CN116838666A - Anti-jamming structure and hydraulic rock drill - Google Patents

Abstract

The application provides an anti-jamming structure which is applied to a hydraulic rock drill and comprises a piston, a cylinder body and a reversing valve, wherein the piston and the reversing valve are coaxially arranged in the cylinder body, the reversing valve is arranged between the piston and the cylinder body, and the reversing valve is used for assisting the piston to reverse; a braking dead space, a piston rear space for oil inlet and a piston front space are arranged between the cylinder body and the piston; the reversing valve is provided with an anti-blocking part protruding towards the direction of the piston, the piston is provided with a yielding groove recessed towards the center of the piston, and the anti-blocking part is matched with the yielding groove to prevent the piston from being blocked in the braking dead space. Through the effect of anti-sticking portion and groove of stepping down, can make the piston get into and stop the dead chamber after can withdraw from fast to the condition emergence of piston jamming in the dead chamber of braking has been played. On the other hand provides a hydraulic rock drill, including foretell anti-sticking structure, the piston is difficult for the jamming in the dead space of braking, reduces time, the manpower that consume because of the piston jamming for rock drill work efficiency obtains improving.

Description

Anti-jamming structure and hydraulic rock drill

Technical Field

The application relates to the technical field of rock drills, in particular to an anti-jamming structure and a hydraulic rock drill.

Background

Rock drill is a tool for rock production and mainly comprises an impact structure and a turning structure. The rotary structure comprises a drill rod, the drill rod is impacted when the impact piston extends outwards from the cylinder body to the limit position, and the drill rod transmits impact force to rock for drilling.

In the prior art, in order to prevent the piston from being overturned to the rearmost side and causing the piston to strike the cylinder body, on the premise of increasing the whole length of equipment as small as possible, the braking dead spaces are arranged at the front end and the rear end of the piston in a general rock drill. The front end is usually limited by the front end machinery matched with the piston impact body and reduces the empty impact to realize the protection, and the rear end can only realize the hydraulic protection by the braking dead space.

In actual use, because the pressure is higher than rated pressure, the piston stroke increases, the piston gets into the dead space of back braking, or the piston has assembled the rear side after the maintenance of tearing open the machine, the piston gets into the dead space of back braking, or there is not oil in the rock drill chamber when starting again, rock drill tilt up leads to the piston dead weight influence, there is not hydraulic resistance in the dead space of back braking, the piston landing is like the existence of the dead space of back braking etc. the existence of the dead space of back braking, though effectively protected the piston to a certain extent, but also the problem of dead space of back braking behind the dead space of back braking that accompanies existence piston entering back braking, need rely on the rock drill to withdraw from the piston back braking dead space, even stop scheduling problem.

In summary, there is room for further improvement in the hydraulic rock drill of the prior art.

Disclosure of Invention

In order to solve the technical problems, the application provides an anti-jamming structure which can effectively promote a piston to rapidly withdraw after entering a braking dead space so as to prevent jamming of the piston; on the other hand, the application also provides a hydraulic rock drill which is provided with an anti-jamming structure, so that the jamming probability of the hydraulic rock drill can be reduced, and the working efficiency of the rock drill is greatly improved.

In a first aspect, the application provides an anti-jamming structure, which is applied to a hydraulic rock drill, wherein the anti-jamming structure comprises a piston, a cylinder body and a reversing valve, the piston and the reversing valve are coaxially arranged in the cylinder body, the reversing valve is positioned between the piston and the cylinder body, and the reversing valve is used for assisting the piston to reverse;

a braking dead space, a piston rear space for oil inlet and a piston front space are arranged between the cylinder body and the piston;

the reversing valve is provided with an anti-blocking part protruding towards the direction of the piston, the piston is provided with a yielding groove recessed towards the center of the piston, and the anti-blocking part is matched with the yielding groove to prevent the piston from being blocked in a braking dead space.

Compared with the prior art, the anti-jamming structure applied to the hydraulic rock drill has the advantages that the anti-jamming part is arranged on the reversing valve for reversing the auxiliary piston, the yielding groove which is sunken towards the center of the piston is arranged on the piston, when the reversing valve moves axially relative to the piston, the anti-jamming part can act with steps at two ends of the yielding groove so as to generate thrust on the piston, when the piston enters the braking dead cavity, oil is filled in the front cavity or the rear cavity of the piston, hydraulic oil can generate thrust on the reversing valve so as to push out the piston entering the braking dead cavity, and the piston can quickly withdraw after entering the braking dead cavity, so that the situation that the piston is jammed in the braking dead cavity is prevented;

in addition, the setting of the abdication groove shortens the acting path length of the anti-blocking part on the piston, and reduces the friction and the contact area between the anti-blocking part and the piston when the reversing valve moves, thereby reducing the probability of the piston being strained by the reversing valve.

In some alternative embodiments, a braking part is arranged on the peripheral wall of the reversing valve, and a valve braking cavity matched with the braking part is arranged between the cylinder body and the reversing valve.

In some alternative embodiments, the braking portion is a protrusion protruding toward the cylinder;

an oil outlet gap is formed between the top of the braking part and the cylinder body.

In some alternative embodiments, at least one buoyancy groove is arranged on the peripheral wall of the reversing valve;

the buoyancy groove is recessed toward the center of the piston.

In some alternative embodiments, the buoyancy tank has a radial depth of 1 to 4mm.

In some alternative embodiments, the relief groove has a radial depth of 1 to 2mm.

In some optional embodiments, the steps at two ends of the yielding groove are provided with buffer parts, and the surfaces of the buffer parts are inclined surfaces.

In some alternative embodiments, a gap is formed between the lower end of the anti-blocking portion and the yielding groove.

In some alternative embodiments, the bottom of the anti-seize portion is planar.

The anti-jamming structure provided by the application has at least the following technical effects:

the reversing valve is provided with the anti-blocking part matched with the yielding groove of the piston, so that the piston can rapidly withdraw after entering the braking dead space, and the piston is prevented from being blocked in the braking dead space;

the buffer parts are arranged on the steps at the two ends of the abdication groove, and the surfaces of the buffer parts are inclined surfaces, so that when the inclined surfaces of the buffer parts act on the anti-blocking parts, the acting force applied by the anti-blocking parts to the piston along the axial direction is decomposed, the stress concentration of the anti-blocking parts and the piston is reduced, the abrasion force of the reversing valve to the piston can be reduced, the probability of the piston being damaged by pulling is further reduced, and the service life of the piston is further ensured;

through set up buoyancy groove on the switching-over valve, can provide the support force to the switching-over valve to effectively reduce the hydraulic pressure chucking power that the switching-over valve is eccentric to cause.

In a second aspect, the application also provides a hydraulic rock drill comprising an anti-seize arrangement as described in any one of the embodiments above. The hydraulic rock drill has the anti-jamming structure, and the piston of the hydraulic rock drill is not easy to jam in the braking dead space, so that the working efficiency of the rock drill is higher.

Drawings

Fig. 1 is a schematic cross-sectional view of an anti-seize structure for a rock drill according to an embodiment of the application;

FIG. 2 is a schematic cross-sectional view of a piston according to an embodiment of the present application;

FIG. 3 is a schematic cross-sectional view of a reversing valve of an embodiment of the application;

FIG. 4 is an enlarged partial schematic view of FIG. 1;

FIG. 5 is an enlarged partial schematic view of FIG. 2;

FIG. 6 is an enlarged partial schematic view of FIG. 3;

fig. 7 is a schematic cross-sectional view of the connection of the reversing valve brake to the valve brake chamber in accordance with one embodiment of the present application.

Reference numerals:

1. a reversing valve; 2. a cylinder; 3. a piston; 4. braking dead space; 5. a valve braking chamber; 6. a piston front chamber; 7. a piston rear chamber;

11. an anti-seize part; 12. a braking section; 13. a buoyancy tank; 14. an oil outlet gap;

31. a relief groove; 32. a buffer section;

41. front braking dead space; 42. rear braking dead space.

Detailed Description

In order to better understand the technical solutions of the present disclosure, the present disclosure will be described in detail, clearly and completely with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the present disclosure.

In the description of the present application, the description of the first and second is only for the purpose of distinguishing technical features, and should not be construed as indicating or implying relative importance or implying the number of technical features indicated or the precedence of the technical features indicated.

It will be appreciated by those skilled in the art that in the present disclosure, the terms "longitudinal," "transverse," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," etc. refer to an orientation or positional relationship based on that shown in the drawings, which is merely for convenience of description and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore the above terms should not be construed as limiting the present application.

The application is described in further detail below with reference to the accompanying drawings, see for example figures 1 to 7.

In a first aspect, the present application provides an anti-seizing structure for a hydraulic rock drill, which is located in an impact structure of the hydraulic rock drill, capable of having a technical effect of anti-seizing on a piston 3; referring to fig. 1, the anti-jamming structure comprises a piston 3, a cylinder body 2 and a reversing valve 1, wherein the piston 3 and the reversing valve 1 are coaxially arranged in the cylinder body 2, the reversing valve 1 is positioned between the cylinder body 2 and the piston 3, the reversing valve 1 and the piston 3 can move in the cylinder sleeve along the axial direction, the reversing valve 1 moves in the cylinder body 2 to change the oil connection condition of a rear cavity 7 of the piston, the thrust of the rear end face of the piston 3 is switched, and the piston 3 is further assisted to move; a braking dead space 4 is arranged between the cylinder body 2 and the piston 3, two braking dead spaces 4 are respectively arranged at a rear front braking dead space 41 and a rear braking dead space 42, a piston rear space 7 and a piston front space 6 for oil inlet are arranged between the cylinder body 2 and the piston 3, pressure can be applied to the piston 3 and the reversing valve 1 by feeding hydraulic oil into the piston rear space 7 and the piston front space 6 so as to push the piston 3 to move, the front braking dead space 41 is arranged at a position close to the piston front space 6, the rear braking dead space 42 is arranged at a position close to the piston rear space 7, and the two are arranged along the axial direction of the piston 3; the braking dead space 4 can prevent the piston 3 from overriding the rearmost or foremost side, causing the piston 3 to strike the cylinder 2;

as shown in fig. 4, the reversing valve 1 is provided with an anti-seizing portion 11 protruding towards the direction of the piston 3, the piston 3 is provided with a receding groove 31 recessed towards the center of the piston 3, and the anti-seizing portion 11 cooperates with the receding groove 31 to prevent the piston 3 from seizing in the braking dead space 4; when the piston 3 performs impact or return movement and needs to switch the next movement, after oil is fed into the front piston cavity 6 or the rear piston cavity 7, high-pressure oil acts on the reversing valve 1 to generate a moving precursor force for the reversing valve 1, and then the anti-blocking part 11 is matched with the steps at the two ends of the yielding groove 31 to generate an pushing force for the piston 3, so that the piston 3 entering the braking dead cavity 4 is pushed out, the piston 3 can quickly withdraw after entering the braking dead cavity 4, and the situation that the piston 3 is blocked in the braking dead cavity 4 is prevented;

in this embodiment, as shown in fig. 2 and 5, the anti-seizing portion 11 is disposed on the inner peripheral wall of the reversing valve 1, and by disposing the anti-seizing portion 11 to protrude toward the direction of the piston 3, when the reversing valve 1 moves relative to the piston 3, the anti-seizing portion 11 protrudes to act with the relief groove 31, so that the reversing valve 1 can easily push out the piston 3 from the dead space 4, and the volume of the anti-seizing portion 11 is relatively small while ensuring the pushing force of the anti-seizing portion 11 to the piston 3, thereby saving the manufacturing material and manufacturing cost of the reversing valve 1;

in this embodiment, as shown in fig. 3 and 6, two ends of the relief groove 31 form steps with the outer peripheral wall of the piston 3, by providing the relief groove 31, when the anti-seizing portion 11 needs to act on the piston 3 to push out the piston 3 from the dead space 4, the anti-seizing portion 11 can enter the azimuth groove to move along the axial direction of the piston 3, the anti-seizing portion 11 can act on the steps at two ends of the relief groove 31, the anti-seizing portion 11 applies a force to the steps at two ends of the relief groove 31, so as to apply a pushing force to the piston 3, and push out the piston 3 from the dead space 4; the arrangement of the relief groove 31 shortens the acting path length of the anti-blocking part 11 on the piston 3, reduces the friction and the contact area of the reversing valve 1 on the piston 3, and reduces the probability of the piston 3 being damaged by the reversing valve 1.

Further, the radial depth of the relief groove 31 is 1 to 2mm. By reasonably setting the depth of the relief groove 31, on one hand, the processing difficulty can be reduced, and on the other hand, when the piston 3 is expanded by heating, the protrusion of the piston 3 at the relief groove 31 is in interference with the anti-blocking part 11 to damage the piston 3.

Further, as shown in fig. 4, a gap is formed between the lower end of the anti-seizing portion 11 and the relief groove 31; in this embodiment, a gap is formed between the bottom of the relief groove 31 and the lower end of the anti-seizing portion 11, so that, on the one hand, when the reversing valve 1 moves in the axial direction relative to the piston 3, the anti-seizing portion 11 acts on the bottom of the relief groove 31, and the anti-seizing portion 11 rubs with the relief groove 31 to damage the piston 3; on the other hand, in order that oil can enter between the piston 3 and the reversing valve 1, the oil can smoothly act on the anti-blocking part 11 and the step of the yielding groove 31 to generate acting force, so that the reversing valve 1 can play a better role in pushing the piston 3, the speed of the piston 3 withdrawing from the braking dead space 4 is higher, and the response is more sensitive; in addition, the gap enables the oil to circulate between the reversing valve 1 and the cylinder 2, and prevents the oil from being blocked in the piston rear chamber 7.

In another alternative embodiment of the present application, the anti-seize portion 11 is further modified in this embodiment; as shown in fig. 4 and 6, in the cross section along the axial direction of the piston 3, the anti-seizing portion 11 is substantially inverted triangle, and the end of the anti-seizing portion 11 near the piston 3 is smaller, and the end of the anti-seizing portion 11 connected to the reversing valve 1 is larger, so that when the anti-seizing portion 11 acts on the piston 3, the reaction force of the piston 3 to the anti-seizing portion 11 acts on the inclined surface of the anti-seizing portion 11, so that the force can be decomposed, thereby reducing the stress concentration and reducing the probability of breakage of the anti-seizing portion 11.

In another alternative embodiment of the present application, in this embodiment, the anti-blocking portion 11 is further improved, as shown in fig. 4 and 6, the bottom of the anti-blocking portion 11 is a plane, so that when the reversing valve 1 acts on the piston 3, the acting force can be distributed greatly, the end of the anti-blocking portion 11 is not too concentrated in a point, and the probability of breaking the end of the anti-blocking portion 11 can be reduced; when the anti-seizing portion 11 is inadvertently brought into contact with the outer peripheral wall of the piston 3, the contact area between the anti-seizing portion 11 and the piston 3 is relatively large, so that the force applied to the piston 3 is not excessively concentrated at one point, and impact damage to the contact portion of the piston 3 is reduced.

Further, as shown in fig. 6, the connection heights of the anti-seizing portion 11 and the reversing valve 1 on the front and rear sides are not uniform, and the connection height of the anti-seizing portion 11 and the front end of the reversing valve 1 is greater than the connection height of the anti-seizing portion with the rear end, so that the anti-seizing portion 11 can be conveniently processed.

In another alternative embodiment of the present application, as shown in fig. 4 and 5, buffer parts 32 are provided at two ends of the yielding groove 31, and the surface of the buffer part 32 is an inclined surface; when the buffer part 32 makes the anti-blocking part 11 act on the piston 3, the inclined surfaces of the anti-blocking part 11 and the buffer part 32 act, and the acting force applied by the anti-blocking part 11 to the piston 3 along the axial direction is decomposed, so that the stress concentration of the anti-blocking part 11 and the piston 3 is reduced, the abrasion force of the reversing valve 1 to the piston 3 can be reduced, the probability of the piston 3 being strained is further reduced, and the service life of the piston 3 is further ensured.

In another alternative embodiment of the present application, as shown in fig. 4, 6 and 7, a braking part 12 is arranged on the peripheral wall of the reversing valve 1, and a valve braking cavity 5 matched with the braking part 12 is arranged between the cylinder body 2 and the reversing valve 1; by pumping out the oil from the valve braking cavity 5, the reversing valve 1 can extrude the hydraulic oil in the valve braking cavity 5 through clearance fit between the braking part 12 of the reversing valve 1 and the valve braking cavity 5 after reversing, thereby realizing stable deceleration of the reversing valve 1 to reach a limit position and reducing damage caused by collision of the reversing valve 1.

Further, as shown in fig. 4, 6, and 7, the braking portion 12 is a protrusion protruding toward the cylinder 2; by arranging the braking part 12 to protrude towards the cylinder body 2, the braking part 12 can directly act with the side wall of the valve braking cavity 5 when the reversing valve 1 moves, so that the volume of the braking part 12 is relatively small, and the manufacturing materials and the manufacturing cost of the reversing valve 1 are saved;

as shown in fig. 7, an oil outlet gap 14 is formed between the top of the braking part 12 and the cylinder body 2, and unfilled corners are formed at two ends of the top of the braking part 12 along the axial direction, and as shown in fig. 7, when the side wall of the braking part 12 is attached to the inner wall of the valve braking cavity 5, the unfilled corners are communicated with the oil outlet gap 14 to form an oil outlet channel, so that hydraulic oil can flow out of the oil outlet channel when the braking part 12 acts with the valve braking cavity 5 to extrude the hydraulic oil; the contact surface between the brake portion 12 and the valve brake chamber 5 is a flat surface, so that the contact area between the brake portion 12 and the valve brake chamber 5 can be increased, and the hydraulic oil in the valve brake chamber 5 can be squeezed out as much as possible.

In another alternative embodiment of the present application, as shown in fig. 3 and 6, at least one buoyancy groove 13 is provided on the outer peripheral wall of the reversing valve 1, the buoyancy groove 13 is recessed toward the central axis direction of the piston 3, the buoyancy groove 13 is provided along the outer peripheral wall of the piston 3, and the buoyancy groove 13 is annular; through setting up buoyancy tank 13 on switching-over valve 1, hydraulic oil can carry out in the buoyancy tank 13 to can provide to switching-over valve 1 and hold in the palm the holding force, thereby effectively reduce switching-over valve 1 and produce decentration owing to the side force, the hydraulic pressure chucking power of production then, with this chucking phenomenon that prevents switching-over valve 1 production.

Further, the radial depth of the buoyancy tank 13 is 1 to 4mm; through the reasonable degree of depth that sets up buoyancy groove 13, can adjust the holding and holding up the power to piston 3, set up the degree of depth in this scope with buoyancy groove 13, can make when filling hydraulic oil in the buoyancy groove 13, hold up the effect best to piston 3.

Further, as shown in fig. 6, the surface of the buoyancy tank 13 is an arc surface, so that the contact area between the hydraulic oil and the buoyancy tank 13 can be increased, and the supporting force on the reversing valve 1 can be further increased.

Further, as shown in fig. 3 and 6, the buoyancy grooves 13 are arranged at two sides of the braking portion 12, so that the overall bearing and supporting force of the reversing valve 1 can be effectively ensured to be relatively even, and the reversing valve 1 is balanced in stress. In actual use, the number of buoyancy tanks 13 on both sides of the braking portion 12 and the positions of the buoyancy tanks 13 are reasonably set according to the setting positions of the braking portion 12, so that the whole reversing valve 1 can be stressed and balanced. In the present application, since the braking portion 12 is provided with the offset, two buoyancy grooves 13 are provided at the front side of the braking portion 12, and one buoyancy groove 13 is provided at the rear side of the braking portion 12, so that the reversing valve 1 can be balanced in force as much as possible.

In the use process of the anti-jamming structure, the anti-jamming structure is shown in combination with fig. 4:

when the piston 3 moves backwards and enters the rear braking dead space 42, oil is returned from the valve braking space 5, hydraulic oil in the valve braking space 5 at the front end is reduced and enters oil into the valve braking space 5 at the rear end of the reversing valve 1, and meanwhile, the hydraulic oil flows to the anti-blocking part 11 of the reversing valve 1, pressure is generated on the reversing valve 1, and the reversing valve 1 moves forwards under the high pressure action of the hydraulic oil;

when the reversing valve 1 moves to be in contact with the buffer part 32 at the front end of the relief groove 31, the anti-blocking part 11 acts on the buffer part 32 of the relief groove 31 to generate forward acting force to push the piston 3 forward, so that the piston 3 can be smoothly and rapidly separated from the rear braking dead space 42, hydraulic oil enters the rear braking dead space 42 to generate pressure on the step of the piston 3 acted by the piston 3 and the rear braking dead space 4, and the piston 3 is accelerated to move forward.

In a second aspect, the present application provides a hydraulic rock drill comprising an anti-seize arrangement as in any one of the embodiments described above. The rock drill provided by the application has an anti-jamming structure, the piston 3 is not easy to jam in the braking dead space 4, and the time and labor consumed by the jamming of the piston 3 are reduced, so that the working efficiency of the rock drill is greatly improved.

It should be noted that, in the case that the embodiments of the present application do not conflict with the solutions and the technical solutions can coexist, new embodiments may be arbitrarily combined.

The foregoing has outlined rather broadly the more detailed description of the application in order that the detailed description of the application that follows may be better understood, and in order that the present application may be better understood. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the application can be made without departing from the principles of the application and these modifications and adaptations are intended to be within the scope of the application as defined in the following claims.

Claims (10)

1. The anti-jamming structure is applied to a hydraulic rock drill and is characterized by comprising a piston (3), a cylinder body (2) and a reversing valve (1), wherein the piston (3) and the reversing valve (1) are coaxially arranged in the cylinder body (2), the reversing valve (1) is positioned between the piston (3) and the cylinder body (2), and the reversing valve (1) is used for assisting the piston (3) to carry out reversing;

a braking dead space (4), a piston rear space (7) for oil inlet and a piston front space (6) are arranged between the cylinder body (2) and the piston (3);

the reversing valve (1) is provided with an anti-blocking part (11) protruding towards the direction of the piston (3), the piston (3) is provided with a yielding groove (31) recessed towards the center of the piston (3), and the anti-blocking part (11) is matched with the yielding groove (31) to prevent the piston (3) from being blocked in the braking dead space (4).

2. The anti-seize structure as claimed in claim 1, characterized in that,

a braking part (12) is arranged on the peripheral wall of the reversing valve (1), and a valve braking cavity (5) matched with the braking part (12) is arranged between the cylinder body (2) and the reversing valve (1).

3. The anti-seize structure as claimed in claim 2, characterized in that,

the braking part (12) is a bulge protruding towards the cylinder body (2);

an oil outlet gap (14) is formed between the top of the braking part (12) and the cylinder body (2).

4. The anti-seize structure as claimed in claim 1, characterized in that,

at least one buoyancy groove (13) is formed in the peripheral wall of the reversing valve (1);

the buoyancy groove (13) is recessed toward the center of the piston (3).

5. The anti-sticking structure according to claim 4, wherein,

the radial depth of the buoyancy groove (13) is 1 to 4mm.

6. The anti-seize structure as claimed in claim 1, characterized in that,

the radial depth of the relief groove (31) is 1 to 2mm.

7. The anti-seize structure as claimed in claim 1, characterized in that,

the steps at two ends of the yielding groove (31) are provided with buffer parts (32), and the surfaces of the buffer parts (32) are inclined surfaces.

8. The anti-seize structure as claimed in claim 1, characterized in that,

a gap is formed between the lower end of the anti-blocking part (11) and the yielding groove (31).

9. The anti-seize structure as claimed in claim 1, characterized in that,

the bottom of the anti-blocking part (11) is a plane.

10. A hydraulic rock drill, characterized in that it comprises an anti-seize structure according to any one of the preceding claims 1-9.