CN115788274A

CN115788274A - Hydraulic rock drill

Info

Publication number: CN115788274A
Application number: CN202211355559.7A
Authority: CN
Inventors: 吴忆文; 肖浩; 常旭阳
Original assignee: Shanghai Lvzuan Machinery Co ltd; Plod Changzhou Hydraulic Technology Co ltd
Current assignee: Shanghai Lvzuan Machinery Co ltd; Plod Changzhou Hydraulic Technology Co ltd
Priority date: 2022-11-01
Filing date: 2022-11-01
Publication date: 2023-03-14

Abstract

The invention discloses a hydraulic rock drill, which comprises a machine body with a cavity, a piston and a drill bit tail, wherein the machine body is composed of a machine base, a cylinder barrel, an intermediate body, a gear box cover and a machine head which are sequentially fixed and hermetically connected, the piston can axially move in the machine body, and the drill bit tail can axially move and rotate relative to the machine body. The hydraulic rock drill adopts unique idle stroke prevention design, stroke brake design, return stroke brake design, valve sleeve reversing push rod design, multi-section piston design, leakage cavity design, independently designed impact part and rotary part and design without radial relative motion, and effectively solves the problems of low power efficiency, short service life of structures and parts, large vibration and large noise in the working process of the existing rock drill.

Description

Hydraulic rock drill

Technical Field

The invention relates to a hydraulic rock drill, and belongs to the technical field of rock drills.

Background

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 bit shank head crushes and drills rock to a certain depth to form a dent. After the piston is withdrawn, the drill bit shank rotates by a certain angle, the piston moves forwards, and a new dent is formed when the piston impacts the drill bit shank again. The segmental rock mass between the two indents is sheared by the horizontal force component generated on the shank adapter. The piston continuously impacts the drill bit shank and continuously inputs compressed air or pressure water from the central hole of the drill bit shank to discharge rock slag out of the hole, namely a circular drill hole with a certain depth is formed.

While the rock drill industry is continuously developed, the hydraulic rock drill produced in China is low in efficiency, for example, the power conversion efficiency of a back cavity oil return rock drill is generally below 55%; the service life of partial structure and parts is short, the vibration is large in the working process, the energy transfer efficiency is low, and the like, so that most rock drills depend on an inlet.

Disclosure of Invention

In order to solve the defects of the prior art, the invention provides the hydraulic rock drill which adopts independent research and development and independent design, has excellent power conversion efficiency, small vibration and small noise, can prolong the service life of parts, and is convenient to maintain.

The technical scheme adopted by the invention is as follows:

the utility model provides a hydraulic rock drill, includes the organism that has the cavity of constituteing by frame, cylinder, midbody, gear box lid and the aircraft nose fixed and sealing connection in proper order, still be provided with in the organism:

the valve is arranged in the base, the cylinder body is arranged in the cylinder barrel, a plurality of corresponding rear push rod channels and front push rod channels are respectively and uniformly arranged in one end where the valve and the cylinder body are abutted, a rear push rod and a front push rod are respectively and slidably arranged in each rear push rod channel and each front push rod channel, and the diameter of the front push rod is larger than that of the rear push rod;

the piston is provided with a central hole, horizontally penetrates through the valve and the cylinder body, the rear end of the piston is positioned in the inner cavity of the machine base at the rear side of the valve, the front end of the piston extends into the lubricating air chamber at the front end of the intermediate body, rod bodies at two ends of the piston are respectively in sealing connection with the valve and the intermediate body to form a closed space for preventing hydraulic oil leakage, and the piston can axially displace relative to the valve, the cylinder body and the intermediate body;

the valve sleeve is sleeved on the piston positioned in the inner cavity at the front end of the valve and can axially displace under the action of oil pressure;

an oil inlet channel and an oil return channel are formed among the piston, the valve sleeve, the valve, the cylinder body, the base and the cylinder barrel, and the front side surface and the rear side surface of the base are respectively provided with an oil inlet P communicated with the oil inlet channel and an oil outlet T communicated with the oil return channel;

the drill rod tail is horizontally and rotatably arranged in the gear box, the gear box cover and the machine head, extends out of the front end of the machine head, and acts on the drill rod tail to enable the drill rod tail to axially displace when the piston is acted by hydraulic oil to axially displace forwards;

the transmission mechanism is arranged in the gear box, a cycloid motor for driving the transmission mechanism to act so as to drive the drill bit shank to rotate is fixedly arranged outside the gear box, and a rear retaining sleeve and a front retaining sleeve for limiting the axial displacement distance of the drill bit shank are respectively arranged in an inner cavity at the front end of the transmission mechanism and an inner cavity at the rear end of the machine head;

the inner cavity of the engine base at the rear side of the valve, the central hole of the piston, the intermediate body, the drill shank, the transmission mechanism, the rear retaining sleeve, the front retaining sleeve and the engine head form a lubricating and cooling channel, the drill shank and the engine head form a flushing channel, the intermediate body is provided with two lubricating air ports communicated with the lubricating and cooling channel, and the engine head is provided with a flushing water port communicated with the flushing channel.

As a preferred form of the present invention,

the valve is provided with a first high-pressure oil cavity, a first main oil return cavity, a first oil inlet P, an oil outlet T and a plurality of high-pressure oil channels, wherein the first high-pressure oil cavity is formed with the base from back to front;

the cylinder body is provided with a first oil return cavity with the front end of the valve, and a second oil return cavity, an inner ring groove and a second high-pressure oil cavity are sequentially formed in the cylinder body from back to front, the second oil return cavity is communicated with the first oil return cavity and the total oil return cavity, the second high-pressure oil cavity is communicated with the first high-pressure oil cavity, a leakage ring chamber is formed between the cylinder body and the cylinder barrel at the front end of the second high-pressure oil cavity, an oil return channel for communicating the leakage ring chamber with the second oil return cavity is arranged in the cylinder body, and a plurality of front push rod channels are communicated with the inner ring groove;

the piston is provided with a background stage and a foreground stage, the background stage of the piston can axially displace in an inner cavity at the front end of the valve and an inner cavity at the rear end of the cylinder body, the cylinder body is provided with an inner stage D for separating the inner ring groove and the high-pressure oil cavity II and an inner stage E for separating the high-pressure oil cavity II and the inner cavity at the front end of the cylinder body, and the foreground stage of the piston can axially displace in the inner stage D, the high-pressure oil cavity II and the inner stage E of the cylinder body;

the high-pressure oil cavity I, the high-pressure oil channel and the high-pressure oil cavity II form an oil inlet channel; the leakage cavity, the oil return cavity II, the oil return cavity I and the main oil return cavity form an oil return channel.

As a preferred form of the present invention, the,

the backstage stage rear end of piston forms stress surface A, and the front end forms stress surface C, and piston foreground stage rear end forms cross-section B, and the front end forms stress surface B, and stress surface A's stress area is greater than stress surface C, stress surface B's stress area, and the diameter that is located the piston between stress surface C and the cross-section B is greater than the diameter that is located the piston of stress surface A rear side, is less than the diameter that is located the piston of stress surface B front side.

Preferably, a front sealing seat for the piston to pass through and be connected with the piston in a sealing manner is arranged in an inner cavity at the rear end of the intermediate body, the valve and the front sealing seat in the intermediate body are connected with the piston in a sealing manner to form a sealed space for preventing hydraulic oil leakage, a front copper sleeve for the piston to pass through is arranged in an inner cavity at the front end of the cylinder body, and the front copper sleeve is connected with the cylinder body in a sealing manner.

Preferably, a piston rear end leakage chamber is arranged in the inner cavity of the rear end of the valve, and the piston rear end leakage chamber is communicated with the main oil return cavity through an inclined hole in the valve; and a piston front end leakage cavity is formed at the front end of the front copper sleeve, the front sealing seat and the inner cavity of the front end of the cylinder body, and the piston front end leakage cavity is communicated with the leakage ring chamber through a through hole in the cylinder body.

As a preferred aspect of the present invention, a dust ring through which the piston passes is further disposed at the front end of the front sealing seat, and a high-pressure accumulator is further disposed on the machine base.

As a preferable aspect of the present invention, the transmission mechanism includes:

the pinion is arranged in a cavity above the gear box, is fixedly connected with the actuating shaft of the cycloid motor and is rotationally connected with the gear box through needle roller bearings arranged at the outer sides of the two ends;

the sealing sleeve is arranged in the inner cavity at the front end of the gear box, the front end of the sealing sleeve is embedded into the gear box cover, and the sealing sleeve is fixedly connected and sealed with the gear box and the gear box cover;

the large gear is arranged in a cavity below the gear box and is meshed with the small gear, two ends of the large gear penetrate through the gear box, the front end of the large gear extends into an inner cavity of a gear box cover, the large gear is rotatably connected with the gear box through two conical bearings arranged on the outer peripheries of the two ends of the large gear, and the rear end of the drill shank is inserted into the inner cavity of the large gear without rotation and clearance fit;

the rear retaining sleeve is arranged in a cavity at the front end of the large gear, a limiting space is formed between the rear retaining sleeve and the front retaining sleeve, the drill shank penetrates through the rear retaining sleeve and the front retaining sleeve, and a limiting table surface is formed on the drill shank in the limiting space.

Preferably, shaft seals respectively abutted against the outer peripheries of the two ends of the large gear are arranged in the inner cavity at the rear end of the gear box and the inner cavity at the rear end of the gear box cover, and retaining rings respectively matched with the inner cavity at the rear end of the gear box and the inner cavity at the rear end of the gear box cover to limit the corresponding shaft seals are arranged in the inner cavity at the rear end of the gear box and the inner cavity at the rear end of the gear box cover.

Preferably, the rear retaining sleeve is internally provided with two symmetrical through holes, a plurality of supporting blocks for supporting the drill shank are formed on the inner surface of the rear retaining sleeve in a surrounding manner, an air channel for lubricating air to pass through and communicated with the through holes is formed between the supporting blocks, and an air passing gap I is formed between the surface of the rear retaining sleeve positioned at the outer end of the through holes and the inner cavity of the front section of the bull gear;

a second air passing gap is formed between the front blocking sleeve and the rear blocking sleeve, and two air passing grooves corresponding to the through holes are formed on the front blocking sleeve;

a nose copper sleeve for limiting through a check ring is arranged in an inner cavity at the front end of the nose, the inner wall of the nose copper sleeve is attached to the periphery of the drill bit shank, a drill bit shank protective ring is arranged at the nose end part at the front end of the nose copper sleeve, a plurality of corresponding air passing holes are formed in the nose copper sleeve, and an inner air groove communicated with the air passing holes is formed in the nose copper sleeve;

an air passing ring is formed on the section of the inner cavity at the rear end of the machine head, an air passing groove communicated with the air passing hole is formed in the inner cavity at the front end of the machine head, and the air passing ring is communicated with the air passing groove through a lubricating air passage formed in the machine head;

the engine base inner cavity, the piston center hole, the lubricating air chamber, the air passing channel, the through hole, the air passing gap I, the air passing gap II, the air passing groove, the air passing ring, the lubricating air passage, the air passing groove, the air passing hole and the inner air chamber on the rear side of the valve form a lubricating and cooling channel.

Preferably, a water trough is formed in the inner cavity of the machine head between the copper sleeve and the air passing ring, and a plurality of U-shaped seals for sealing with the drill bit shank are arranged in the inner cavities of the machine head at the front end and the rear end of the water trough;

the flushing water port in the machine head is communicated with the water trough, the drill bit shank is provided with a water-flowing hole which is communicated with the water trough and the inner cavity at the front end of the drill bit shank, and the water trough and the water-flowing hole form a flushing channel.

The invention has the beneficial effects that:

1. by adopting a unique idle driving prevention design, the distance of the piston moving rightwards is always within a designed stroke, and other parts of the machine cannot be impacted and damaged; by adopting a unique stroke braking design, the motion of the piston is reversed while the piston strikes the drill bit shank, so that the optimal impact power and frequency are achieved; by adopting a unique return braking design, the piston return quick braking and reversing are realized, and the impact frequency is improved;

2. by adopting the unique design of the valve sleeve reversing push rod, the problem of large leakage of the reversing valve of the back-cavity oil-return rock drill is solved, and the efficiency of the rock drill is improved;

3. the piston return stroke variable speed movement is realized by adopting a unique multi-section piston design, and the front section phi 33: phi 38 annulus pressure force, accelerated return stroke, rear segment phi 35: the differential pressure of the phi 38 ring surface reduces the return acceleration, improves the braking speed of the piston during the stroke, and improves the frequency of the rock drill;

4. by adopting a unique leakage cavity design, the steckel seal sealing elements at two ends of the piston are always in a low-pressure (oil return pressure) working state, so that the service life of the sealing elements can be prolonged;

5. the impact part and the rotation part which are independently designed are adopted, so that the maintenance is convenient; and the rock drill can be simply deformed into a hydraulic impactor by replacing the front end rotary part;

6. the design without radial relative motion is adopted, the outer hexagonal design is adopted at the tail part of the drill bit shank, the large gear and the rear retaining sleeve are both designed in an inner hexagonal shape, and when the design and the rear retaining sleeve are used in a matched mode, the large gear drives the drill bit shank to rotate, and the drill bit shank drives the rear retaining sleeve of the drill bit shank to rotate, so that the service life of parts can be prolonged;

7. the vibration is small, the noise is small, the optimal power efficiency is 73% when the impact pressure is 140bar, the impact power is maximum when the impact pressure is 160bar, the power conversion efficiency is obviously improved, and the efficiency of the rock drill is obviously improved.

Drawings

Fig. 1 is a schematic perspective view of a hydraulic rock drill according to the present invention;

fig. 2 is a cross-sectional view of a hydraulic rock drill provided by the present invention;

fig. 3 is a cross-sectional view of a piston section rock drill according to the invention;

FIG. 4 is a sectional view of a stepped surface section of a piston and an inner platform of a cylinder barrel;

FIG. 5 is a schematic perspective view of the valve;

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

FIG. 7 is a perspective view of the cylinder barrel;

FIG. 8 is a cross-sectional view of the cylinder barrel;

FIG. 9 is a cross-sectional view of the intermediate body;

FIG. 10 is a cross-sectional view of the transmission;

FIG. 11 is a cross-sectional view at the handpiece;

FIG. 12 is a perspective view of a bull gear;

FIG. 13 is a perspective view of a shank adapter;

FIG. 14 is a schematic perspective view of a rear spacer sleeve;

FIG. 15 is a schematic perspective view of a front sleeve;

FIG. 16 is a schematic diagram of a first stage of the stroke and reversing process;

FIG. 17 is a structural diagram of a second stage of the stroke and reversing process;

FIG. 18 is a schematic view of a third stage of the stroke and commutation process;

FIG. 19 is a schematic diagram of a first stage of the return stroke and reversing process;

FIG. 20 is a schematic diagram of a second stage structure during the return stroke and the reversing process;

FIG. 21 is a schematic structural view of idle driving prevention and stroke braking;

FIG. 22 is a schematic structural view of a return brake;

FIG. 23 is a schematic view of a multi-section piston in one state;

FIG. 24 is a schematic view of the multi-section piston in another state;

FIG. 25 is a schematic view of lubrication and cooling passages;

FIG. 26 is a schematic view of a flush channel;

FIG. 27 is a graph showing the results of comparative tests;

FIG. 28 is a graph of piston displacement versus time at an impact pressure of 80 bar;

FIG. 29 is a graph of piston displacement versus time at a percussion pressure of 100 bar;

FIG. 30 is a graph of piston displacement versus time at a percussion pressure of 120 bar;

FIG. 31 is a graph of piston displacement versus time at a 140bar impact pressure;

FIG. 32 is a graph of piston displacement versus time at a percussion pressure of 160 bar;

FIG. 33 is a perspective view of the valve and valve housing;

the main reference numerals in the figures have the following meanings:

1. a machine base, 2, a cylinder barrel, 3, a middle body, 4, a gear box, 5, a gear box cover, 6, a machine head, 7, a piston, 8, a drill rod tail, 9, a sealing sleeve, 10, a positioning pin, 11, a long screw rod component, 12, a short screw rod component, 13, a valve, 14, a cylinder body, 15, a front copper sleeve, 16, a front sealing seat, 17, a dust ring, 18, a Stent seal, 19, a high-pressure oil cavity I, 20, a total oil return cavity, 21, an oil inlet P,22, an oil outlet T,23, a high-pressure oil channel, 24, a rear push rod channel, 25, an oil return cavity I, 26, an oil return cavity II, 27, an inner ring groove, 28, a high-pressure oil cavity II, 29, a hole channel I, 30, a hole channel II, 31, a hole channel III, 32, a sinking cavity, 33, an oil passing channel, 34, a leakage ring chamber, a leakage chamber, 35, an oil return channel, 36, a front push rod channel, 37, a piston rear end leakage chamber, 38, an inclined hole, 39 and a piston front end leakage chamber, 40, through holes, 41, a rear push rod, 42, a front push rod, 43, a valve sleeve, 44, a background stage, 45, a foreground stage, 46, stress surfaces A,47, stress surfaces C,48, sections B,49, stress surfaces B,50, inner stages D,51, inner stages E,52, a high-pressure accumulator, 53, a cycloid motor, 54, a rear retaining sleeve, 55, a front retaining sleeve, 56, a pinion, 57, a gearwheel, 58, a needle bearing, 59, a conical bearing, 60, a limiting table surface, 61, a shaft seal, 62, a retainer ring, 63, a through hole, 64, a support block, 65, an air passage, 66, an air passage first, 67, an air passage second, 68, an air passage groove, 69, a nose copper sleeve, 70, a drill bit tail protective ring, 71, an air passage hole, 72, an inner air groove, 73, an air passage ring, 74, an air passage groove, 75, a lubricating air passage, 76, a lubricating channel, a water passage groove, 78, a U-shaped air sealing port, 79. water flowing hole 80, flushing water port 81 and lubricating air chamber.

Detailed Description

The present invention will be described in detail with reference to the accompanying drawings and examples.

As shown in fig. 1-33: the embodiment is a hydraulic rock drill, and as shown in fig. 1 and fig. 2, the hydraulic rock drill comprises a machine body with a cavity, a piston 7 capable of axially displacing in the machine body and a drill shank 8 capable of axially displacing and rotating relative to the machine body, wherein the machine body consists of a machine base 1, a cylinder barrel 2, an intermediate body 3, a gear box 4, a gear box cover 5 and a machine head 6 which are fixedly connected in sequence.

The rear end of a cylinder barrel 2 is inserted into the front end of a machine base 1, the rear end of a midbody 3 is inserted into the front end of the cylinder barrel 2, the rear end of a gear box 4 is inserted into the front end of the midbody 3, abutting surfaces of two adjacent components are sealed through sealing rings, a sealing sleeve 9 is arranged in an inner cavity of the front end of the gear box 4, the rear end of a gear box cover 5 is embedded into the sealing sleeve 9, similarly, the sealing sleeve 9 and the gear box 4 and the abutting surfaces of the gear box cover 5 are sealed through the sealing rings, the machine base 1, the cylinder barrel 2, the midbody 3, the gear box 4 and the gear box cover 5 are positioned through a plurality of positioning pins 10 in abutting ends of the machine head 6, the machine base 1, the cylinder barrel 2, the midbody 3, the gear box 4 and the gear box cover 5 are assembled into a whole through four long screw rod assemblies 11, and the machine head 6 is fixed with the gear box cover 5 through four short screw rod assemblies 12, so that a machine body is formed.

Referring to fig. 3 and 4, a valve 13 is arranged in an inner cavity of a machine base 1, a cylinder 14 is arranged in a cylinder 2 between the valve 13 and an intermediate body 3, the valve 13 and the cylinder 14 are also positioned by positioning pins, a front copper sleeve 15 is clamped in an inner cavity at the front end of the cylinder 14, a front sealing seat 16 is clamped in an inner cavity at the rear end of the intermediate body 3, a piston 7 sequentially penetrates through the valve 13, the cylinder 2, the front copper sleeve 15 and the front sealing seat 16 and extends into a lubricating air chamber 81 at the front end of the intermediate body 3, and a dust ring 17 for the piston 7 to penetrate through is clamped at the front end of the front sealing seat 16.

Sealing rings are arranged between contact surfaces of the valve 13 and the base 1, between contact surfaces of the cylinder 14 and the cylinder barrel 2, between the cylinder 14 and the intermediate body 3 and the front copper sleeve 15, and between contact surfaces of the intermediate body 3 and the front sealing seat 16; and a stirling seal 18 for sealing is provided in both grooves in the valve 13 and in both grooves in the front seal seat 16 to prevent leakage of hydraulic oil.

The valve 13 and the base 1 form a high-pressure oil chamber I19, a total oil return chamber 20 is formed with the base 1 and the cylinder barrel 2, the base 1 is provided with an oil inlet P21 communicated with the high-pressure oil chamber I19 and an oil outlet T22 communicated with the total oil return chamber 20, the valve 13 is internally provided with a plurality of high-pressure oil channels 23 communicated with an inner chamber at the front end of the valve 13, the front end of the valve 13 is internally provided with four rear push rod channels 24, and the four rear push rod channels 24 are correspondingly communicated with the four high-pressure oil channels 23.

Referring to fig. 3-9 and 33, a first oil return cavity 25 is formed at the front end of the cylinder 14 and the valve 13, and a second oil return cavity 26, an inner annular groove 27 and a second high-pressure oil cavity 28 are sequentially formed in the cylinder 14 from back to front, wherein the second oil return cavity 26 is communicated with the first oil return cavity 25 through a first duct 29 in the cylinder 14, and is communicated with the main oil return cavity 20 through a second duct 30 communicated with the first duct 29 and a third duct 31 communicated with the second duct 30 in the valve 13; two sinking cavities 32 communicated with the second high-pressure oil cavity 28 are formed between the middle cylinder block 14 and the cylinder barrel 2; a plurality of oil passing channels 33 which are communicated with each other are arranged in the front end valve 13 and the rear end cylinder body 14, one end of each oil passing channel 33 is respectively communicated with the plurality of high-pressure oil channels 23, the other end of each oil passing channel 33 is communicated with the corresponding sinking cavity 32, and then the second high-pressure oil cavity 28 is communicated with the first high-pressure oil cavity 19; a leakage ring chamber 34 is formed between the cylinder body 14 and the cylinder barrel 2 which are positioned at the front end of the second high-pressure oil chamber 28, an oil return channel 35 for communicating the leakage ring chamber 34 with the second oil return chamber 26 is arranged in the cylinder body 14, and the oil return channel 35 is arranged corresponding to the first pore channel 29; the rear cylinder 14 has a plurality of front rod passages 36 therein, which correspond to the rear rod passages 24, respectively, and the front ends of which communicate with the inner annular groove 27.

The rear end cavity of the valve 13 is provided with a rear end piston leakage chamber 37, the rear end piston leakage chamber 37 is positioned at the front side of the Stent seal 18 on the valve 13, and the rear end piston leakage chamber 37 is communicated with the main oil return cavity 20 through an inclined hole 38 on the valve 13; the front end of the front copper sleeve 15, the front sealing seat 16 and the front inner cavity of the cylinder 14 form a front piston end leakage chamber 39, and the front piston end leakage chamber 39 is communicated with the leakage ring chamber 34 through a through hole 40 on the cylinder 14.

A rear push rod 41 and a front push rod 42 are respectively embedded in each rear push rod channel 24 and each front push rod channel 36, the diameter of the front push rod 42 is larger than that of the rear push rod 41, and the rear push rod 41 and the front push rod 42 can freely move (clearance fit) in the corresponding rear push rod channel 24 and the corresponding front push rod channel 36; a valve bush 43 is clamped in the front-end inner cavity of the valve 13, the valve bush 43 can move freely (in clearance fit) in the front-end inner cavity of the valve 13, in an initial state, the rear end of the valve bush 43 is abutted against the inner part of the front-end inner cavity of the valve 13 to seal the inner end of the high-pressure oil channel 23, and a clearance for communicating the inner cavity of the valve bush 43 with the oil return cavity I25 is formed between the front end of the valve bush 43 and the rear end of the cylinder 14; the periphery of the front end of the valve sleeve 43 forms a bulge, the rear push rod 41 is abutted against the rear end face of the bulge, the front push rod 42 is abutted against the front end face of the bulge, and the valve sleeve 43 can axially displace relative to the piston 7 in a space formed by the front end inner cavity of the valve 13 and the rear end inner cavity of the cylinder 14 under the action of hydraulic oil.

The piston 7 is provided with a background stage 44 and a foreground stage 45, the rear end of the background stage 44 of the piston 7 forms a stress surface A46, the front end forms a stress surface C47, the rear end of the foreground stage 45 of the piston 7 forms a cross section B48, the front end forms a stress surface B49, and the stress area of the stress surface A46 is larger than the stress areas of the stress surface C47 and the stress surface B49; and the back stage 44 of the piston 7 is axially displaceable in the front end inner chamber of the valve 13 and the rear end inner chamber of the cylinder 14, the cylinder 14 has an inner stage D50 for separating the inner annular groove 27 and the second high-pressure oil chamber 28 and an inner stage E51 for separating the second high-pressure oil chamber 28 and the front end inner chamber of the cylinder 14, and the front stage 45 of the piston 7 is axially displaceable in the inner stage D50, the second high-pressure oil chamber 28 and the inner stage E51 of the cylinder 14.

Referring to fig. 1, a high-pressure energy accumulator 52 is arranged at the rear end of a machine base 1, a high-pressure diaphragm is placed in a groove at the upper end of the machine base 1, an outer cover is screwed into the machine base 1, a nitrogen-filled connector and a plug are screwed into the outer cover, a plurality of inner holes for communicating the groove at the upper end with a high-pressure oil cavity I19 are formed in the machine base 1, and the high-pressure energy accumulator 52 serves as a common structure in the existing rock drilling machine, can be used as a liquid compensation device, eliminates pulsation, reduces noise, absorbs hydraulic impact and serves as a hydraulic air spring.

Referring to fig. 10-15, the drill rod 8 is horizontally and rotatably arranged in the gear box 4, the gear box cover 5 and the nose 6 and extends out of the front end of the nose 6, the rear end of the drill rod 8 extends into the lubricating air chamber 81 of the intermediate body 3 and has a certain distance to be punched with the front end of the piston 7, and when the piston 7 is axially displaced forwards under the action of hydraulic oil, the drill rod 8 is acted on the drill rod to axially displace the piston 7.

A transmission mechanism is arranged in the gear box 4, a cycloid motor 53 for driving the transmission mechanism to act so as to drive the drill bit shank 8 to rotate is fixedly arranged outside the gear box 4, and a rear retaining sleeve 54 and a front retaining sleeve 55 for limiting the axial displacement distance of the drill bit shank 8 are respectively arranged in an inner cavity at the front end of the transmission mechanism and an inner cavity at the rear end of the nose 6.

The transmission mechanism comprises a small gear 56, a large gear 57 and the sealing sleeve 9, wherein the small gear 56 is arranged in a cavity above the gear box 4, is fixedly connected with an actuating shaft of the cycloid motor 53 and is rotationally connected with the gear box 4 through needle bearings 58 arranged at the outer sides of two ends; the sealing sleeve 9 is arranged in the inner cavity at the front end of the gear box 4, the front end of the sealing sleeve is embedded into the gear box cover 5, and the sealing sleeve is fixedly connected and sealed with the gear box 4 and the gear box cover 5; the large gear 57 is arranged in a cavity below the gear box 4 and is meshed with the small gear 56, two ends of the large gear penetrate through the gear box 4, the front end of the large gear extends into an inner cavity of the gear box cover 5, the large gear is rotatably connected with the gear box 4 through two conical bearings 59 arranged on the peripheries of the two ends, the rear end of the drill rod shank 8 is inserted into the inner cavity of the large gear 57 and is free of rotation and clearance fit, in actual application, the rear end of the drill rod shank 8 adopts an outer hexagonal design, and an inner hole of the large gear 57 adopts an inner hexagonal design, so that the drill rod shank 8 and the large gear 57 do not move relative to each other in a radial direction.

The rear retaining sleeve 54 is arranged in the cavity at the front end of the large gear 57, a limiting space is formed between the rear retaining sleeve 54 and the front retaining sleeve 55, the drill shank 8 penetrates through the rear retaining sleeve 54 and the front retaining sleeve 55, and a limiting table surface 60 is formed on the drill shank 8 in the limiting space.

Shaft seals 61 which are respectively abutted against the outer peripheries of the two ends of the large gear 57 are respectively arranged in the inner cavity of the rear end of the gear box 4 and the inner cavity of the rear end of the gear box cover 5, and retaining rings 62 which are respectively matched with the inner cavity of the rear end of the gear box 4 and the inner cavity of the rear end of the gear box cover 5 to limit the corresponding shaft seals 61 are respectively arranged in the inner cavity of the rear end of the gear box 4 and the inner cavity of the rear end of the gear box cover 5 which are positioned at the rear end of each shaft seal 61.

The pinion 56 is driven to move through the action of the cycloid motor 53 so as to drive the bull gear 57 to rotate, and the rear end of the drill rod shank 8 is inserted into the inner cavity of the bull gear 57 and is not in rotation and clearance fit, so that the drill rod shank 8 can be driven to rotate when the bull gear 57 rotates.

The rear retaining sleeve 54 is internally provided with two symmetrical through holes 63, a plurality of supporting blocks 64 for supporting the drill shank 8 are formed on the inner surface of the rear retaining sleeve 54 in a surrounding manner, and in practical application, the plurality of supporting blocks 64 form an internal hexagonal design, so that the drill shank 8 and the rear retaining sleeve 54 do not move in a radial direction relative manner, an air passage 65 for lubricating air to pass through and communicate with the through holes 63 is formed between the plurality of supporting blocks 64, and an air passing gap I66 is formed between the surface of the rear retaining sleeve 54 positioned at the outer end of the through holes 63 and the inner cavity of the front section of the large gear 57 after the surface of the rear retaining sleeve 54 is milled and leveled; a second air passing gap 67 is formed between the front blocking sleeve 55 and the rear blocking sleeve 54, and two air passing grooves 68 corresponding to the through holes 63 are formed on the front blocking sleeve 55; a nose copper sleeve 69 which is limited by a retainer ring 62 is arranged in an inner cavity at the front end of the nose 6, the inner wall of the nose copper sleeve 69 is attached to the outer periphery of the drill bit 8, a drill bit protection ring 70 is arranged at the end part of the nose 6 at the front end of the nose copper sleeve 69, a plurality of corresponding air passing holes 71 are formed in the nose copper sleeve 69, and an inner air groove 72 which is communicated with the air passing holes 71 is formed in the nose copper sleeve 69; an air passing ring 73 is formed on the section of the inner cavity at the rear end of the machine head 6, an air passing groove 74 communicated with the air passing hole 71 is formed in the inner cavity at the front end of the machine head 6, and the air passing ring 73 is communicated with the air passing groove 74 through a lubricating air passage 75 formed in the machine head 6; the inner cavity of the machine base 1 at the rear side of the valve 13, the central hole of the piston, the lubricating air chamber, the air leakage channel 65, the through hole 63, the first air leakage gap 66, the second air leakage gap 67, the air leakage groove 68, the air leakage ring 73, the lubricating air channel 75, the air leakage groove 74, the air leakage hole 71 and the inner air groove 72 form a lubricating and cooling channel, and the front side and the rear side of the intermediate body 3 are provided with two lubricating air ports 76 communicated with the lubricating and cooling channel.

A water trough 77 is formed in the inner cavity of the nose 6 between the nose copper sleeve 69 and the air passing ring 73, and a plurality of U-shaped seals 78 for sealing with the drill shank 8 are arranged in the inner cavity of the nose 6 at the front end and the rear end of the water trough 77; a washing water port 80 in the machine head 6 is communicated with the water trough 77, a water trough 79 communicated with the water trough 77 and communicated with an inner cavity at the front end of the drill shank 8 is arranged on the drill shank 8, the water trough 77 and the water trough 79 form a washing channel, and the machine head 6 is provided with the washing water port 80 communicated with the washing channel.

Stroking and reversing

The first stage is as follows: referring to fig. 16, high-pressure hydraulic oil enters the first high-pressure oil chamber 19 through an oil inlet P21 on the base 1, the high-pressure oil enters the high-pressure oil passage 23, at this time, the valve sleeve 43 seals the inner end of the high-pressure oil passage 23, the high-pressure oil enters the left end chamber of the rear push rod passage 24 communicated with the high-pressure oil passage 23, and then, no high-pressure oil exists in the right end chamber of the front push rod passage 36 because the front push rod passage 36, the second oil return chamber 26, the first oil return chamber 25 and the main oil return chamber 20 are communicated and connected to an oil outlet T22 on the base 1.

And a second stage: referring to fig. 17, high-pressure oil always enters the cavity at the left end of the rear push rod channel 24 to push the rear push rod 41 to move axially rightward, so as to push the valve sleeve 43 to move axially rightward, the valve sleeve 43 abuts against the rear end of the cylinder 14 after moving rightward, so that a gap originally formed between the front end of the valve sleeve 43 and the rear end of the cylinder 14 and used for communicating the cavity of the valve sleeve 43 with the oil return cavity one 25 is closed, at this time, the high-pressure oil channel 23 is communicated with the cavity at the front end of the valve 13, so that the high-pressure oil can enter the cavity at the front end of the valve 13, and then the piston 7 is pushed to move axially rightward due to the fact that the stress area of the stress surface a46 is larger than that of the stress surface B49.

And a third stage: referring to fig. 18, in the process of the forward movement of the piston 7, when the section B48 crosses the front end surface of the inner stage D50, the high-pressure oil in the high-pressure oil chamber two 28 enters the inner annular groove 27 and enters the right end chamber of the front push rod channel 36, and then, since the diameter of the front push rod 42 is larger than that of the rear push rod 41, under the condition of equal pressure, the front push rod 42 pushes the valve sleeve 43 to move leftward until the valve sleeve 43 closes the inner end of the high-pressure oil channel 23 again, at this time, the gap originally existing between the front end of the valve sleeve 43 and the rear end of the cylinder 14 and communicating the inner chamber of the valve sleeve 43 and the first return oil chamber 25 is restored, so that the hydraulic oil in the inner chamber of the valve sleeve 43 can enter the first return oil chamber 25 through the gap, and then the force-bearing surface a46 has no pressure, the force-bearing surface C47 enters the inner annular groove 27 through the high-pressure oil chamber two 28, and acts on the force-bearing surface C47 through the gap between the piston 7 and the cylinder 14 to decelerate the piston 7 until the piston 7 hits the drill rod tail 8 and the target after reversing hit.

Return stroke and reversing

The first stage is as follows: after the piston 7 is reversed, because only the force bearing surface C47 is acted by oil pressure, the piston 7 accelerates to move leftwards, when the section B48 crosses the front end surface of the inner stage D50 in the process of moving leftwards of the piston 7, as shown in figure 19, only the force bearing surface B49 is acted by oil pressure, and because the area of the force bearing surface B49 is smaller than that of the force bearing surface A46, the return movement acceleration of the piston 7 is reduced.

And a second stage: as shown in fig. 20, during the process that the piston 7 continues to move leftward, when the force-bearing surface C47 crosses the front end surface of the second oil return cavity 26, the high-pressure oil originally existing in the right end chamber of the front push rod channel 36 enters the second oil return cavity 26, so that the leftward force applied to the front push rod 42 is reduced; since high-pressure oil always enters the left end cavity of the rear push rod channel 24, the valve sleeve 43 is pushed to the right, so that the valve sleeve 43 moves to the right, and when the valve sleeve reaches a certain position, a closed space filled with hydraulic oil is formed by the piston 7, the valve 13, the valve sleeve 43 and the cylinder 14, so that the piston 7 brakes.

When the valve sleeve 43 continues to move rightwards, the inner end of the high-pressure oil channel 23 is opened, and high-pressure oil enters the front end inner cavity of the piston 7 and the inner cavity of the valve sleeve 43 and acts on the stress surface A46, so that the piston 7 is reversed, and a new stroke motion is started.

Air defense beating design

Referring to fig. 21, when the piston 7 moves to the right to reach the force-bearing surface B49 and enters the inner stage E51, the front stage 45 of the piston 7 forms a closed space with the cylinder 14 and the front copper bush 15, so that the piston 7 is braked, the distance of the piston 7 moving to the right is always within the designed stroke, and other parts of the machine are not damaged by impact.

Stroke brake design

Referring to fig. 18, in the process of the forward movement of the piston 7, when the section B48 crosses the front end surface of the inner stage D50, the high-pressure oil in the high-pressure oil chamber two 28 enters the inner annular groove 27 and enters the right end chamber of the front push rod channel 36, and since the diameter of the front push rod 42 is larger than that of the rear push rod 41, under the condition of equal pressure, the front push rod 42 pushes the valve sleeve 43 to move leftward, in the process of the leftward movement of the valve sleeve 43, the valve sleeve 43 closes the inner end of the high-pressure oil channel 23, and meanwhile, a gap between the front end of the valve sleeve 43 and the rear end of the cylinder 14, which is communicated with the inner chamber of the valve sleeve 43 and the first oil return chamber 25, is in a closed state, at this time, a closed space is formed between the piston 7, the valve 13, the valve sleeve 43 and the cylinder 14, and at this time, no high-pressure oil enters the closed space, even though the piston 7 brakes.

Return braking design

Referring to fig. 22, when the piston 7 moves leftwards until the force bearing surface C47 crosses the front end surface of the second oil return cavity 26, the front push rod channel 36 is communicated with the second oil return cavity 26 through the inner annular groove 27 and the gap between the cylinder 14 and the piston 7, so that the front push rod 42 loses oil pressure, the rear push rod 41 is always subjected to oil pressure, so that the rear push rod 41 pushes the valve sleeve 43 to move rightwards, when the front end of the valve sleeve 43 abuts against the rear end of the cylinder 14 to close the gap between the inner cavity of the communicating valve sleeve 43 and the first oil return cavity 25, the inner end of the high-pressure oil channel 23 is not opened, at this time, the inner cavity of the front end of the valve 13, the inner cavity of the valve sleeve 43 and the front end of the cylinder 14 form a closed space, and since liquid is difficult to be compressed, at this time, the piston 7 brakes instantly to realize quick return braking, reversing and increasing impact frequency of the piston 7.

Valve pocket reversing push rod design

The rear push rod 41 slides left and right in the rear push rod channel 24 of the valve 13, the front push rod 42 slides left and right in the front push rod channel 36 of the cylinder 14, the valve sleeve 43 slides left and right in the space formed by the cylinder 14 and the valve 13, the left end of the valve sleeve 43 contacts with the right end of the rear push rod 41, the right end of the valve sleeve 43 contacts with the left end of the front push rod 42, because the left end chamber of the rear push rod channel 24 is always filled with high-pressure oil, the valve sleeve 43 is pushed to the right, and the right end chamber of the front push rod channel 36 alternately has high pressure and low pressure, when high pressure occurs, because the diameter of the rear push rod 41 is smaller than that of the front push rod 42, the valve sleeve 43 is pushed to the left; conversely, when a low pressure occurs, it causes the valve sleeve 43 to be pushed to the right. The oil pressure is reduced by 50% when the gap seal length is 10mm, the oil pressure is reduced by 90% when the gap seal length is 20mm, the gap seal length is larger than 20mm in the whole moving process of the front push rod 42 and the rear push rod 41, only a small amount of leaked high-pressure oil exists, the problem of large leakage of the reversing valve 13 of the oil-return rock drill is solved, and the efficiency of the rock drill is improved.

Multi-section piston design

Referring to fig. 23, when the piston 7 returns (the piston 7 moves to the left), when both end surfaces of the front step section 45 are located in the second high-pressure oil chamber 28, the piston 7 is subjected to Φ 33: Φ 38 annulus differential pressure, accelerated return (left); referring to fig. 24, when the section B48 crosses the front end surface of the inner stage D50, only the force-bearing surface B49 is located in the second high-pressure oil chamber 28, and the piston 7 is subjected to Φ 35: the differential pressure of the phi 38 ring surface reduces the return acceleration (leftwards), improves the braking speed of the piston 7 during the stroke, and improves the frequency of the rock drill.

Design of leakage cavity

Referring to fig. 6 and 8, the valve 13 has an inclined hole 38 to communicate the rear end leakage chamber 37 of the piston with the general oil return cavity 20, and the cylinder 14 has a through hole 40 to communicate the front end leakage chamber 39 of the piston with the leakage ring chamber 34, and the leakage ring chamber 34 and the general oil return cavity 20 are communicated through the oil return passage 35, so that the seals of the steckel seal 18 at both ends of the piston 7 are always in a low-pressure (oil return pressure) working state, and the service life of the seals is prolonged.

The impact part and the rotary part are independently designed

The impact part of the piston 7 and the rotary part of the drill shank 8 adopt independent design, thereby being convenient for maintenance; and by replacing the front end turning part, the rock drill can be simply deformed into a hydraulic impactor.

The design without radial relative motion is shown in fig. 12, 13 and 14, the tail part of the drill bit shank 8 adopts an outer hexagonal design, the large gear 57 and the rear retaining sleeve 54 both adopt an inner hexagonal design, when the design is used in a matching way, the large gear 57 drives the drill bit shank 8 to rotate, the drill bit shank 8 drives the rear retaining sleeve 54 of the drill bit shank 8 to rotate, and the service life of parts is prolonged.

Lubrication and cooling design

Referring to fig. 25, after cooling and lubricating air is received by the lubricating air port 76 and filled with the lubricating air chamber 81, the cooling and lubricating air enters the inner cavity of the engine base 1 at the rear side of the valve 13 from the center hole of the piston, passes through the gap between the drill shank 8 and the bull gear 57, reaches the air passing channel 65 of the rear retainer 54, then sequentially passes through the through hole 63, the air passing gap one 66, the air passing gap two 67 and the air passing groove 68 on the front retainer 55 to enter the air passing ring 73, sequentially passes through the lubricating air channel 75, the air passing groove 74 and the air passing hole 71 to enter the inner air groove 72 in the nose copper sleeve 69, and then provides lubrication and cooling for the relative motion between the drill shank 8 and the bull gear 57, the rear retainer 54, the front retainer 55 and the nose copper sleeve 69, and can cool the piston 7.

Flush design

Referring to fig. 26, the front stop sleeve 55 is snapped into the nose 6, and the shank 8 passes through the front stop sleeve 55, through a plurality of U-seals 78, and then through the nose copper sleeve 69. The flushing water enters the water trough 77 inside the machine head 6 from the outside through the flushing water port 80 on the machine head 6, and because the two sides of the drill shank 8 are sealed by the U-shaped seals 78, the entering water can only enter the water outlet 79 on the drill shank 8 and is output to the outside of the rock drill. The shank 8 will move left and right, the forward position being limited by the front stop 55 and the reverse position being limited by the rear stop 54.

The hydraulic rock drill provided by the invention is subjected to comparative tests under the conditions that the impact pressures are respectively 80, 100, 120, 140 and 160bar, and various performance data in the test process are recorded, the test result is shown in fig. 27, and the graphs of the relationship between the piston displacement and the time under different impact pressures are shown in fig. 28-32.

Through comparison test results, the hydraulic rock drill provided by the invention achieves the optimal power efficiency when the impact pressure is 140bar, and the impact power is the maximum when the impact pressure is 160 bar; and noise and vibration are small.

The above description is only a preferred embodiment of the present patent, and it should be noted that, for those skilled in the art, several modifications and decorations can be made without departing from the inventive concept, and these modifications and decorations should also be regarded as the protection scope of the present patent.

Claims

1. The utility model provides a hydraulic rock drill, includes the organism that has the cavity of constituteing by frame, cylinder, midbody, gear box, gear case lid and the aircraft nose fixed and sealing connection in proper order, its characterized in that still is provided with in the organism:

the valve sleeve is sleeved on the piston positioned in the front end inner cavity of the valve and can generate axial displacement under the action of oil pressure;

the drill rod tail is horizontally and rotatably arranged in the gear box, the gear box cover and the machine head, extends out of the front end of the machine head, and acts on the drill rod tail to cause axial displacement when the piston is axially displaced forwards under the action of hydraulic oil;

2. A hydraulic rock drill according to claim 1, characterized in that the machine is adapted to perform the above-mentioned functions

3. A hydraulic rock drill according to claim 2, characterized in that the rock drill is characterized in that

4. The hydraulic rock drill according to claim 2, wherein a front sealing seat is provided in the rear end inner cavity of the intermediate body for the piston to pass through and be connected with the piston in a sealing manner, the valve and the front sealing seat in the intermediate body are connected with the piston in a sealing manner to form a sealed space for preventing hydraulic oil from leaking, and a front copper sleeve is provided in the inner cavity at the front end of the cylinder body for the piston to pass through, and is connected with the cylinder body in a sealing manner.

5. A hydraulic rock drill according to claim 4, characterized in that a piston rear end leakage chamber is provided in the valve rear end inner chamber, said piston rear end leakage chamber being in communication with the main oil return chamber through an inclined hole in the valve; and a piston front end leakage cavity is formed at the front end of the front copper sleeve, the front sealing seat and the inner cavity of the front end of the cylinder body, and the piston front end leakage cavity is communicated with the leakage ring chamber through a through hole in the cylinder body.

6. A hydraulic rock drill according to claim 4 wherein a dust ring through which the piston passes is provided at the forward end of the front seal housing and a high pressure accumulator is provided on the housing.

7. A hydraulic rock drill according to claim 2, characterized in that the transmission mechanism includes:

8. The hydraulic rock drill according to claim 7, wherein shaft seals respectively abutting against outer peripheries of both ends of the large gear are provided in the rear end inner chamber of the gear box and in the rear end inner chamber of the gear box cover, and retainer rings respectively engaging with the rear end inner chamber of the gear box and the rear end inner chamber of the gear box cover to restrain the corresponding shaft seals are provided in the rear end inner chamber of the gear box and in the rear end inner chamber of the gear box cover at the rear end of each shaft seal.

9. The hydraulic rock drill according to claim 7, wherein the rear sleeve has two symmetrical through holes, a plurality of support blocks for supporting the shank are formed around the inner surface of the rear sleeve, an air passage for lubricating air to pass through and communicate with the through holes is formed between the support blocks, and a first air passing gap is formed between the surface of the rear sleeve at the outer end of the through holes and the inner cavity of the front section of the bull gear;

a machine head copper sleeve for limiting through a check ring is arranged in an inner cavity at the front end of the machine head, the inner wall of the machine head copper sleeve is attached to the outer periphery of the drill bit shank, a drill bit shank protecting ring is arranged at the end part of the machine head at the front end of the machine head copper sleeve, a plurality of corresponding air passing holes are formed in the machine head copper sleeve, and an inner air groove communicated with the air passing holes is formed in the machine head copper sleeve;

the engine base inner cavity, the piston center hole, the lubricating air chamber, the air channel, the through hole, the air gap I, the air gap II, the air channel, the air ring, the lubricating air channel, the air hole and the inner air channel on the rear side of the valve form a lubricating and cooling channel.

10. The hydraulic rock drill according to claim 9, wherein a water trough is formed in the inner cavity of the machine head between the copper sleeve and the air passing ring, and a plurality of U-shaped seals for sealing with the drill bit shank are arranged in the inner cavity of the machine head at the front end and the rear end of the water trough;