CN213683926U

CN213683926U - Hydraulic rock drill with rotary sleeve

Info

Publication number: CN213683926U
Application number: CN202021763324.8U
Authority: CN
Inventors: 李永胜; 张辉; 韩龙; 李水涛; 张婕妤; 陈茹; 刘世伟; 刘璐
Original assignee: Shandong Tianrui Heavy Industry Co Ltd
Current assignee: Shandong Tianrui Heavy Industry Co Ltd
Priority date: 2020-08-21
Filing date: 2020-08-21
Publication date: 2021-07-13
Anticipated expiration: 2030-08-21

Abstract

The utility model discloses a hydraulic rock drill with a rotary sleeve, which comprises a shell, wherein a front end cover and a rear end cover are respectively arranged at two ends of the shell, a drill bit tail and a piston for impacting the drill bit tail are movably arranged in the shell, a rotary sleeve is movably sleeved outside the piston in the shell, a piston front cavity and a piston rear cavity are respectively arranged at two sides of the piston in the rotary sleeve, the rotary sleeve is positioned in the shell and rotates for sequentially and alternately introducing hydraulic oil into the piston front cavity and the piston rear cavity to force the piston to be positioned in the rotary sleeve to perform stroke and backward movement, one end of the drill bit tail close to the rotary sleeve is in transmission and sliding connection with the rotary sleeve, the rotary sleeve of the utility model can play the role of a steering valve for controlling the piston to perform stroke and backward movement to impact the drill bit tail, and the rotary sleeve can transmit torque to the drill bit tail to drive the drill bit tail to, the whole structure is simple, the volume is small, the weight is light, and the failure rate is low.

Description

Hydraulic rock drill with rotary sleeve

Technical Field

The utility model relates to a rock drill, specific theory relates to a hydraulic rock drill of rotatory sleeve in area belongs to engineering machine tool technical field.

Background

At present, in the mining, high-speed rail, subway tunnel and water conservancy construction of China, a large number of hydraulic rock drills are used, the hydraulic rock drills are rock drilling equipment using high-pressure liquid as power, and the hydraulic rock drills have the advantages of high output power, high rock breaking efficiency, low energy consumption, long service life, good working environment and easiness in automatic control, are rapidly popularized and popularized in the world and are indispensable construction equipment in rock drilling engineering operation.

Traditional hydraulic rock drill, as patent number is: 201510847547.X, there is provided a hydraulic rock drill comprising a shank; the hydraulic rotary speed changing module is provided with an output shaft and is configured to receive hydraulic fluid and convert the hydraulic pressure energy of the hydraulic fluid into the mechanical energy of the output shaft so as to drive the drill bit shank to rotate; a hydraulic impact module having an impact rod, mounted to the hydraulic rotary speed change module, configured to receive hydraulic fluid and control a flow direction of the hydraulic fluid to reciprocate the impact rod along a length direction of the shank adapter to impact the shank adapter; and the drill bit shank connecting module is arranged on the hydraulic rotating speed changing module, and the drill bit shank penetrates through the drill bit shank connecting module and is arranged on the output shaft.

The traditional hydraulic rock drill adopts an independent swing mechanism to provide torque for the rotation of the drill rod tail, and further needs to arrange an independent torque transmission device beside the main body of the rock drill, and then utilizes a transmission rod to transmit the torque generated by a hydraulic motor to the machine head and then utilizes the meshing of gears to transmit the torque to the drill rod tail, so that the hydraulic rock drill has the advantages of large weight and volume, complex mechanism, difficult disassembly, high failure rate and high use cost.

For solving the bulky problem of above-mentioned hydraulic rock drill weight, a hydraulic rock drill has appeared among the prior art, be as patent number: 201610344684.6 discloses a hydraulic rock drill, which comprises a machine body, an impact drill shank and an impact piston are arranged on the machine body along the axis, the impact piston is arranged on the right side of the impact drill shank, the machine body comprises a left machine body and a right machine body, the left machine body is fixedly connected with the right machine body, the left end of the left machine body is fixedly connected with a left end cover of the machine body, the right end of the right machine body is fixedly connected with a right end cover of the machine body, the right end cover of the right machine body is provided with an air-water external port, a torsion connecting sleeve and a cam rotor hydraulic motor are arranged in the left machine body, the cam rotor hydraulic motor is arranged on the right side of the torsion connecting sleeve, the impact piston passes through the cam rotor hydraulic motor, the impact drill shank is in sliding fit with the torsion connecting sleeve, a left piston cylinder and a right piston cylinder are arranged in the right machine body, a reversing valve is also arranged in the right.

Above-mentioned this type of hydraulic rock drill, it sets up inside hydraulic rock drill's organism to fix cam rotor hydraulic motor, then can drive cam rotor hydraulic motor through hydraulic pressure force and rotate, and transmit cam rotor hydraulic motor's torsion to the bore bit tail through the torsion adapter sleeve, realize driving bore bit tail pivoted, can make hydraulic rock drill's whole small, but above-mentioned this type of hydraulic rock drill's overall structure is complicated, manufacturing cost and use cost are high, and the equipment installation is loaded down with trivial details, again because of overall structure is complicated, it is when using, job stabilization, break down easily, when the maintenance is loaded down with trivial details after breaking down, greatly reduced result of use.

SUMMERY OF THE UTILITY MODEL

The to-be-solved main technical problem of the utility model is to provide a through rotatory sleeve transmission moment of torsion to advance the oil return in turn around controlling the piston as the diverter valve with rotatory sleeve, make the piston back and forth movement carry out the rock drilling, and whole small, light in weight, overall structure is simple, and the fault rate is low, the hydraulic rock drill of taking rotatory sleeve of convenient maintenance and maintenance.

In order to solve the technical problem, the utility model provides a following technical scheme:

the utility model provides a take rotary sleeve's hydraulic rock drill, which comprises an outer shell, the both ends of shell are provided with front end housing and rear end housing respectively, shell internalization is provided with the bore bit tail and is used for striking the piston of bore bit tail, the outside activity cover that lies in the piston in the shell is equipped with rotary sleeve, the both sides that lie in the piston in the rotary sleeve are provided with cavity and piston back cavity before the piston respectively, rotary sleeve is located the shell internal rotation and forces the piston to be located rotary sleeve and carry out stroke and back stroke motion through letting in hydraulic oil in turn in to cavity and piston back cavity before the piston, the bore bit tail is close to rotary sleeve's one end and links to each other and rotates synchronous with rotary

The following is the utility model discloses to above-mentioned technical scheme's further optimization:

the rear end cover is fixedly provided with a hydraulic motor, the power output end of the hydraulic motor is in transmission connection with the rotating sleeve, the hydraulic motor outputs power to drive the rotating sleeve to rotate, and the rotating sleeve transmits torque to drive the drill bit shank to rotate.

Further optimization: the drill bit tail is in transmission connection with the rotary sleeve through the connecting sealing sleeve, and the drill bit tail is connected with the connecting sealing sleeve through meshing teeth or splines.

Further optimization: and a limiting support assembly for supporting the rotating sleeve to rotate and limiting the position of the rotating sleeve in the shell is arranged on the outer surface of the rotating sleeve.

Further optimization: the rotary sleeve comprises a main body part and a packaging plate, the packaging plate and a connecting sealing sleeve are respectively located at two axial ends of a piston, two axial ends of the packaging plate are respectively connected with the main body part to limit a moving space of the piston, the packaging plate is provided with a connecting shaft extending towards the direction far away from the piston, the main body part is provided with a middle partition plate extending towards the piston, a buffer chamber is arranged between the middle partition plate and the packaging plate and located in the rotary sleeve, and a buffer device used for buffering the stroke impact force of the piston is arranged on the packaging plate of the buffer chamber.

Further optimization: the coaxial setting of piston is in rotatory sleeve, and the piston includes the piston main part, and the sealed sliding connection of internal surface of piston main part and rotatory sleeve, both sides are integrative piston rod and back piston rod before the front and back of piston main part respectively, and in the one end through connection seal cover of preceding piston rod extended to the installation cavity, the one end of back piston rod run through intermediate bottom and extended to the cushion chamber indoor.

Further optimization: the buffering device comprises a buffering column which is integrally arranged on the packaging plate and located at the center, the buffering column and the piston are coaxially arranged, a piston rear cavity is formed in one end, far away from the piston main body, of the rear piston rod, and the cross section shape of the piston rear cavity is matched with that of the buffering column.

Further optimization: the shell is provided with a front cavity oil inlet and a front cavity oil outlet at positions corresponding to the front cavity of the piston, a rear cavity oil inlet and a rear cavity oil outlet at positions corresponding to the rear cavity of the piston, and the shell is provided with a buffer cavity oil return opening at a position corresponding to the buffer cavity.

Further optimization: the rotary sleeve is provided with a plurality of front cavity oil conveying channels communicated with the front cavities of the pistons, a first sealing section is arranged between two adjacent front cavity oil conveying channels, and the rotary sleeve is positioned in the shell to rotate so that the front cavity oil conveying channels are respectively communicated with the front cavity oil inlets and the front cavity oil outlets in turn.

Further optimization: a plurality of rear cavity oil conveying channels communicated with the piston rear cavity are formed in the rotary sleeve, the rear cavity oil conveying channels and the front cavity oil conveying channels are arranged in a staggered mode, a second sealing section is arranged between every two adjacent rear cavity oil conveying channels, and the rotary sleeve is located in the shell and rotates to enable the rear cavity oil conveying channels to be communicated with a rear cavity oil inlet and a rear cavity oil outlet in sequence.

The above technical scheme is adopted in the utility model, think about ingeniously, rational in infrastructure, the effect that the rotary sleeve cover established and can play the diverter valve outside the piston, be used for letting in hydraulic oil in turn behind cavity and the piston cavity before the piston in proper order, and force the piston to carry out the stroke and move backward and strike the bore bit tail, and be connected for the transmission between bore bit tail and the rotary sleeve, and then the rotary sleeve can drive the bore bit tail to bore bit tail transmission moment of torsion and rotate, it needs the independent moment of torsion transmission device of peripheral hardware to drive bore bit tail pivoted drawback to have got rid of current hydraulic rock drill completely, and then can effectually reduce hydraulic rock drill's volume, make this hydraulic rock drill compare traditional rock drill's overall structure simple, the fault rate is low, and convenient maintenance and maintenance.

The present invention will be further explained with reference to the drawings and examples.

Drawings

Fig. 1 is a schematic diagram of the overall structure of an embodiment of the present invention;

FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1;

FIG. 3 is a cross-sectional view taken along line B-B of FIG. 1;

fig. 4 is a schematic structural view of a rotary sleeve and a piston according to an embodiment of the present invention;

FIG. 5 is a schematic structural view of the embodiment of the present invention during the stroke;

FIG. 6 is a schematic structural view of the embodiment of the present invention during the backward movement;

FIG. 7 is a position diagram of the rotating sleeve and the housing during the backward stroke of the embodiment of the present invention;

FIG. 8 is a position diagram of the rotating sleeve and the housing during the backward stroke of the embodiment of the present invention;

fig. 9 is a schematic structural view of a buffering device according to an embodiment of the present invention;

FIG. 10 is a schematic view of an embodiment of the present invention illustrating a buffer device during operation;

fig. 11 is a schematic view of the buffering device in the embodiment of the present invention during operation.

In the figure: 1-drill rod shank; 101-external teeth; 2-front end cover; 3-a front axial bearing; 4-connecting a sealing sleeve; 41-installation cavity, 42-inner gear engagement; 5-a front radial bearing; 6-a housing; 61-front chamber oil inlet; 62-front chamber oil outlet; 63-a rear cavity oil inlet; 64-a rear chamber oil outlet, 65-a buffer chamber oil return port; 7-sealing ring; 8-rotating the sleeve; 81-intermediate partition board; 82-a package board; 83-a connecting shaft; 84-a buffer chamber; 85-buffer column; 86-front chamber oil transfer channel; 87-a first seal section; 88-rear chamber oil transfer channel; 89-a second seal segment; 80-an oil return passage; 9-a piston; 91-a piston body; 92-a front piston rod; 93-a rear piston rod; 94-piston rear cavity; 10-rear radial bearing; 11-rear axial bearing; 12-rear end cap; 13-connecting sleeve; 14-a hydraulic motor; 15-piston front chamber; 16-piston rear chamber; 17-oil inlet pipeline; and 18-an oil outlet pipeline.

Detailed Description

Example (b): as shown in fig. 1-3, a hydraulic rock drill with a rotary sleeve includes a housing 6, a front end cover 2 and a rear end cover 12 are respectively fixedly arranged at two ends of the housing 6, a drill shank 1 and a piston 9 for impacting the drill shank 1 are movably arranged in the housing 6, the rotary sleeve 8 is movably sleeved outside the piston 9 in the housing 6, a piston front chamber 15 and a piston rear chamber 16 are respectively arranged at two sides of the piston 9 in the rotary sleeve 8, the rotary sleeve 8 is rotatably arranged in the housing 6 and forces the piston 9 to perform stroke and retreat movement in the rotary sleeve 8 by sequentially and alternately introducing hydraulic oil into the piston front chamber 15 and the piston rear chamber 16, and one end of the drill shank 1 close to the rotary sleeve 8 is connected with the rotary sleeve 8 and rotates synchronously with the rotary sleeve 8.

As shown in fig. 1, a hydraulic motor 14 is fixedly arranged on the rear end cover 12, a power output end of the hydraulic motor 14 is in transmission connection with the rotary sleeve 8, the hydraulic motor 14 outputs power to drive the rotary sleeve 8 to rotate, and the rotary sleeve 8 transmits torque to drive the drill bit shank 1 to rotate.

As shown in fig. 1, the front cover 2 and the rear cover 12 are fixedly connected to the housing 6 by a bolt fastening assembly, and the front cover 2 and the rear cover 12 are used for enclosing both ends of the housing 6.

The drill bit shank 1 is arranged in the shell 6 and close to the front end cover 2, the drill bit shank 1 and the shell 6 are coaxially arranged, and one end, close to the front end cover 2, of the drill bit shank 1 penetrates through the front end cover 2 and extends outwards.

As shown in fig. 1 and 5, the torque can be transmitted to the rotary sleeve 8 by the output power of the hydraulic motor 14, the rotation of the rotary sleeve 8 can be used for reversing the external hydraulic oil, so that the hydraulic oil is respectively and sequentially introduced into the piston front chamber 15 and the piston rear chamber 16, the hydraulic oil forces the piston 9 to be positioned in the rotary sleeve 8 to perform stroke and retreat movement, and the piston 9 can impact the root of the drill shank 1 during stroke movement.

And the rotation of the rotating sleeve 8 can transmit the torque to the drill bit shank 1, so that the drill bit shank 1 is driven to rotate.

As shown in fig. 1, a connecting sealing sleeve 4 is fixedly arranged on the rotating sleeve 8 at a position close to the drill bit shank 1, and the drill bit shank 1 is in transmission connection with the rotating sleeve 8 through the connecting sealing sleeve 4.

The connecting sealing sleeve 4 is fixedly connected with the rotating sleeve 8 through a bolt fastening assembly.

An installation cavity 41 is formed in the connecting sealing sleeve 4, and one end of the drill shank 1 close to the connecting sealing sleeve 4 is installed in the installation cavity 41.

The inner wall of the installation cavity 41 is integrally connected with an inner meshing tooth 42 at a position close to the drill rod shank 1, one end of the drill rod shank 1 close to the connecting sealing sleeve 4 is integrally connected with an outer meshing tooth 101, and the outer meshing tooth 101 of the drill rod shank 1 is in meshing transmission connection with the inner meshing tooth 42 in the connecting sealing sleeve 4.

By the design, the drill rod shank 1 is meshed with the inner meshing teeth 42 in the connecting sealing sleeve 4 through the outer meshing teeth 101, the drill rod shank 1 can move along the axial direction of the connecting sealing sleeve 4, and then when the piston 9 impacts the root of the drill rod shank 1, the drill rod shank 1 can move, and the rotary sleeve 8 rotates to drive the drill rod shank 1 to integrally rotate through the connecting sealing sleeve 4, so that the drill rod shank is convenient to use.

In addition to this embodiment, the connection between the drill shank 1 and the connecting sealing sleeve 4 may also be connected by a spline, and the drill shank 1 and the connecting sealing sleeve 4 may be connected by a spline to realize the transmission connection between the drill shank 1 and the connecting sealing sleeve 4.

As shown in fig. 1, a limiting support assembly for supporting the rotation of the rotating sleeve 8 and limiting the position of the rotating sleeve 8 in the housing 6 is provided on the outer surface of the rotating sleeve 8.

The limiting support assembly comprises a front radial bearing 5 and a rear radial bearing 10 which are sleeved on the outer surface of the rotating sleeve 8 and are close to the front end and the rear end of the rotating sleeve, and the outer surfaces of the front radial bearing 5 and the rear radial bearing 10 are connected with the shell 6.

The front end surface and the rear end surface of the rotating sleeve 8 are respectively and fixedly provided with a front axial bearing 3 and a rear axial bearing 11, and the front axial bearing 3 and the rear axial bearing 11 are fixedly arranged on the corresponding front end cover 2 and the corresponding rear end cover 12.

By means of such a design, the front radial bearing 5 and the rear radial bearing 10 and the front axial bearing 3 and the rear axial bearing 11 can be used for supporting the rotating sleeve 8 in the housing 6 for rotation, and the front radial bearing 5 and the rear radial bearing 10 and the front axial bearing 3 and the rear axial bearing 11 can also be used for limiting the position of the rotating sleeve 8 in the housing 6, so that the rotating sleeve 8 can be installed in a fixed position.

As shown in fig. 1 and 4, the rotating sleeve 8 includes a main body portion and a packaging plate 82, the packaging plate 82 and the connecting sealing sleeve 4 are respectively located at two axial ends of the piston 9, two axial ends of the packaging plate 82 are respectively connected with the main body portion to define a moving space of the piston 9, the packaging plate 82 is used for packaging a rear end of the rotating sleeve 8, and the packaging plate 82 is provided with a connecting shaft 83 extending in a direction away from the piston 9.

The hydraulic motor 14 is fixedly arranged on the rear end cover 12, and the power output end of the hydraulic motor 14 is in transmission connection with the connecting shaft 83 through the connecting sleeve 13.

By means of the design, the rotating sleeve 8 can be in transmission connection with the power output end of the hydraulic motor 14 through the connecting shaft 83 and the connecting sleeve 13 conveniently.

The rear end cover 12 is provided with a through hole for the connecting shaft 83 and the power output end of the hydraulic motor 14 to pass through.

The piston 9 is coaxially arranged in the rotary sleeve 8, the piston 9 comprises a piston main body 91, a front piston rod 92 and a rear piston rod 93, the front piston rod 92 and the rear piston rod 93 are respectively and correspondingly arranged on the front side and the rear side of the piston main body 91, and one ends of the front piston rod 92 and the rear piston rod 93 close to the piston main body 91 are integrally connected with the piston main body 91.

The diameter of the outer surface of the piston main body 91 is equal to the diameter of the inner surface of the rotating sleeve 8, the outer surface of the piston main body 91 is in sealing sliding connection with the inner surface of the rotating sleeve 8, and the diameters of the outer surfaces of the front piston rod 92 and the rear piston rod 93 are smaller than the diameter of the outer surface of the piston main body 91.

A piston front chamber 15 is provided in the rotary sleeve 8, said piston front chamber 15 being jointly formed between the front end face of the piston body 91 and the inner surface of the rotary sleeve 8 and the cross-section of the connecting gland 4.

A piston rear chamber 16 is provided in the rotary sleeve 8, and the piston rear chamber 16 is formed between the rear end surface of the piston main body 91 and the inner surface of the rotary sleeve 8.

The end of the front piston rod 92 of the piston 9 remote from the piston body 91 extends through the connecting gland 4 and into the mounting cavity 41.

As shown in fig. 1 and fig. 4-6, the design is such that when the pressure of the hydraulic oil in the piston rear chamber 16 is greater than the pressure of the hydraulic oil in the piston front chamber 15, the pressure of the hydraulic oil in the piston rear chamber 16 acts on the piston main body 91 of the piston 9 to push the piston main body 91 to move toward the side close to the connecting gland 4, and at this time, the piston main body 91 drives the front piston rod 92 to move close to and strike the drill shank 1, so that the stroke of the piston 9 strikes the drill shank 1.

When the pressure of the hydraulic oil in the front piston chamber 15 is greater than the pressure of the hydraulic oil in the rear piston chamber 16, the pressure of the hydraulic oil in the front piston chamber 15 acts on the piston main body 91 of the piston 9 to push the piston main body 91 to move towards the side far away from the connecting seal sleeve 4, and at the moment, the piston main body 91 drives the front piston rod 92 to move away from the drill shank 1, so that the piston 9 retreats.

The joint of the front piston rod 92 and the connecting sealing sleeve 4 is provided with a sealing ring 7, and the sealing ring 7 is fixedly arranged on the connecting sealing sleeve 4.

The sealing ring 7 is used for improving the sealing performance of the joint of the front piston rod 92 and the connecting sealing sleeve 4, and the hydraulic oil in the front piston chamber 15 is prevented from leaking at the joint.

As shown in fig. 1 and 4, the main body of the rotating sleeve 8 is provided with an intermediate partition 81 extending toward the piston 9, the intermediate partition 81 is spaced apart from the packing plate 82, and a buffer chamber 84 is provided between the intermediate partition 81 and the packing plate 82 in the rotating sleeve 8.

The end of the rear piston rod 93 remote from the piston body 91 extends through the intermediate partition 81 and into the cushion chamber 84.

A buffer device for buffering the retreating impact force of the piston 9 is provided in the buffer chamber 84 on the packing plate 82.

The damping means comprises a damping post 85 integrally provided on the package plate 82 at a central position, the damping post 85 being coaxially provided with the piston 9.

A piston rear cavity 94 is formed in one end, far away from the piston main body 91, of the rear piston rod 93, and the cross section of the piston rear cavity 94 is matched with that of the buffer column 85.

As shown in fig. 1, 4 and 9-10, the damping chamber 84 is filled with hydraulic oil, when the piston 9 moves backward, the rear piston rod 93 of the piston 9 moves to a side close to the damping post 85, at this time, the rear cavity 94 of the piston comes into contact with the damping post 85, and further, the hydraulic oil in the rear cavity 94 of the piston starts to be discharged outward under the action of pressure, as the piston 9 continuously moves backward, the discharge speed of the hydraulic oil in the rear cavity 94 of the piston becomes slower and slower until the piston stops, and at this time, the movement speed of the piston 9 is also decelerated from the original high speed until the piston stops under the reaction force of the hydraulic oil.

And then adopt this buffer can cushion the back stroke impact force of piston 9, avoid piston 9 direct impact rotatory sleeve 8's packaging plate 82, prevent that rotatory sleeve 8 from damaging, increase of service life greatly.

As shown in fig. 1 and 4, a sealing ring 7 is disposed at the joint of the rear piston rod 93 and the packaging plate 82, and the sealing ring 7 is fixedly mounted on the packaging plate 82.

The sealing ring 7 is used for improving the sealing performance of the joint of the rear piston rod 93 and the packaging plate 82, and hydraulic oil in the piston rear chamber 16 is prevented from leaking at the joint.

As shown in fig. 1 to 3, a front chamber oil inlet 61 and a front chamber oil outlet 62 are respectively formed in positions of the housing 6 corresponding to the piston front chamber 15, and the front chamber oil inlet 61 and the front chamber oil outlet 62 are coaxially arranged.

A rear cavity oil inlet 63 and a rear cavity oil outlet 64 are respectively formed in the position, corresponding to the piston rear cavity 16, of the shell 6, and the rear cavity oil inlet 63 and the rear cavity oil outlet 64 are coaxially arranged.

A buffer chamber oil return port 65 is formed in the housing 6 at a position corresponding to the buffer chamber 84.

A plurality of front cavity oil conveying channels 86 are formed in the positions, corresponding to the front cavity oil inlet 61 and the front cavity oil outlet 62, of the rotary sleeve 8, the front cavity oil conveying channels 86 are communicated with the piston front cavity 15 in the rotary sleeve 8, the front cavity oil conveying channels 86 are arranged at intervals in an annular mode along the outer surface of the rotary sleeve 8, and a first sealing section 87 is arranged between every two adjacent front cavity oil conveying channels 86.

As shown in fig. 5, when the rotary sleeve 8 is located in the housing 6 for rotation, the front chamber oil feed passage 86 is alternately communicated with the front chamber oil inlet 61 and the front chamber oil outlet 62, respectively, so that the front chamber oil inlet 61 and the front chamber oil outlet 62 are alternately communicated with the front piston chamber 15 through the front chamber oil feed passage 86.

As shown in fig. 6-7, and when the rotary sleeve 8 rotates to communicate the front chamber oil delivery passage 86 with the front chamber oil inlet 61, the first sealing section 87 thereof corresponding to the front chamber oil delivery passage 86 rotates to the position of the front chamber oil outlet 62, and can be used for sealing the front chamber oil outlet 62 by the first sealing section 87.

As shown in fig. 1 and 2, when the rotary sleeve 8 rotates to communicate the front chamber oil delivery passage 86 with the front chamber oil outlet 62, the first sealing section 87 thereof corresponding to the front chamber oil delivery passage 86 rotates to the position of the front chamber oil inlet 61, and can be used for sealing the front chamber oil inlet 61 by the first sealing section 87.

As shown in fig. 1 and 3, a plurality of rear chamber oil delivery passages 88 are formed in positions on the rotary sleeve 8 corresponding to the rear chamber oil inlet 63 and the rear chamber oil outlet 64, the rear chamber oil delivery passages 88 are communicated with the piston rear chamber 16 in the rotary sleeve 8, the rear chamber oil delivery passages 88 are respectively annularly and sequentially arranged at intervals along the outer surface of the rotary sleeve 8, the rear chamber oil delivery passages 88 and the front chamber oil delivery passages 86 are arranged in a staggered manner, and a second sealing section 89 is arranged between two adjacent rear chamber oil delivery passages 88.

As shown in fig. 1 and 2, the design is such that when the rotary sleeve 8 is positioned in the housing 6 for rotation, the rear chamber oil delivery passage 88 can be sequentially and alternately communicated with the rear chamber oil inlet 63 and the rear chamber oil outlet 64 respectively, and further, the sequential and alternate communication between the rear chamber oil inlet 63 and the rear chamber oil outlet 64 and the piston rear chamber 16 through the rear chamber oil delivery passage 88 can be realized.

As shown in fig. 1, 2 and 5, when the rotary sleeve 8 rotates to communicate the rear chamber oil delivery passage 88 with the rear chamber oil inlet 63, the second seal section 89 thereof corresponding to the rear chamber oil delivery passage 88 rotates to the position of the rear chamber oil outlet 64, and can be used to seal the rear chamber oil outlet 64 by the second seal section 89.

As shown in fig. 6 and 8, when the rotary sleeve 8 rotates to communicate the rear chamber oil delivery passage 88 with the rear chamber oil outlet 64, the second seal section 89 thereof corresponding to the rear chamber oil delivery passage 88 rotates to the position of the rear chamber oil inlet 63, and can be used to seal the rear chamber oil inlet 63 by the second seal section 89.

As shown in fig. 1-3 and 5-8, the rear chamber oil delivery passages 88 and the front chamber oil delivery passages 86 are arranged alternately, and when the rotary sleeve 8 rotates to communicate the front chamber oil delivery passages 86 with the front chamber oil outlet 62, the first sealing section 87 corresponding to the front chamber oil delivery passages 86 rotates to the position of the front chamber oil inlet 61 for sealing the front chamber oil inlet 61, and at the same time, the rear chamber oil delivery passages 88 communicate with the rear chamber oil inlet 63, the second sealing section 89 corresponding to the rear chamber oil delivery passages 88 rotates to the position of the rear chamber oil outlet 64 for sealing the rear chamber oil outlet 64, at the same time, output of the hydraulic oil in the front piston chamber 15 is realized, and high-pressure hydraulic oil is introduced into the rear piston chamber 16, at the same time, the pressure of the hydraulic oil in the rear piston chamber 16 is greater than the pressure of the hydraulic oil in the front piston chamber 15, and the piston 9 moves forward under the pressure of the hydraulic oil in the rear piston chamber 16, the impact on the root of the drill bit shank 1 is realized, and the stroke is finished.

When the rotary sleeve 8 rotates to enable the front chamber oil delivery channel 86 to be communicated with the front chamber oil inlet 61, the first sealing section 87 corresponding to the front chamber oil delivery channel 86 rotates to the position of the front chamber oil outlet 62 to seal the front chamber oil outlet 62, and at the moment, the rear chamber oil delivery channel 88 is communicated with the rear chamber oil outlet 64, and the second sealing section 89 corresponding to the rear chamber oil delivery channel 88 rotates to the position of the rear chamber oil inlet 63 to seal the rear chamber oil inlet 63; at the moment, high-pressure hydraulic oil is introduced into the piston front chamber 15, hydraulic oil is output into the piston rear chamber 16, the pressure of the hydraulic oil in the piston front chamber 15 is larger than that of the hydraulic oil in the piston rear chamber 16, and then the piston 9 moves backwards under the action of the pressure of the hydraulic oil in the piston front chamber 15, so that the piston 9 is far away from the drill shank 1, and the retreating is completed.

As shown in fig. 1, a plurality of oil return passages 80 are formed in the rotary sleeve 8 at positions corresponding to the buffer chamber oil return openings 65, the oil return passages 80 are communicated with the buffer chamber 84 in the rotary sleeve 8, and the plurality of oil return passages 80 are respectively arranged at intervals in an annular shape along the outer surface of the rotary sleeve 8.

By the design, when the rotary sleeve 8 is positioned in the shell 6 to rotate, the oil return channels 80 can be respectively and alternately communicated with the buffer chamber oil return openings 65, and further the buffer chamber oil return openings 65 can be communicated with the buffer chamber 84 through the oil return channels 80.

As shown in fig. 5 to 6, hydraulic lines for introducing high-pressure hydraulic oil into the piston front chamber 15 and the piston rear chamber 16 are provided outside the housing 6, and the hydraulic lines include an oil inlet line 17 and an oil outlet line 18.

The liquid outlet end of the oil inlet pipeline 17 is communicated with a front cavity oil inlet 61 and a rear cavity oil inlet 63, and the oil outlet pipeline 18 is communicated with a front cavity oil outlet 62, a rear cavity oil outlet 64 and a buffer cavity oil return port 65.

A rubber membrane in the energy accumulator divides the inner cavity of the energy accumulator into 2 independent chambers, one is connected with a hydraulic oil circuit, and the other is filled with high-pressure nitrogen. Because the nitrogen can be compressed, the hydraulic oil chamber can be used as a buffer oil chamber under the action of the pressure of the nitrogen in the nitrogen chamber.

Wherein the accumulator functions as follows: (1) the energy storage piston is pushed by pressure oil to impact forwards, when the impact is finished and the piston retracts backwards, the energy storage device can buffer the oil chamber to store the energy of the redundant pressure oil and release the energy in the next stroke, so that the oil supply quantity of an impact stroke is increased, the impact speed of the impact piston is increased, and the energy consumption is reduced. (2) The impact energy of the buffer hydraulic rock drill is very large, the recoil force transmitted from the drill rod is also very large, and the buffer oil chamber of the energy accumulator can absorb the recoil force transmitted from the drill rod. (3) When the pressure oil of the hydraulic system has great impact and vibration, the energy accumulator can absorb or relieve the impact and vibration to avoid damaging the system pipeline and parts

In this embodiment, the frequency f of the hydraulic rock drill is equal to the rotation speed r of the hydraulic motor 14 multiplied by the number n of oil delivery channels at the same position on the rotating sleeve 8, and f = r × n.

As shown in fig. 1 to 11, when in use, the hydraulic motor 14 works and outputs power to drive the rotary sleeve 8 to rotate continuously through the connecting sleeve 13, when the rotary sleeve 8 rotates to a stroke position shown in fig. 5, the front chamber oil delivery passage 86 is communicated with the front chamber oil outlet 62, the first sealing section 87 corresponding to the front chamber oil delivery passage 86 rotates to a position of the front chamber oil inlet 61 to seal the front chamber oil inlet 61, the rear chamber oil delivery passage 88 is communicated with the rear chamber oil inlet 63, and the second sealing section 89 corresponding to the rear chamber oil delivery passage 88 rotates to a position of the rear chamber oil outlet 64 to seal the rear chamber oil outlet 64.

At this time, the hydraulic oil output from the oil inlet pipeline 17 enters the piston rear chamber 16, the hydraulic oil in the piston front chamber 15 enters the oil outlet pipeline 18 through the front chamber oil delivery channel 86 and the front chamber oil outlet 62, the pressure of the hydraulic oil in the piston rear chamber 16 is greater than that of the hydraulic oil in the piston front chamber 15, and the piston 9 moves forward under the pressure of the hydraulic oil in the piston rear chamber 16, so that the root of the drill bit shank 1 is impacted, and the stroke is completed.

When the rotary sleeve 8 rotates by a certain angle to reach the retreating position shown in fig. 6, when the front chamber oil delivery channel 86 is communicated with the front chamber oil inlet 61, the first sealing section 87 corresponding to the front chamber oil delivery channel 86 is rotated to the position of the front chamber oil outlet 62 for sealing the front chamber oil outlet 62, and the rear chamber oil delivery channel 88 is communicated with the rear chamber oil outlet 64 at this time, and the second sealing section 89 corresponding to the rear chamber oil delivery channel 88 is rotated to the position of the rear chamber oil inlet 63 for sealing the rear chamber oil inlet 63.

At this time, the hydraulic oil output from the oil inlet pipeline 17 enters the piston front chamber 15, the hydraulic oil in the piston rear chamber 16 enters the oil outlet pipeline 18 through the rear chamber oil delivery channel 88 and the rear chamber oil outlet 64, the pressure of the hydraulic oil in the piston front chamber 15 is greater than that of the hydraulic oil in the piston rear chamber 16, and the piston 9 moves backwards under the pressure of the hydraulic oil in the piston front chamber 15, so that the piston 9 is far away from the drill shank 1, the rear piston rod 93 of the piston 9 impacts on the buffer device, and the retreating process is completed.

When the rotary sleeve 8 rotates to the retreating position shown in fig. 6, hydraulic oil is filled in the buffer chamber 84, the piston 9 moves towards one side close to the buffer column 85 under the action of the pressure of the hydraulic oil in the piston front chamber 15, the rear piston rod 93 of the piston 9 moves towards one side close to the buffer column 85, at this time, the rear piston cavity 94 is in contact with the buffer column 85, further, the hydraulic oil in the rear piston cavity 94 begins to be discharged outwards under the action of the pressure, the discharge speed of the hydraulic oil in the rear piston cavity 94 is gradually reduced to stop along with the continuous backward movement of the piston 9, and at this time, the movement speed of the piston 9 is also reduced from the original high speed under the reaction force of the hydraulic oil until the piston stops.

For those skilled in the art, based on the teachings of the present invention, changes, modifications, substitutions and variations can be made to the embodiments without departing from the principles and spirit of the invention.

Claims

1. The utility model provides a hydraulic rock drill of rotatory telescopic in area, includes shell (6), and the both ends of shell (6) are provided with front end housing (2) and rear end housing (12) respectively, and shell (6) internalization is provided with bore bit shank (1) and is used for striking piston (9) of bore bit shank (1), its characterized in that: the outside activity cover that lies in piston (9) in shell (6) is equipped with rotating sleeve (8), the both sides that lie in piston (9) in rotating sleeve (8) are provided with preceding cavity of piston (15) and piston rear chamber (16) respectively, rotating sleeve (8) are located shell (6) internal rotation and through in proper order alternately to leading cavity of piston (15) and piston rear chamber (16) in let in hydraulic oil and force piston (9) to be located rotating sleeve (8) and carry out stroke and back stroke motion, drill rod tail (1) is close to the one end of rotating sleeve (8) and links to each other and with rotating sleeve (8) synchronous revolution.

2. A hydraulic rock drill with a rotary sleeve according to claim 1 characterised in that: a hydraulic motor (14) is fixedly arranged on the rear end cover (12), the power output end of the hydraulic motor (14) is in transmission connection with the rotating sleeve (8), the hydraulic motor (14) outputs power to drive the rotating sleeve (8) to rotate, and the rotating sleeve (8) transmits torque to drive the drill bit shank (1) to rotate.

3. A hydraulic rock drill with a rotary sleeve according to claim 2 characterised in that: the drill bit tail is characterized in that a connecting sealing sleeve (4) is fixedly arranged at a position, close to the drill bit tail (1), on the rotating sleeve (8), a mounting cavity (41) is formed in the connecting sealing sleeve (4), the drill bit tail (1) is in transmission connection with the rotating sleeve (8) through the connecting sealing sleeve (4), and the drill bit tail (1) is connected with the connecting sealing sleeve (4) through meshing teeth or splines.

4. A hydraulic rock drill with a rotary sleeve according to claim 3 characterised in that: and a limiting and supporting assembly for supporting the rotating sleeve (8) to rotate and limiting the position of the rotating sleeve (8) in the shell (6) is arranged on the outer surface of the rotating sleeve (8).

5. A hydraulic rock drill with a rotary sleeve according to claim 4 characterised in that: rotating sleeve (8) includes main part and packaging plate (82), packaging plate (82) and connection seal cover (4) are located the axial both ends of piston (9) respectively, the axial both ends of packaging plate (82) link to each other with the main part respectively in order to inject the activity space of piston (9), be equipped with connecting axle (83) that the orientation kept away from piston (9) direction extension on packaging plate (82), be provided with intermediate bottom (81) towards piston (9) extension on the main part, it is provided with buffering cavity (84) to lie in rotating sleeve (8) between intermediate bottom (81) and packaging plate (82), be provided with the buffer who is used for buffering the back stroke impact force of piston (9) on packaging plate (82) of buffering cavity (84).

6. A hydraulic rock drill with a rotary sleeve according to claim 5, characterized in that: piston (9) coaxial setting is in rotatory sleeve (8), piston (9) are including piston main part (91), piston main part (91) and the sealed sliding connection of internal surface of rotatory sleeve (8), both sides are integrative being connected with preceding piston rod (92) and back piston rod (93) respectively around piston main part (91), the one end through connection seal cover (4) of preceding piston rod (92) and extend to in installation cavity (41), the one end of back piston rod (93) is run through intermediate bottom (81) and is extended to in buffer chamber (84).

7. A hydraulic rock drill with a rotary sleeve according to claim 6, characterized in that: the buffering device comprises a buffering column (85) which is integrally arranged on a packaging plate (82) and located at the center position, the buffering column (85) and a piston (9) are coaxially arranged, a piston rear cavity (94) is formed in one end, far away from a piston main body (91), of a rear piston rod (93), and the cross section shape of the piston rear cavity (94) is matched with that of the buffering column (85).

8. A hydraulic rock drill with a rotary sleeve according to claim 7 characterised in that: a front cavity oil inlet (61) and a front cavity oil outlet (62) are respectively formed in the position, corresponding to the front cavity (15) of the piston, of the shell (6), a rear cavity oil inlet (63) and a rear cavity oil outlet (64) are respectively formed in the position, corresponding to the rear cavity (16) of the piston, of the shell (6), and a buffer cavity oil return opening (65) is formed in the position, corresponding to the buffer cavity (84), of the shell (6).

9. A hydraulic rock drill with a rotary sleeve according to claim 8 characterised in that: a plurality of front cavity oil conveying channels (86) communicated with the piston front cavity (15) are formed in the rotary sleeve (8), a first sealing section (87) is arranged between every two adjacent front cavity oil conveying channels (86), and the rotary sleeve (8) is positioned in the shell (6) to rotate so that the front cavity oil conveying channels (86) are respectively communicated with the front cavity oil inlet (61) and the front cavity oil outlet (62) in sequence and alternately.

10. A hydraulic rock drill with a rotary sleeve according to claim 9 characterised in that: a plurality of rear cavity oil conveying channels (88) communicated with the piston rear cavity (16) are formed in the rotary sleeve (8), the rear cavity oil conveying channels (88) and the front cavity oil conveying channels (86) are arranged in a staggered mode, a second sealing section (89) is arranged between every two adjacent rear cavity oil conveying channels (88), and the rotary sleeve (8) is located in the shell (6) and rotates to enable the rear cavity oil conveying channels (88) to be sequentially communicated with the rear cavity oil inlet (63) and the rear cavity oil outlet (64) in an alternating mode.