CN115898251A - Impact device of rock drill and rock drill - Google Patents

Abstract

The application discloses percussion device of rock drill, stop sleeve, cylinder liner and two at least back stop sleeves including preceding stop sleeve, cylinder liner and, preceding stop sleeve, arbitrary back stop sleeve and cylinder liner coaxial connect gradually, back stop sleeve in set up the locking groove that suits with the drilling tool, the rear end of drilling tool is located in the cavity that preceding stop sleeve and back stop sleeve constitute, the extreme position that the drilling tool moved backward has been restricted to the bottom surface of locking groove, the locking groove of seting up on each back stop sleeve is in the axial degree of depth diverse of back stop sleeve. The standardized rear stop sleeve can complete power regulation of equipment only by replacing the rear stop sleeve, and is convenient to adjust.

Description

Impact device of rock drill and rock drill

Technical Field

The application relates to the field of rock drills, in particular to an impact device of a rock drill and the rock drill.

Background

Rock drills are tools used to directly mine rock material. It drills blastholes in rock formations to deposit explosives to blast the rock to complete the exploitation of rock material or other stone work. Rock drills work according to the impact crushing principle. When the drill bit works, the piston does high-frequency reciprocating motion and continuously impacts the drill bit shank. Under the action of impact force, the pointed wedge-shaped drill bit crushes and drills the rock to a certain depth to form a dent. After the piston is withdrawn, the drill rod rotates by a certain angle, the piston moves forwards, and a new dent is formed when the drill rod is impacted again. The segmental rock mass between the two indents is sheared by the horizontal component force generated on the drill bit. The piston continuously impacts the drill bit shank and continuously inputs compressed air or pressure water from the central hole of the drill bit to discharge rock slag out of the hole, namely, a circular drill hole with a certain depth is formed.

Related art such as application (patent) No.: chinese patent CN202210577445.0 discloses a "hydrostatic suspension piston type hydraulic breaking hammer", which includes: 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. The area where the cylinder body is matched with the piston head is provided with more than or equal to two circles, and each circle is uniformly provided with more than two static pressure suspension cavities for supporting the piston.

The stamping piston of the rock drill in the prior art mainly considers the problems of lubrication, impact force and the like. In the prior art, the adjustment of the frequency and the impact energy of the equipment is usually realized by a hydraulic system, such as the following (patent) application numbers: CN201410071079.7, which is a "hydraulic control system with continuously adjustable rock drilling machine power", discloses a variable pump including LS control, a control valve block, a throttle hole and a pilot control handle, wherein the control valve block includes a logic valve, an overflow valve, a balance valve, a hydraulic directional valve, a shuttle valve and a pressure reducing valve; the invention can continuously control the impact pressure of the rock drill between the set lowest impact pressure and the set highest impact pressure according to the moving angle of the pilot operation handle, and the balance valve amplifies the control pressure of the operation handle, thereby changing the control pressure of the LS control pressure of the variable displacement pump and the control pressure of the logic valve, and continuously changing the impact pressure of the rock drill between the set lowest impact pressure and the set highest impact pressure, and further achieving the purpose of continuously adjusting the impact power of the rock drill. The invention can flexibly adjust the impact power of the rock drilling machine under the condition of special rocks, saves energy, obtains the optimal rock drilling effect and improves the production efficiency of the rock drilling machine.

In the prior art, the power adjustment of a piston is changed, starting from a hydraulic system, and the impact performance parameters of the rock drill are changed by changing the oil inlet pressure and the flow of the hydraulic system, so that the impact energy and the impact frequency of the rock drill are reduced and increased simultaneously, and the limit of overhigh pressure on higher requirements of the hydraulic system exists simultaneously. Therefore, the applicability is poor, and various use conditions cannot be met. The inventor of the application changes the structure of the impact device, quickly realizes the power regulation of the impact device in the rock drill, and can realize the single parameter promotion of the impact energy and the impact frequency on the premise of ensuring that the external oil supply pressure condition is unchanged (unchanged flow, unchanged pressure and unchanged external system). And although the change of the impact energy of the piston requires stroke change, so that the change of the periodic total displacement is caused, the frequency and the impact energy are reversely changed, the total flow can be ensured not to be changed greatly, a hydraulic system is not required to be modified, the adjustment is simpler, and the proper performance parameters can be obtained by directly matching the rock drill according to the working condition by the conventional system.

Disclosure of Invention

The technical problem that this application will be solved provides an impact device and rock drill of rock drill, and the power regulation of equipment can be accomplished to standardized back stop sleeve, only need to change rear end stop sleeve, and the adjustment is convenient.

The technical scheme adopted by the application is as follows: the utility model provides an impact device of rock drill, includes preceding stop collar, cylinder liner and two at least back stop collars, preceding stop collar, arbitrary back stop collar and cylinder liner coaxial connect gradually, back stop collar in set up the retaining groove that suits with the drilling tool, the rear end of drilling tool is located the cavity that preceding stop collar and back stop collar constitute, the extreme position that the drilling tool moved backward has been restricted to the bottom surface of retaining groove, the retaining groove that sets up on each back stop collar is the degree of depth variation in the back stop collar axial direction.

Compared with the prior art, the rear stop sleeve has the advantages that at least two rear stop sleeves are arranged, and the depth of the stop groove formed in each rear stop sleeve in the axial direction is different from that of the rear stop sleeve. The bottom surface of the stop groove limits the extreme position of the drill tool moving backwards, and the extreme position of the drill tool at the rear end influences the striking point of the piston in the whole working process. The position of a striking point of the piston is adjusted, so that the moving distance of the piston is influenced, and the frequency of the piston impacting the drilling tool is further influenced; the distance that the piston moves in the oil directly influences the energy storage (kinetic energy) of the piston. The change of the rear stop sleeve realizes the adjustment of the frequency and the impact energy of the equipment. This application is designed into standardized external member with back locking cover, only needs supporting change back locking cover can accomplish the power regulation of equipment, and the adjustment is convenient.

In some embodiments of the present application, the outer dimensions of each rear stop sleeve are substantially identical. This application will be back the locking cover design and be standardized external member, avoid its external dimension to cause the influence to the structure function of this application.

In some embodiments of the present application, the present application includes a head section and at least two tail sections, the head section is connected with any one of the tail sections to form a piston installed in a cylinder liner, the tail section is provided with a first signal channel, and the first signal channel communicates the outer circumferential surface of the piston with the rear end surface of the piston; the lengths of the first signal channels on different tail sections are different, and the tail sections correspond to the rear stop sleeves one by one.

In the present application, the rear stop sleeve is generally replaced simultaneously with the synchronous replacement of the tail sections, and the outer dimensions of the tail sections are identical, and the difference is only the length of the first signal channel. I.e. the end section in this application is also a standardized kit.

The rear stop sleeve is selected according to the use working condition, the corresponding piston tail section is selected in a matched mode, the position of the first signal oil port is correspondingly adjusted on the premise that the change of the striking point of the piston is guaranteed, the impact point moment of the rock drill is guaranteed to be the moment with the maximum speed in the motion process of the piston, and the performance of the rock drill is exerted to the maximum extent.

Specifically, if the distance for inserting the piston in the intermediate-frequency rear stop sleeve is X, the length of the first signal channel, that is, the distance from the outer circumferential surface of the piston, which is communicated with the rear end surface of the piston, to the rear end surface of the piston is Y. Then, the distance for inserting the piston in the high-frequency rear stop sleeve is X-N, and the length of the first signal channel is Y + N; the distance for inserting the piston in the low-frequency rear stop sleeve is X + M, and the length of the first signal channel is Y-M. Since the depth of the stop groove of the rear stop sleeve affects the moving distance of the piston, the length of the first signal channel (the distance from the rear end face of the piston) needs to be changed correspondingly when the first signal channel needs to feed back a signal that the first signal port normally works.

In some embodiments of the present application, the drill tool includes a mounting portion, the mounting portion is located at the rear end of the entire drill tool, the diameter of the mounting portion is larger than the diameter of other portions of the drill tool, and the mounting portion is matched with splines and the like to transmit rotation. The front stop sleeve and the rear stop sleeve are connected to form a limiting cavity for accommodating the mounting part, and the limiting cavity limits the movement stroke of the drilling tool.

Specifically, the stop grooves form the limit cavities, and the limit cavities on different rear stop sleeves have different depths in the axial direction. The depth of the stop groove determines the length of the whole limit cavity, namely the stroke length of the drill tool movement.

In some embodiments of the present application, the rear end face of the mounting portion is a circular truncated cone structure, and the rear end face of the mounting portion includes a plane and an inclined plane around the plane outer ring. The plane of the rear end face of the mounting part is an impact surface contacted with the piston, and the bottom surface of the stop groove is adapted to the inclined surface of the rear end face of the mounting part. In this application, the design of the inclined surface also serves a guiding function, ensuring that the drill tool is coaxial with the piston when the drill tool is moved backwards to the extreme position.

In some embodiments of the application, the piston is arranged coaxially with the drill tool, and the piston reciprocates in the cylinder sleeve to drive the drill tool to impact the rock wall.

And the tail section is provided with a second signal channel which communicates the peripheral surface of the piston with the rear end surface of the piston. And in the movement process of normal work of the piston, the first signal oil port is communicated with the first signal channel at intervals. The first signal channel is a signal that the piston normally works. And under the idle-driving state (abnormal operation) of the piston, the second signal oil port is communicated with the first signal channel or not.

In some embodiments of the present application, the head section surface is provided with a gap preventing shaft, the gap preventing shaft comprises a plurality of coaxially arranged ring members, and a gap exists between two adjacent ring members; the nominal diameter value of the ring is equal to the diameter of a dead cavity of the cylinder sleeve.

The piston is provided with an idle-driving preventing shaft and is matched with a dead cavity of the cylinder sleeve, and before the idle-driving drilling tool impacts the front end stop sleeve, the piston enters the dead cavity to perform energy consumption in advance, so that the damage of parts is reduced.

From a near drilling tool to a far drilling tool, the outer diameters of the ring pieces are sequentially increased; the diameter of the ring furthest from the drill tool has a value equal to the diameter of the dead space of the cylinder block. Preferably, the idle driving prevention shaft comprises at least three coaxially arranged ring members. The whole braking is divided into at least three stages between the idle-stop shafts, the clearance is gradually reduced, the stability of the piston braking can be effectively ensured, and the instantaneous increase of the pressure is avoided.

Specifically, the idle driving prevention shaft is in clearance fit with the dead space; the clearance between the idle driving preventing shaft and the dead cavity is 0.02 mm-0.1 mm.

A pressure equalizing groove is arranged between two adjacent ring pieces; the outer diameter of the pressure equalizing groove is smaller than that of the ring piece. Meanwhile, the pressure equalizing grooves are arranged between the shafts, so that hydraulic clamping force generated by piston eccentricity due to uneven oil distribution on the piston shafts can be effectively reduced.

In some embodiments of the present application, the inner wall surface of the cylinder liner is sequentially provided with a front cavity, a rear cavity, a first signal oil port, a first high-pressure oil port, a first oil return port, a second signal oil port, a second oil return port, and a second high-pressure oil port from front to back.

The front cavity is connected with the oil inlet branch, the rear cavity is connected with the oil return branch, the first signal oil port and the second signal oil port are communicated through an oil duct arranged on the cylinder sleeve, the first high-pressure oil port and the second high-pressure oil port are communicated with the oil inlet branch, and the first oil return port and the second oil return port are communicated with the oil return branch. The oil inlet branch is connected with constant high-pressure oil, the oil return branch is connected with constant low-pressure oil, and the oil return pressure is approximately equal to 0.

The above embodiments may be combined arbitrarily, based on common general knowledge in the art.

A rock drill includes an adjustable percussion device.

Drawings

The present application will be described in further detail below with reference to the drawings and preferred embodiments, but those skilled in the art will appreciate that the drawings are only drawn for the purpose of illustrating the preferred embodiments and therefore should not be taken as limiting the scope of the present application. Furthermore, unless specifically stated otherwise, the drawings are merely schematic representations based on conceptual representations of elements or structures depicted and may contain exaggerated displays and are not necessarily drawn to scale.

FIG. 1 is a schematic structural view of an adjustable impact device employing a mid-frequency rear stop sleeve;

FIG. 2a is a schematic structural diagram of a middle frequency rear stop sleeve;

FIG. 2b is a schematic diagram of the structure of the mid-frequency end section;

FIG. 3 is a schematic diagram of an adjustable impact device employing a low frequency rear stop sleeve;

FIG. 4a is a schematic structural view of a low frequency rear stop collar;

FIG. 4b is a schematic diagram of the low frequency end section;

FIG. 5 is a schematic structural view of an adjustable impingement device employing a high frequency rear stop sleeve;

FIG. 6a is a schematic structural diagram of a high frequency rear stop sleeve;

fig. 6b is a schematic diagram of the high frequency end section.

FIG. 7 is a schematic view of an adjustable impact device of the present application;

FIG. 8 is an enlarged view of a portion of FIG. 7 at A;

FIG. 9 is a schematic view of the piston of the present application;

FIG. 10 is a first enlarged view of a portion of the adjustable impingement device of the present application;

FIG. 11 is a second enlarged view of a portion of the adjustable impingement device of the present application;

fig. 12 is a schematic view of the diverter valve.

Wherein the reference numerals are specified as follows:

2. a cylinder liner; 3. a diverter valve; 4. a piston; 401. a head section; 402. a tail section; 4a, preventing idle driving between shafts; 4b, a contraction section 7 and an oil inlet branch; 8. an oil return branch; 9. a drill tool; 9a, a mounting part;

11. an oil path; 12. a conduction groove; 13. a first signal path; 14. a second signal path;

21. a front cavity; 22. a rear cavity; 23. a first signal oil port; 24. a first high-pressure oil port; 25. a first oil return port; 26. a second signal oil port; 27. a second oil return port; 28. a second high-pressure oil port;

31. a front stop sleeve; 32. a rear stop sleeve; 33. a stopper groove; 34. a limiting cavity; 35. a ring member; 36. a dead space; 37. a pressure equalizing groove;

41. a primary oil distribution sleeve; 42. an oil distribution ring; 43. a secondary oil distribution sleeve; 44. pushing the valve rod; 45. a limiting groove; 46. a concave limiting cavity; 47. a first channel; 48. a second channel; 49. a third channel; 50. and a fourth channel.

Detailed Description

The present application will now be described in detail with reference to the accompanying drawings.

In order to make the objects, technical solutions and advantages of the present application more apparent, the present application is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present application and are not intended to limit the present application.

A percussion device for rock drilling machines, as shown in figures 1 to 12: the drill bit comprises a front stop sleeve 31, a cylinder sleeve 2 and at least two rear stop sleeves 32, wherein the front stop sleeve 31, any rear stop sleeve 32 and the cylinder sleeve 2 are coaxially and sequentially connected, the rear end of a drill bit 9 is positioned in a cavity formed by the front stop sleeve 31 and the rear stop sleeve 32, a piston 4 and the drill bit 9 are coaxially arranged, the piston 4 is installed in the cylinder sleeve 2 and is coaxially arranged with the drill bit 9, and the piston 4 reciprocates in the cylinder sleeve 2 to drive the drill bit (9) to impact a rock wall. The rear stop sleeve 32 is internally provided with a stop groove 33 corresponding to the drill bit 9, the bottom surface of the stop groove 33 limits the backward movement limit position of the drill bit 9, and the depth of the stop groove 33 arranged on each rear stop sleeve 32 in the axial direction of the rear stop sleeve is different. The bottom surface of the stop groove 33 limits the extreme position of the drill tool 9 in the backward direction, and the extreme position of the drill tool 9 in the rear end will affect the striking point of the piston 4 in the whole working process. The position of the striking point of the piston 4 is adjusted, so that the moving distance of the piston 4 is influenced, and the frequency of the piston 4 impacting the drilling tool 9 is further influenced; the distance that the piston 4 moves in the oil directly influences the energy storage kinetic energy of the piston 4. The change in the rear stop sleeve 32 enables adjustment of the frequency and impact energy of the device. This application is the standardized external member of back stop sleeve 32 design, only needs supporting change back stop sleeve 32 and initiative piston 4 can accomplish the power regulation of equipment, and the adjustment is convenient.

The application has wider applicability, and the stop sleeve 32 (the depth of the stop groove 33 is moderate as shown in figure 1) is suitable for most working conditions after the intermediate frequency is standard-matched; for soft rock strata, a high-frequency rear stop sleeve 32 is selected (the depth of a stop groove 33 is deeper, as shown in figure 5); for hard rock formations, a low frequency rear stop sleeve 32 is selected (the depth of the stop groove 33 is shallow, as shown in fig. 3). The gear kit is reasonably selected, and the working efficiency can be effectively improved.

The outer dimensions of each rear stop sleeve 32 are identical. The rear stop sleeve 32 is designed into a standardized sleeve, and the influence of the external dimension on the structural function of the rear stop sleeve is avoided.

The drill tool 9 comprises a mounting part, the mounting part is positioned at the rear end of the whole drill tool 9, and the diameter of the mounting part is larger than that of other parts of the drill tool 9. The front stop sleeve 31 and the rear stop sleeve 32 are connected to form a limit cavity 34 for accommodating the mounting part, and the limit cavity 34 limits the movement stroke of the drill tool 9.

Specifically, the stop grooves 33 form the limit cavities 34, and the depth of the limit cavities 34 on different rear stop sleeves 32 in the axial direction is different. The depth of the stop groove 33 determines the length of the entire limit chamber 34, i.e. the length of the stroke of the movement of the drill tool 9.

The rear end face of installation department be round platform structure, the rear end face of installation department includes the plane and centers on the inclined plane at the planar outer lane. The plane of the rear end surface of the mounting part is a collision surface contacted with the piston 4, and the bottom surface of the stop groove 33 is adapted to the inclined surface of the rear end surface of the mounting part. In the present application, the design of the inclined surface also serves a guiding function, ensuring that the drill tool 9 is coaxial with the piston 4 when the drill tool 9 is moved backwards to the extreme position.

In the second embodiment, as shown in fig. 7 to 12, an idle-driving preventing shaft chamber 4a is arranged on the surface of the piston 4, the idle-driving preventing shaft chamber 4a includes a plurality of coaxially arranged ring members 35, and a space exists between two adjacent ring members 35; the nominal value of the diameter of the ring 35 is equal to the diameter of the dead space 36 of the liner 2.

The piston 4 is provided with an idle-driving preventing shaft space 4a and is matched with a dead cavity 36 of the cylinder sleeve 2, and before the idle-driving drilling tool 9 impacts a front end stop sleeve, the piston 4 enters the dead cavity 36 to perform energy consumption in advance, so that the damage of parts is reduced.

The outer diameters of the ring pieces 35 increase in sequence from the proximal drill tool 9 to the distal drill tool 9; the diameter of the ring 35 furthest from the drill tool 9 has a value equal to the diameter of the dead space 36 of the cylinder block. Preferably, the lost motion prevention shafting 4a of the present application comprises at least three coaxially arranged ring members 35. The anti-idle shaft hitting room 4a divides the whole braking into at least three stages, the clearance is gradually reduced, the braking stability of the piston 4 can be effectively ensured, and the instantaneous increase of the pressure is avoided.

Specifically, the idle driving preventing shaft room 4a is in clearance fit with the dead space 36; the clearance between the idle driving preventing shaft space 4a and the dead space 36 is 0.02 mm-0.1 mm.

A pressure equalizing groove 37 is arranged between two adjacent ring pieces 35; the outer diameter of the pressure equalizing groove 37 is smaller than the outer diameter of the ring member 35. Meanwhile, the pressure equalizing grooves 37 are arranged between the shafts, so that the hydraulic clamping force generated by eccentricity of the piston 4 due to uneven oil distribution on the piston 4 between the shafts can be effectively reduced.

The rest of the second embodiment is the same as the first embodiment.

In the third embodiment, as shown in fig. 1 to 6b, a front cavity 21, a rear cavity 22, a first signal oil port 23, a first high-pressure oil port 24, a first oil return port 25, a second signal oil port 26, a second oil return port 27, and a second high-pressure oil port 28 are sequentially formed on the inner wall surface of the cylinder liner 2 from front to back.

The front cavity 21 is connected with the oil inlet branch, the rear cavity 22 is connected with the oil return branch 8, the first signal oil port 23 and the second signal oil port 26 are communicated through an oil duct arranged on the cylinder sleeve 2, the first high-pressure oil port 24 and the second high-pressure oil port 28 are communicated with the oil inlet branch, and the first oil return port 25 and the second oil return port 27 are communicated with the oil return branch 8. The oil inlet branch is connected with constant high-pressure oil, the oil return branch 8 is connected with constant low-pressure oil, and the oil return pressure is approximately equal to 0.

The rear end of the piston 4 is respectively provided with a first signal channel 13 and a second signal channel 14, and the first signal channel 13 and the second signal channel 14 respectively communicate the peripheral surface of the piston 4 with the rear end surface of the piston 4. During the movement of the piston 4 in normal operation, the first signal oil port 23 is communicated with the first signal passage 13 at any time. The first signal path 13 is a signal that the piston 4 is operating normally. In the idle-striking state (abnormal operation) of the piston 4, the second signal oil port 26 is communicated with the first signal passage 13.

In the present application, in order to facilitate the fitting of the rear stop sleeve, the piston 4 is not a fixed integral structure, and a section provided with the first signal channel 13 and other parts of the piston are of a sectional structure, so that the rear stop sleeve 32 is convenient to replace part of the piston structure. Specifically, the piston 4 includes a head section 401 and a tail section 402 which are independently arranged, and the first signal path 13 and the second signal path 14 are arranged on the tail section 402.

The present application includes at least two tail sections 402, the lengths of the first signal paths 13 on different tail sections 402 are different, and the tail sections 402 correspond to the rear stop sleeves 32 one to one.

In the present application, as shown in fig. 2a and 2b, if the distance by which the piston 4 is inserted into the intermediate-frequency rear stopper sleeve 32 is X, the length of the first signal path 13, that is, the distance from the outer peripheral surface of the piston 4 communicating with the rear end surface of the piston 4 to the rear end surface of the piston 4 is Y. Then, as shown in FIG. 6a, the distance for inserting the piston 4 in the high frequency rear stop sleeve 32 is X-N, and as shown in FIG. 6b, the length of the first signal channel 13 is Y + N; as shown in fig. 4a, the distance in the low frequency rear stop sleeve 32 for insertion of the piston 4 is X + M, while as shown in fig. 4b, the length of the first signal path 13 is Y-M. Since the depth of the stop groove 33 of the rear stop sleeve 32 affects the moving distance of the piston 4, the length of the first signal channel 13 (the distance from the rear end surface of the piston 4) is changed correspondingly when the first signal channel 13 feeds back a signal that the first signal port 23 normally works.

The general parameters for the jack drill to select the rear stop sleeve 32 and the tail section 402 are provided as follows: the intermediate frequency gear, X and Y are obtained according to the standard design of the rock drill, in order to ensure the adjustability, X is generally 4-10mm, and Y is generally selected to be 30-40mm. N and M are positive values, N is generally 1-4mm, M is generally 0-10mm, and N and M are not necessarily equal, after N is adjusted, the situation that the impact point of the piston is just close to the maximum speed position of the piston 4 under the stroke is ensured, and the position of the first signal oil port 23 is adjusted accordingly, the situation that the impact point is close to the maximum speed position of the piston 4 is ensured, and N is generally equal to about 0.5-3 times of M

The other contents of the third embodiment are the same as those of the first embodiment or the second embodiment.

The fourth embodiment, as shown in fig. 1 to 12, comprises a cylinder sleeve 2, a reversing valve 3 and a piston 4, wherein the piston 4 and the reversing valve 3 are coaxially arranged in the cylinder sleeve 2. The reversing valve 3 and the piston 4 are coaxially arranged, and both the reversing valve 3 and the piston 4 can move in the cylinder sleeve 2 along the axial direction.

An oil inlet branch 7 and an oil return branch 8 are formed in the cylinder sleeve 2, and oil passes through the cylinder sleeve 2 to contact with the piston 4 and the reversing valve 3. The change valve 3 moves in the cylinder sleeve 2, the movable change valve 3 changes the connection condition of oil, the switching of the thrust of the rear end face of the piston 4 is realized, and the whole movement of the piston 4 is further assisted.

In the present application, the side of the piston 4 close to the drill tool 9 is referred to as the front side, and correspondingly, the side of the piston 4 far from the drill tool 9 is referred to as the rear side. The front end of the piston 4 is connected with a drilling tool 9, and the rear end of the piston 4 is connected with the reversing valve 3 in a contact mode at intervals.

The reversing valve 3 is provided with an oil way 11, and the oil way 11 is communicated with the front end face and the rear end face of the reversing valve 3. Furthermore, the front end of the reversing valve 3 is provided with a contact surface, the contact surface is contacted with the piston 4, the contact surface is provided with a conduction groove 12, and the conduction groove 12 is communicated with the oil path 11 and the periphery of the reversing valve 3. In the state that the reversing valve 3 is in contact with the piston 4, although a corresponding sealing structure is not specially made on the structure, in the working process, the situation that oil cannot circulate between the contact surfaces of the reversing valve 3 still occurs. Therefore, the present application is additionally provided with the conduction groove 12, so that the oil can smoothly flow through the conduction groove 12 in the working process, that is, the oil on the periphery of the reversing valve 3 is in a mutual conduction state with the oil path 11.

The inner wall surface of the cylinder sleeve 2 is sequentially provided with a front cavity 21, a rear cavity 22, a first signal oil port 23, a first high-pressure oil port 24, a first oil return port 25, a second signal oil port 26, a second oil return port 27 and a second high-pressure oil port 28 from front to back.

The front cavity 21 is connected with the oil inlet branch 7, the rear cavity 22 is connected with the oil return branch 8, the first signal oil port 23 and the second signal oil port 26 are communicated through an oil duct arranged on the cylinder sleeve 2, the first high-pressure oil port 24 and the second high-pressure oil port 28 are communicated with the oil inlet branch 7, and the first oil return port 25 and the second oil return port 27 are communicated with the oil return branch 8. The oil inlet branch is connected with constant high-pressure oil, the oil return branch is connected with constant low-pressure oil, and the oil return pressure is approximately equal to 0.

The piston 4 is provided with an idle-driving preventing shaft space 4a corresponding to the front cavity 21, the diameter of the idle-driving preventing shaft space 4a is the maximum diameter of the piston 4, and the idle-driving preventing shaft space 4a is positioned in the front cavity 21. During the whole movement process of the normal work of the piston 4, the piston is limited by the front cavity 21 and is always in the front cavity 21.

The piston 4 is provided with a contraction section 4b corresponding to the rear cavity 22, and the diameter of the contraction section 4b is smaller than that of the piston 4 adjacent to the contraction section 4 b. Throughout the movement of piston 4 during normal operation, the diameter of constriction 4b is smaller and constriction 4b is not constrained by back cavity 22 and movement may be out of the range of back cavity 22.

Specifically, in an environment where oil is full of oil, the acting area of the oil on the rear end face of the piston 4 is larger than that of the inner contraction section 4b of the rear cavity 22, and the acting area of the oil on the inner contraction section 4b of the rear cavity 22 is larger than that of the anti-idle hitting shaft chamber 4a of the front cavity 21.

Because the action area of the switching oil pressure end face (rear end face) is large, the oil pressure required by the same action thrust is lower, the flow is larger, the lower action oil pressure can reduce the damage of parts caused by high-pressure impact to a certain extent, and the consumption of the parts is reduced.

The rear end of the piston 4 is respectively provided with a first signal channel 13 and a second signal channel 14, and the first signal channel 13 and the second signal channel 14 respectively communicate the peripheral surface of the piston 4 with the rear end surface of the piston 4. During the movement of the piston 4 in normal operation, the first signal oil port 23 is communicated with the first signal passage 13 at any time. The first signal path 13 is a signal that the piston 4 is operating normally. In the idle-striking state (abnormal operation) of the piston 4, the second signal oil port 26 is communicated with the first signal passage 13.

The rear end surface of the piston 4 is communicated with the oil path 11 of the reversing valve 3, and the second signal channel 14 is communicated with the rear end of the reversing valve 3.

The reversing valve 3 and the piston 4 are coaxially arranged, and the front cavity 22 and the rear cavity 22 of the reversing valve 3 alternately change oil to realize the movement of the reversing valve 3. The piston 4 and the reversing valve 3 are coaxially arranged, so that the structure is simple and compact, and the disassembly, assembly and maintenance are simpler. The center height is lower in the aspect of the external dimension of the application.

In this application, become oil pocket position still less in turn to this kind of turn becomes oil pocket area of contact big, and the large-traffic characteristics of this kind of rock drill low pressure again in addition, the terminal surface oil pressure is more stable, and the sudden change is littleer, and the switching-over motion is more stable, has reduced the possibility that negative pressure appears in this terminal surface, and the cooperation choke valve effect cavity negative pressure probability appears and has reduced the possibility that cavitation appears in the rock drill cavity to a certain extent.

The present application also includes a push valve assembly. In the cylinder sleeve 2, a piston 4, a reversing valve 3 and a push valve component are arranged in sequence from front to back. The reversing valve 3 is of a cylindrical structure, and a notch for accommodating the push valve component is formed in the rear end face of the reversing valve 3. The push valve assembly is partly or partly embedded in the groove during the whole movement of the piston 4.

The push valve assembly comprises a primary oil distribution sleeve 41, a secondary oil distribution sleeve 43 and a push valve rod 44. The first-stage oil distribution sleeve 41 is sleeved outside the second-stage oil distribution sleeve 43, and the second-stage oil distribution sleeve 43 is sleeved outside the push valve rod 44.

The cylinder sleeve 2 is internally provided with a limiting groove 45, and the limiting groove 45 and the rear end surface of the inner cavity of the cylinder sleeve 2 form stroke limitation of the primary oil distribution sleeve 41. In the whole movement process of normal work of the piston 4, at least part of the primary oil distribution sleeve 41 moves between the limiting groove 45 and the rear end face of the inner cavity of the cylinder sleeve 2.

The rear end face of the first-stage oil distribution sleeve 41 and the rear end face of the inner cavity of the cylinder sleeve 2 form a stroke limit of the second-stage oil distribution sleeve 43. During the whole movement process of the normal work of the piston 4, at least part of the primary oil distribution sleeve 41 moves between the rear end surface of the primary oil distribution sleeve 41 and the rear end surface of the inner cavity of the cylinder sleeve 2.

Further, an oil distribution ring 42 is installed at the rear end face of the primary oil distribution sleeve 41. The rear end surface of the oil distribution ring 42 and the rear end surface of the inner cavity of the cylinder sleeve 2 form the stroke limit of the secondary oil distribution sleeve 43.

A limiting concave cavity 46 is arranged in the secondary oil distribution sleeve 43, and the limiting concave cavity 46 and the rear end surface of the inner cavity of the cylinder sleeve 2 form stroke limitation of the push valve rod 44. During the whole movement of the piston 4 in normal operation, the thrust valve stem 44 moves at least partially between the limiting cavity 46 and the rear end face of the internal cavity of the cylinder liner 2.

During the whole movement process of the normal work of the piston 4, the moving stroke of the push valve rod 44 is larger than that of the secondary oil distribution sleeve 43, and the moving stroke of the secondary oil distribution sleeve 43 is larger than that of the primary oil distribution sleeve 41.

The second high-pressure oil port 28 is communicated with the rear end faces of the first-stage oil distribution sleeve 41, the second-stage oil distribution sleeve 43 and the push valve rod 44. The second high-pressure oil port 28 communicates with the rear end surface of the oil distribution ring 42.

The first-stage oil distribution sleeve 41 is provided with a first channel 47 for oil to pass through, the first channel 47 communicates the inner wall surface and the outer peripheral surface of the first-stage oil distribution sleeve 41, and a gap exists between the first-stage oil distribution sleeve 41 and the second-stage oil distribution sleeve 43. The second-stage oil distribution sleeve 43 is provided with a second channel 48 for oil to pass through, the second channel 48 communicates the inner wall surface and the outer peripheral surface of the second-stage oil distribution sleeve 43, and a gap is formed between the second-stage oil distribution sleeve 43 and the second-stage oil distribution sleeve 43. The first passage 47 and the second passage 48 are communicated with the second oil return port 27.

A third channel 49 is arranged on the second-stage oil distribution sleeve 43, the third channel 49 is communicated with the front end surface of the second-stage oil distribution sleeve 43 and the peripheral surface of the second-stage oil distribution sleeve 43, and a fourth channel 50 for oil to pass through is arranged on the second-stage oil distribution sleeve 43; the fourth passage 50 is occasionally in communication with the third passage 49 throughout the entire movement of the piston 4 in normal operation.

In this application, 3 hierarchical brakings of switching-over valve, the switching-over braking process is steady more high-efficient.

The push valve component performs stepped braking, the reversing is more stable, different reversing braking efficiencies can be realized through the action areas of all levels of the push valve component, the application range is wide, and the reversing mechanism is particularly suitable for reversing mechanisms of high-power equipment.

The rest of the example four is the same as the example three.

The motion process of the application is as follows:

stroke motion:

the kinematic pair (the piston 4, the reversing valve 3, the push rod, the secondary oil distribution sleeve 43, the primary oil distribution sleeve 41 and the primary oil distribution ring 42) is subjected to a high-pressure acting force at the second high-pressure oil port 28 and a high-pressure acting force at the front cavity 21, resultant force is forward, the kinematic pair performs accelerated motion forward until the primary oil distribution sleeve 41 reaches a left stroke limit, the primary oil distribution sleeve 41 and the primary oil distribution ring 42 stop moving, the acting area of the previous high-pressure oil is reduced, and the kinematic pair (the piston 4, the reversing valve 3, the push rod and the secondary oil distribution sleeve 43) continues accelerated motion forward, but the acceleration is reduced.

The kinematic pair (the piston 4, the reversing valve 3, the push rod and the secondary oil distribution sleeve 43) still receives the high-pressure acting force at the second high-pressure oil port 28 and the high-pressure acting force at the front cavity 21, the resultant force is forward until the secondary oil distribution sleeve 43 reaches the mechanical limit, and at the moment, high-pressure oil at the first high-pressure oil port 24 enters the rear end face of the piston 4 from the front end of the reversing valve 3 through the conduction groove 12, so that the piston 4 is separated from the reversing valve 3. Because the action area of the rear end surface of the piston 4 is far larger than that of the front cavity 21, the piston 4 does accelerated motion forwards; the action area of the front end surface of the reversing valve 3 is larger than that of the rear end of the push valve rod 44 and smaller than that of the combined rear end surface of the primary oil distribution sleeve 41 and the secondary oil distribution sleeve 43, so that the reversing valve 3 is pressed to be stationary at the position.

The piston 4 moves forward in an accelerated manner until the first signal channel 13 is communicated with the oil port of the first signal channel 13, and high-pressure oil enters the rear end of the reversing valve 3 from the first signal channel 13 and the oil path 11; the action area of high-pressure oil at the rear side of the reversing valve 3 (the sum of the action area of the rear end of the reversing valve 3 and the action area of the rear end face of the push valve rod 44) is larger than that of the front end face of the reversing valve 3, the area difference value is the area difference value of the rear end face and the front end face of the push valve rod 44, so that the main action force of the reversing valve 3 is changed into rear side thrust, the resultant force moves forwards, and the reversing valve 3 starts to move forwards in an accelerated manner.

The piston 4 and the reversing valve 3 do forward accelerated motion at different acceleration and speed until the reversing valve 3 closes the first high-pressure oil port 24, the rear end face of the piston 4 and the front cavity 22 and the rear cavity 22 of the reversing valve 3 lose the action of high-pressure oil, and meanwhile, the piston 4 and the drilling tool 9 collide to move, impact energy is transmitted to the drilling tool 9, and the backward return motion of a new period is prepared to start; the main power of the reversing valve 3 is changed into the force applied to the valve pushing rod 44, and the resultant force moves forwards continuously until the resultant force contacts with the rear end face of the piston 4 to wait for the next return stroke stage.

And (3) return movement:

the push valve rod 44 is acted by constant high-pressure oil, the resultant force is forward, and the reversing valve 3 is pressed at the foremost end of the stroke; the rear end face of the piston 4 is communicated with the first oil return port 25, and the first high-pressure oil port 24 is closed; the front cavity 21 of the piston 4 is fed with oil at high pressure, the back cavity 22 is fed with oil at low pressure, and the back end surface of the piston is connected with oil return by virtue of an oil return port on the back end surface of the reversing valve 3; because the action area of the rear end of the push valve rod 44 is smaller than the action area of high-pressure oil in the front cavity 21 of the piston 4, the main action force is the action force of the front cavity 21, the resultant force is backward, and the piston 4 drives the main oil distribution valve and the push valve rod 44 to do accelerated motion backward.

The piston 4 moves backwards to do accelerated motion until the first signal oil port 23 is communicated with the first oil return port 25 at the rear end of the piston 4, and then oil return depends on the first oil return port 25 at the rear end of the reversing valve 3 and the first signal oil port 23 to return oil together; the main acting force is still the acting force of the piston 4 at the front cavity 21, the resultant force is backward, and the piston 4 continues to drive the reversing valve 3 and the push valve rod 44 to do accelerated motion backward.

The piston 4 moves backwards to do accelerated motion until the first oil return port 25 of the rear cavity 22 of the reversing valve 3 is closed, and the oil return of the piston 4 only depends on the second signal oil port 26 to return oil in a single channel; the main acting force is still the acting force of the front cavity 21, the resultant force is backward, and the piston 4 keeps driving the reversing valve 3 and the push valve rod 44 to do backward accelerated motion.

The piston 4 moves backwards to do accelerated motion until the reversing valve 3 is in contact with the secondary oil distribution sleeve 43 and pushes the secondary oil distribution sleeve 43 to move backwards, at the moment, because the rear end of the secondary oil distribution sleeve 43 is acted by high-pressure oil at a second high-pressure groove, the forward resultant force borne by the reversing valve 3 is further increased, and the acting area of the forward resultant force is larger than that of the high-pressure oil of the piston 4 at the front cavity 21, so that the kinematic pair (the piston 4, the reversing valve 3, the push rod and the secondary oil distribution sleeve 43) moves backwards in a decelerating motion together.

The piston 4 moves backwards to perform deceleration movement until the reversing valve 3 contacts with the primary oil distribution sleeve 41 and pushes the secondary oil distribution sleeve 43 to move backwards, at the moment, because the rear end of the secondary oil distribution sleeve 43 and the rear end of the primary oil distribution sleeve 41 are both acted by high-pressure oil, the forward resultant force borne by the reversing valve 3 is further increased, and the action area of the forward resultant force is larger than that of the high-pressure oil in the front cavity 21 of the piston 4, the kinematic pair (the piston 4, the reversing valve 3, the push rod, the secondary oil distribution sleeve 43, the primary oil distribution sleeve 41 and the primary oil distribution ring 42) moves backwards together to perform deceleration movement, and the deceleration effect is stronger.

The piston 4 moves backwards to perform deceleration movement until the push valve rod 44 reaches the stroke limit of the rear side, and at this time, the speed of the kinematic pair (the piston 4, the reversing valve 3, the push rod, the secondary oil distribution sleeve 43, the primary oil distribution sleeve 41 and the primary oil distribution ring 42) approaches to 0, so that the return stroke process is completed, one period of movement is completed, and then the next period is continued.

A rock drill comprising an adjustable percussion device according to any one of the embodiments described above.

The present application has been described in detail above, and specific examples thereof are used herein to explain the principles and implementations of the present application, which are presented solely to aid in understanding the present application and its core concepts. It should be noted that, for those skilled in the art, it is possible to make several improvements and modifications to the present application without departing from the principle of the present application, and such improvements and modifications also fall within the scope of the claims of the present application.

Claims (11)

1. The impact device of the rock drill is characterized by comprising a front stop sleeve (31), a cylinder sleeve (2) and at least two rear stop sleeves (32), wherein the front stop sleeve (31) and any one of the rear stop sleeves (32) are coaxially and sequentially connected with the cylinder sleeve (2), a stop groove (33) matched with a drilling tool (9) is formed in the rear stop sleeve (32), the rear end of the drilling tool (9) is positioned in a cavity formed by the front stop sleeve (31) and the rear stop sleeve (32), the bottom surface of the stop groove (33) limits the limit position of the drilling tool (9) moving backwards, and the stop groove (33) formed in each rear stop sleeve (32) is different in axial depth from the rear stop sleeve (32).

2. The percussion device of a rock drill according to claim 1, characterized by comprising a head section (401) and at least two tail sections (402), the head section (401) being connected to any one of the tail sections (402) to form a piston (4) mounted in a cylinder liner (2), the tail section (402) being provided with a first signal channel (13), the first signal channel (13) communicating the outer peripheral surface of the piston (4) with the rear end surface of the piston (4); the lengths of the first signal channels (13) on different tail sections (402) are different, and the tail sections (402) correspond to the rear stop sleeves (32) one by one.

3. A percussion device for a rock drill according to claim 1, characterized in that the drill tool (9) includes a mounting portion (9 a), said mounting portion (9 a) being located at the rear end of the entire drill tool (9), the diameter of the mounting portion (9 a) being greater than the diameter of the rest of the drill tool (9).

4. A percussion device for a rock drill according to claim 3, characterized in that the front stop sleeve (31) and the rear stop sleeve (32) are connected to form a limiting chamber (34) for receiving the mounting portion (9 a), said limiting chamber (34) limiting the stroke of the movement of the drill tool (9); the stop groove (33) forms the limit cavity (34), and the limit cavities (34) on different rear stop sleeves (32) have different depths in the axial direction.

5. A percussion device for a rock drill according to claim 4, characterized in that the rear end of the mounting portion (9 a) is of a circular truncated cone configuration, the rear end of the mounting portion (9 a) including a flat surface and an inclined surface surrounding an outer ring of the flat surface; the plane of the rear end face of the mounting part (9 a) is an impact surface contacted with the piston (4), and the bottom surface of the stop groove (33) is adapted to the inclined surface of the rear end face of the mounting part (9 a).

6. A percussion device for rock drills according to claim 2 in which the piston (4) is arranged coaxially with the drill tool (9), the piston (4) moving in a reciprocating manner in the cylinder (2) to drive the drill tool (9) to impact the rock wall.

7. A percussion device for a rock drill according to claim 2 or 6, characterized in that the tail section (402) is provided with a second signal channel (14), the second signal channel (14) communicating the outer periphery of the piston (4) with the rear end face of the piston (4).

8. A percussion device for a rock drilling machine according to claim 7, characterized in that during normal working movement of the piston (4), the first signal port (23) is in communication with the first signal channel (13) or vice versa; the first signal channel (13) is a signal for normal work of the piston (4); and under the idle driving state of the piston (4), the second signal oil port (26) is communicated with the first signal channel (13) at intervals.

9. The percussion device of a rock drill according to claim 2, characterized in that the surface of the head section (401) is provided with an idle driving prevention shaft compartment (4 a), the idle driving prevention shaft compartment (4 a) comprises a plurality of coaxially arranged ring members (35), and a space is reserved between two adjacent ring members (35); the nominal value of the diameter of the ring piece (35) is equal to the diameter of a dead chamber (36) of the cylinder sleeve (2).

10. A percussion device for a rock drilling machine according to claim 9, characterized in that said lost motion prevention inter-shaft space (4 a) comprises at least three coaxially arranged ring members (35); from the near drilling tool (9) to the far drilling tool (9), the outer diameters of the ring pieces (35) are sequentially increased; the diameter of the ring (35) furthest from the drill tool (9) has a value equal to the diameter of the dead space (36) of the cylinder.

11. A rock drill characterized by comprising a percussion device of a rock drill according to any one of claims 1-10.

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