establish stroke hydraulic fluid port 15 and at least one become the stroke hydraulic fluid port in the beginning, only sets up one and becomes under the condition of stroke hydraulic fluid port, and the striking frequency of hydraulic breaking hammer can realize the secondary control, is equipped with under the condition of a plurality of stroke hydraulic fluid ports that become, and the striking frequency of hydraulic breaking hammer can realize multistage regulation. In addition, the continuous reversing loop comprises a primary stroke trigger oil way L1. The primary stroke trigger oil circuit L1 is arranged between the primary stroke oil port 15 and the hydraulic control end of the descending working valve position, and the variable frequency trigger oil circuit is arranged between the variable stroke oil port and the hydraulic control end of the descending working valve position. In the ascending process of the piston rod 2, the middle cylinder lower cavity 12 can be communicated with the hydraulic control end of the descending working valve position of the main control hydraulic reversing valve 3 through one of the stroke oil ports and the corresponding trigger oil path, so that the piston rod 2 can reciprocate with the corresponding stroke.

For example, when the piston rod 2 moves upward to make the middle cylinder lower cavity 12 and the preset stroke oil port 15 communicate, the hydraulic oil in the middle cylinder lower cavity 12 can be led into the hydraulic control end of the downward working valve position of the main control hydraulic directional control valve 3 through the preset stroke oil port 15 and the preset stroke trigger oil path L1, so as to trigger the main control hydraulic directional control valve 3 to switch from the upward working valve position to the downward working valve position, so that the piston rod 2 moves from the upward direction to the downward direction, and the whole body shows that the piston rod 2 reciprocates with the preset stroke.

When the piston rod 2 moves upwards to enable the middle cylinder lower cavity 12 to be communicated with any variable stroke oil port, hydraulic oil in the middle cylinder lower cavity 12 can be led into a hydraulic control end of a descending working valve position of the main control hydraulic reversing valve 3 through the variable stroke oil port and a variable frequency trigger oil path, so that the main control hydraulic reversing valve 3 is triggered to be switched from the ascending working valve position to the descending working valve position, the piston rod 2 is changed from ascending to descending, and the whole piston rod 2 reciprocates with a corresponding stroke (non-primary stroke).

In one embodiment, the variable stroke oil ports include a first variable stroke oil port 16 and a second variable stroke oil port 17, for example, the preset stroke oil port 15, the first variable stroke oil port 16 and the second variable stroke oil port 17 may be arranged in sequence from top to bottom. The frequency conversion trigger oil circuit comprises a three-position four-way reversing valve 4 with an O-shaped neutral position function, a first oil inlet branch L2, a second oil inlet branch L3 and an oil discharge branch L4. The first stroke-changing oil port 16 is connected with the hydraulic control end of the downlink working valve position of the main control hydraulic reversing valve 3 sequentially through the first oil inlet branch L2, the three-position four-way valve and the oil discharge branch L4, and the second stroke-changing oil port 17 is connected with the hydraulic control end of the downlink working valve position of the main control hydraulic reversing valve 3 sequentially through the second oil inlet branch L3, the three-position four-way valve and the oil discharge branch L4. That is, the first variable stroke oil port 16 and the second variable stroke oil port 17 are communicated with the hydraulic control end of the downward working valve position of the main control hydraulic directional control valve 3 through the same oil discharge branch L4.

For example, referring to fig. 1, when the three-position four-way selector valve 4 is in the middle position, even if the first variable-stroke oil port 16 or the second variable-stroke oil port 17 is communicated with the middle cylinder lower chamber 12, the hydraulic oil in the middle cylinder lower chamber 12 cannot be introduced into the hydraulic control end of the down-stroke position of the main control hydraulic selector valve 3 through the three-position four-way selector valve 4 and the oil discharge branch L4. When the three-position four-way reversing valve 4 is in the left valve position, hydraulic oil in the middle cylinder lower cavity 12 can be led into a hydraulic control end of the downlink working valve position of the main control hydraulic reversing valve 3 through the first stroke changing oil port 16, the first oil inlet branch L2, the three-position four-way reversing valve 4 and the oil discharge branch L4. When the three-position four-way reversing valve 4 is located at the right valve position, hydraulic oil in the middle cylinder lower cavity 12 can be led into a hydraulic control end of the downlink working valve position of the main control hydraulic reversing valve 3 through the second variable stroke oil port 17, the second oil inlet branch L3, the three-position four-way reversing valve 4 and the oil outlet branch L4.

In the present embodiment, the striking frequency of the hydraulic breaking hammer can be adjusted in three stages.

In one embodiment, the preset stroke trigger oil path L1 is provided with a check valve 5, when the piston rod 2 moves upward to enable the middle cylinder lower cavity 12 to be communicated with the preset stroke oil port 15, hydraulic oil in the middle cylinder lower cavity 12 can enter the preset stroke trigger oil path L1 through the preset stroke oil port 15, and the check valve 5 is pushed open, so that the hydraulic oil is led into a hydraulic control end of a downward working valve position of the main control hydraulic reversing valve 3 through the preset stroke trigger oil path L1. Further, one end of the oil discharge branch L4 is connected to the three-position four-way selector valve 4, and the other end is connected to a portion of the preset stroke trigger oil path L1 located between the check valve 5 and the hydraulic control end of the downstream operation valve.

In one embodiment, the three-position four-way directional valve 4 is a hydraulic pilot directional valve and is provided with control ports K1, K2 for controlling pilot pressure.

Referring to fig. 1, when hydraulic oil is input through K1, the three-position four-way directional valve 4 can be switched to a left valve position to work, and when the piston rod 2 moves upward to enable the middle cylinder lower cavity 12 to be communicated with the first stroke-changing oil port 16, the hydraulic oil in the middle cylinder lower cavity 12 can be led into a hydraulic control end of the downward working valve position of the main control hydraulic directional valve 3 through the first stroke-changing oil port 16, the first oil inlet branch L2, the three-position four-way directional valve 4 and the oil discharge branch L4.

When the piston rod 2 moves upwards to enable the middle cylinder lower cavity 12 to be communicated with the second variable stroke oil port 17, the hydraulic oil in the middle cylinder lower cavity 12 can be led into a hydraulic control end of the downward working valve position of the main control hydraulic reversing valve 3 through the second variable stroke oil port 17, the second oil inlet branch L3, the three-position four-way reversing valve 4 and the oil discharge branch L4.

In an embodiment, the hydraulic breaking hammer comprises a transition valve block 6, the hydraulic pilot reversing valve may be integrated in the transition valve block 6, and accordingly the control ports K1, K2 are opened on the outer wall of the transition valve block 6 to simplify the structural arrangement of the hydraulic breaking hammer.

In one embodiment, the peripheral wall of the middle cylinder 1 is formed with a lower chamber oil return port 14, and the continuous reversing circuit includes a descending oil return path L5 having two ends respectively communicated with the lower chamber oil return port 14 and the crushing hammer oil return port T. In a state that the middle cylinder lower cavity 12 is communicated with a hydraulic control end of a descending working valve position through one of the stroke oil ports and the corresponding trigger oil way, the lower cavity oil return port 14 is communicated with the middle cylinder lower cavity 12, so that in a descending process of the piston rod 2, the middle cylinder lower cavity 12 can be decompressed through the lower cavity oil return port 14, the descending oil return oil way L5 and the hammer oil return port T.

In one embodiment, the peripheral wall of the middle cylinder 1 is formed with an upper cavity in-and-out switching oil port 13 communicating with the upper cavity 11 of the middle cylinder and a lower cavity oil inlet 18 communicating with the lower cavity 12 of the middle cylinder, the lower cavity oil inlet 18 is in communication with the breaking hammer oil inlet P, and the upper cavity in-and-out switching oil port 13 can be selectively communicated with one of the breaking hammer oil inlet P and the breaking hammer oil return port T through the main control hydraulic reversing valve 3.

In the process that the piston rod 2 moves upwards, the upper cavity inlet and outlet switching oil port 13 is communicated with the breaking hammer oil return port T through the main control hydraulic reversing valve 3, so that the pressure of the upper cavity 11 of the middle cylinder body can be relieved through the upper cavity inlet and outlet switching oil port 13, the main control hydraulic reversing valve 3 and the breaking hammer oil return port T.

Under the condition that the upper cavity inlet and outlet switching oil port 13 is communicated with the breaking hammer oil inlet P through the main control hydraulic reversing valve 3, hydraulic oil is led into the upper cavity 11 of the middle cylinder body from the upper cavity inlet and outlet switching oil port 13, so that the pressure of the upper cavity 11 of the middle cylinder body is greater than that of the lower cavity 12 of the middle cylinder body, and the piston rod 2 is pushed to move downwards.

In one embodiment, the hydraulic breaking hammer further comprises an upper cylinder body 7 connected with the upper end of the middle cylinder body 1, a nitrogen gas cavity is formed in the upper cylinder body 7, and the top end of the piston rod 2 extends into the nitrogen gas cavity. In the upward movement process of the piston rod 2, the top end of the piston rod can compress nitrogen in the nitrogen cavity to enable the nitrogen cavity to store energy, and in the downward movement process of the piston rod 2, high-pressure nitrogen in the nitrogen cavity can apply downward thrust to the piston rod 2.

In one embodiment, the hydraulic breaking hammer further comprises a lower cylinder 8 connected with the lower end of the middle cylinder 1 and a drill rod 9 inserted into the lower cylinder 8, the bottom end of the piston rod 2 extends into the lower cylinder 8 and can impact the top of the drill rod 9 when the piston rod 2 moves downwards, and the drill rod 9 can continuously impact stones through the reciprocating motion of the piston rod 2, so that the breaking function is realized.

A second exemplary embodiment of the present invention provides an engineering machine including the above-described hydraulic breaking hammer. For example, the work machine may be an excavator, and a hydraulic system within the excavator may be configured to provide hydraulic energy to the hydraulic breaker hammer. Obviously, the working machine of the exemplary embodiment has all the technical effects brought by the hydraulic breaking hammer, and therefore, the detailed description is omitted here.

The above describes in detail optional implementation manners of embodiments of the present invention with reference to the accompanying drawings, however, the embodiments of the present invention are not limited to the details in the above implementation manners, and in the technical concept scope of the embodiments of the present invention, it is possible to perform various simple modifications on the technical solutions of the embodiments of the present invention, and these simple modifications all belong to the protection scope of the embodiments of the present invention.

It should be noted that, in the above-mentioned embodiments, the various technical features described in the above-mentioned embodiments can be combined in any suitable way without contradiction, and in order to avoid unnecessary repetition, the embodiments of the present invention do not separately describe various possible combinations.

In addition, various different implementation manners of the embodiments of the present invention can be combined arbitrarily, and as long as it does not violate the idea of the embodiments of the present invention, it should be considered as the disclosure of the embodiments of the present invention.

Claims (12)

1. A hydraulic demolition hammer, characterized in that it comprises:

a middle cylinder body (1);

the piston rod (2) is arranged in the middle cylinder body (1);

the continuous reversing loop is arranged among the breaking hammer oil inlet (P), the breaking hammer oil return port (T) and the middle cylinder body (1) and is used for controlling the piston rod (2) to reciprocate with a primary stroke; and

and the variable-frequency trigger oil way is arranged between the continuous reversing loop and the middle cylinder body (1) and is used for triggering the reversing time of a main control hydraulic reversing valve (3) in the continuous reversing loop to change so as to adjust the piston rod (2) to do reciprocating motion with a non-preset stroke.

2. The hydraulic breaking hammer according to claim 1, wherein a middle cylinder upper chamber (11) and a middle cylinder lower chamber (12) which are vertically separated by a circumferential wall annular flange of the piston rod (2) and can generate pressure difference under the action of the continuous reversing circuit are formed in the middle cylinder (1), the main control hydraulic reversing valve (3) comprises an upward working valve position and a downward working valve position, a preset stroke oil port (15) and at least one variable stroke oil port which are vertically and sequentially arranged and can be communicated with the middle cylinder lower chamber (12) are formed in the circumferential wall of the middle cylinder (1), and the continuous reversing circuit comprises a preset stroke trigger oil path (L1);

the hydraulic control system is characterized in that the initial stroke trigger oil way (L1) is arranged between an initial stroke oil port (15) and a hydraulic control end of a downlink working valve position, the variable frequency trigger oil way is arranged between a variable stroke oil port and the hydraulic control end of the downlink working valve position, and in the uplink process of the piston rod (2), the middle cylinder body lower cavity (12) can be communicated with the hydraulic control end of the downlink working valve position through one stroke oil port and the corresponding trigger oil way.

3. The hydraulic breaking hammer according to claim 2, wherein the variable stroke oil port comprises a first variable stroke oil port (16) and a second variable stroke oil port (17), the variable frequency trigger oil path comprises a three-position four-way reversing valve (4) with an O-shaped middle position function, a first oil inlet branch (L2), a second oil inlet branch (L3) and an oil discharge branch (L4), the first variable stroke oil port (16) is connected with a hydraulic control end of the down working valve position sequentially through the first oil inlet branch (L2), the three-position four-way valve and the oil discharge branch (L4), and the second variable stroke oil port (17) is connected with a hydraulic control end of the down working valve position sequentially through the second oil inlet branch (L3), the three-position four-way reversing valve and the oil discharge branch (L4).

4. The hydraulic breaking hammer according to claim 3, wherein the preliminary stroke oil port (15), the first stroke variable oil port (16) and the second stroke variable oil port (17) are sequentially arranged from top to bottom.

5. The hydraulic breaking hammer according to claim 4, wherein a one-way valve (5) is arranged in the initial stroke triggering oil path (L1), one end of the oil discharge branch (L4) is connected with the three-position four-way reversing valve (4) and the other end is connected to the part of the initial stroke triggering oil path (L1) between the one-way valve (5) and the hydraulic control end of the downstream working valve position.

6. The hydraulic breaking hammer according to claim 3, wherein the three-position four-way reversing valve (4) is a hydraulic pilot reversing valve and is provided with a first control oil port (K1) and a second control oil port (K2) for controlling pilot pressure.

7. The hydraulic breaking hammer according to claim 6, characterized in that it comprises a transition valve block (6), the hydraulic pilot directional valve is integrated in the transition valve block (6), and the first control port (K1) and the second control port (K2) are both opened on the outer wall of the transition valve block (6).

8. The hydraulic quartering hammer according to claim 2, characterized in that a lower cavity oil return port (14) is formed in the peripheral wall of the middle cylinder body (1), the continuous reversing circuit includes a downward oil return path (L5) having two ends respectively communicating with the lower cavity oil return port (14) and the quartering hammer oil return port (T), and the lower cavity oil return port (14) communicates with the middle cylinder body lower cavity (12) in a state where the middle cylinder body lower cavity (12) communicates with a hydraulic control end of the downward operating valve position through one of the stroke oil ports and a corresponding trigger oil path.

9. The hydraulic breaking hammer according to claim 2, wherein an upper cavity in-and-out switching oil port (13) communicated with the upper cavity (11) of the middle cylinder body and a lower cavity oil inlet (18) communicated with the lower cavity (12) of the middle cylinder body are formed in the peripheral wall of the middle cylinder body (1), the lower cavity oil inlet (18) is communicated with the breaking hammer oil inlet (P), and the upper cavity in-and-out switching oil port (13) can be selectively communicated with one of the breaking hammer oil inlet (P) and the breaking hammer oil return port (T) through the main control hydraulic reversing valve (3).

10. The hydraulic breaking hammer according to claim 1, further comprising an upper cylinder (7) connected to an upper end of the middle cylinder (1), wherein a nitrogen chamber is formed in the upper cylinder (7), and a top end of the piston rod (2) extends into the nitrogen chamber.

11. The hydraulic breaking hammer according to claim 1, characterized in that it further comprises a lower cylinder (8) connected to the lower end of the middle cylinder (1) and a drill rod (9) inserted in the lower cylinder (8), the bottom end of the piston rod (2) extending into the lower cylinder (8) and being able to strike the top of the drill rod (9).

12. A working machine, characterized in that the working machine comprises a hydraulic demolition hammer according to any one of claims 1-11.

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