Direct impact type hydraulic rock drill

Abstract

The utility model discloses a direct impact type hydraulic rock drill which comprises a machine body composed of a machine tail portion, a cylinder body portion, a gear box portion and a machine head portion, the machine tail portion and the cylinder body portion jointly form an impact assembly, and the gear box portion comprises a rotation assembly. A first cavity for accommodating an impact piston is formed in the impact assembly; the rotary assembly and the machine head part jointly form a second cavity for accommodating the bit shank, and the first cavity is communicated with the second cavity; the impact piston is provided with a center hole. The bit shank is provided with a flushing cavity. One end of the water needle is fixed to the machine tail part, a pipe body of the water needle penetrates through a center hole of the impact piston, extends into the bit shank and is communicated with the flushing cavity, a water inlet cavity isolated from the first cavity is formed in the machine tail part, and the water inlet cavity is communicated with the water needle; and a water inlet communicated with the water inlet cavity is formed in the machine tail part and used for introducing flushing water into the water inlet cavity and the water needle so as to cool the impact piston and the bit shank and flush the bit shank.

Description

Technical Field

[0001] The utility model relates to a straight-throw hydraulic rock drill, belonging to the technical field of rock drills. Background Art

[0002] The flushing assembly of existing hydraulic rock drills is typically integrated into the drill head. This flushing assembly flushes residual material from the flushing chamber at the front end of the drill bit by introducing flushing water. However, existing rock drill structures require multiple water seals at the drill bit. These are vulnerable parts with a short service life and are difficult to replace. Furthermore, if a leak occurs, water can seep through the gaps between the flushing assembly components, affecting the rock drill's operation and potentially causing rust and corrosion in other components. Utility Model Content

[0003] The purpose of the utility model is to provide a direct-impulse hydraulic rock drill, which leads the water needle directly from the tail of the machine to the drill tail. The water seal is easy to install, uses a small number of water seals and can effectively prevent water leakage. It can also cool the machine body while achieving flushing.

[0004] In order to achieve the above-mentioned purpose, the technical solution adopted by the present utility model is:

[0005] A direct impact hydraulic rock drill includes a body consisting of a tail portion, a cylinder portion, a gear box portion, and a head portion, wherein the tail portion and the cylinder portion together constitute an impact assembly, and the gear box portion includes a rotary assembly;

[0006] The impact assembly forms a first chamber for accommodating the impact piston; the rotary assembly and the head of the machine jointly form a second chamber for accommodating the shank, and the first chamber is connected to the second chamber;

[0007] The impact assembly introduces hydraulic oil into the first chamber. The impact piston can reciprocate along the central axis of the first chamber under the push of the hydraulic oil, and the head of the impact piston can pass through the first chamber into the second chamber and impact the tail of the shank.

[0008] The shank adaptor is linearly displaced along the central axis of the second chamber after being struck by the impact piston, and is driven by the rotary assembly to rotate in a positive or reverse direction along the central axis of the second chamber;

[0009] The impact piston has a center hole, and the shank has a flushing cavity; a water needle is provided in the machine body, one end of which is fixed at the tail of the machine, and the tube body passes through the center hole of the impact piston and extends into the shank and is connected with the flushing cavity. A water inlet cavity isolated from the first chamber is formed at the tail of the machine, and the water inlet cavity is connected with the water needle; a water inlet connected with the water inlet cavity is opened at the tail of the machine, which is used to pass flushing water into the water inlet cavity and the water needle to cool the impact piston and the shank, and to flush the shank.

[0010] Preferably, the tail portion includes a base, the cylinder portion includes a cylinder, the gear box portion includes a gear box and a gear box cover, and the head portion includes a head;

[0011] The tail of the cylinder body is embedded in the front inner cavity of the machine base, the tail of the gear box is embedded in the front inner cavity of the cylinder body, the gear box cover is installed on the head of the gear box, and the tail of the machine head is embedded in the front inner cavity of the gear box cover;

[0012] The impact assembly includes a valve sleeve, a valve body, a cylinder sleeve and an impact piston;

[0013] The valve sleeve is embedded in the machine base, with its head embedded in the rear end inner cavity of the cylinder body; the valve body is installed in the front end inner cavity of the valve sleeve; the cylinder sleeve is arranged in the cylinder body, with its tail abutting against the head of the valve sleeve, and its head abutting against the inner wall of the cylinder body; the inner cavity of the valve sleeve is connected to the inner cavity of the cylinder sleeve; the impact piston is installed in the inner cavity of the valve sleeve and the cylinder sleeve;

[0014] An annular rear high-pressure oil chamber and a rear total oil return chamber are sequentially formed along the radial direction between the engine base and the valve sleeve, and between the engine base, the valve sleeve and the tail of the cylinder body.

[0015] A rear end oil return cavity is formed between the inner cavity of the valve sleeve and the inner cavity of the cylinder sleeve and the valve body;

[0016] The cylinder liner is radially formed with an annular middle oil return chamber, a front oil return chamber and a front high-pressure oil chamber in sequence from the rear to the front, and is isolated by an impact piston. The middle oil return chamber, the rear oil return chamber and the rear main oil return chamber are connected;

[0017] The valve sleeve is provided with a plurality of high-pressure oil channels for connecting the rear high-pressure oil chamber with the inner cavity of the valve sleeve;

[0018] The valve body closes the high-pressure oil channel. After the hydraulic oil is injected into the rear high-pressure oil chamber, it pushes the valve body to move axially forward to open the high-pressure oil channel. The rear high-pressure oil chamber is connected to the inner cavity of the valve sleeve. The hydraulic oil enters the inner cavity of the valve sleeve and pushes the impact piston to move axially forward.

[0019] When the impact piston moves forward a preset distance, the front high-pressure oil chamber is connected to the front oil return chamber, and the hydraulic oil pushes the valve body to move axially backward to close the high-pressure oil channel. The impact piston completes the impact under the action of the hydraulic oil and retreats backward;

[0020] When the impact piston retreats a preset distance, the front oil return chamber is connected with the middle oil return chamber, the rear oil return chamber, and the rear total oil return chamber; the high-pressure oil injected into the rear high-pressure oil chamber pushes the valve body to move axially forward to open the high-pressure oil channel so that the rear high-pressure oil chamber is connected with the inner cavity of the valve sleeve, and the hydraulic oil enters the inner cavity of the valve sleeve and pushes the impact piston to move axially forward, and the cycle repeats.

[0021] Preferably, a plurality of back-thrust channels connected to the high-pressure oil channel and the rear end oil return chamber are distributed axially and circumferentially in the head portion of the valve sleeve;

[0022] A plurality of forward thrust passages are distributed axially and circumferentially in the rear end of the cylinder liner, communicating with the rear end oil return chamber and the front end oil return chamber;

[0023] A rear push rod and a front push rod are respectively slidably arranged in the rear push channel and the front push channel for pushing the valve body axial displacement under the action of hydraulic oil, wherein the diameter of the front push rod is larger than that of the rear push rod;

[0024] An accumulator is installed on the side of the engine base, and the liquid side of the accumulator is connected to the rear high-pressure oil chamber; and an oil inlet channel for connecting the rear high-pressure oil chamber and the front high-pressure oil chamber is formed on the valve body and the cylinder sleeve;

[0025] An oil inlet communicated with the rear high-pressure oil chamber and an oil outlet communicated with the rear total return oil chamber are provided on the side of the machine base.

[0026] Preferably, a plurality of step seals are embedded in the rear end inner cavity of the valve sleeve for preventing the hydraulic oil from leaking to the rear end, and a sealing assembly is embedded in the inner cavity where the cylinder sleeve and the cylinder body abut against each other for preventing the hydraulic oil from leaking to the front end;

[0027] An annular rear end leakage oil chamber is formed in the rear end inner cavity of the valve sleeve located at the front end of the step seal; a front end leakage oil chamber is formed between the sealing assembly and the cylinder sleeve;

[0028] The front leakage oil chamber is connected to the rear total oil return chamber; the rear leakage oil chamber is connected to the middle oil return chamber, and is connected to the rear total oil return chamber through the middle oil return chamber and the rear oil return chamber.

[0029] Preferably, the rotary assembly includes a cycloid motor, a pinion gear and a gear;

[0030] The pinion is arranged in the upper cavity of the gear box, and needle bearings are arranged on the outer sides of both ends of the pinion. The pinion rotates relative to the upper cavity of the gear box through the needle bearings.

[0031] The large gear is clamped in the gear box and meshes with the small gear. Conical bearings are provided on the outside of both ends of the large gear. The large gear rotates relative to the gear box through the conical bearings.

[0032] The tail of the shank is inserted into the large gear and has a clearance fit with the large gear without any rotation;

[0033] The cycloid motor is installed outside the upper cavity of the gearbox, and the actuator shaft is inserted into the pinion and meshes with the pinion to drive the pinion to rotate forward or reverse, thereby driving the large gear and the shank to rotate synchronously.

[0034] Preferably, the rotary assembly further comprises a triangular sleeve and a rear stop sleeve;

[0035] The triangular sleeve is embedded in the front end inner cavity of the large gear, and the drill tail is inserted through the triangular sleeve. Teeth are formed around the drill tail along the length direction, and tooth grooves are formed in the inner cavity of the triangular sleeve. The drill tail is engaged with the tooth grooves of the triangular sleeve to achieve non-rotational and clearance fit.

[0036] The rear stop sleeve is arranged in the inner cavity of the large gear at the rear end of the triangular sleeve to limit the axial displacement distance of the shank backward; the inner cavity of the head is formed with an inner convex ring to limit the axial displacement distance of the shank forward.

[0037] Preferably, a lubricating oil chamber is formed between the large gear and the small gear;

[0038] A shaft seal is provided in the rear end inner cavity of the gearbox and the rear end inner cavity of the gearbox cover, which is in contact with the outer peripheral body of the corresponding end of the large gear and is used to prevent the lubricating oil in the lubricating oil cavity from leaking. A retaining ring is also embedded in the rear end inner cavity of the gearbox and the rear end inner cavity of the gearbox cover at the rear end of the shaft seal to prevent the displacement of the shaft seal.

[0039] A sealing sleeve is provided outside the tapered bearing located outside the large gear head, which is in contact with and sealed against the inner wall of the gear box and the gear box cover to prevent leakage of lubricating oil in the lubricating oil cavity.

[0040] Preferably, a plug is provided at the tail of the machine, the tail of the water needle is inserted into the plug, and the tail of the water needle extends outward to form an anti-slip ring;

[0041] An anti-slip part is provided in the plug, which is sleeved outside the water needle and abuts against the anti-slip ring;

[0042] Water seals are provided in the tail of the machine and in the inner cavity of the shank, through which water supply needles are inserted, respectively, to prevent flushing water from leaking into the impact assembly and the rotary assembly;

[0043] A water supply needle is also provided in the shank, through which a star-shaped ring for supporting the water needle is inserted;

[0044] A water inlet hole for connecting the water inlet cavity and the water needle is provided on the water needle located in the water inlet cavity outside the anti-slip component.

[0045] Preferably, a copper sleeve for the shank to pass through is embedded in the front end cavity of the handpiece, and a retaining ring for preventing the copper sleeve from falling off is embedded in the head cavity of the handpiece.

[0046] Preferably, an air intake cavity is further formed in the tail, the valve body closes the air intake cavity, and the air intake cavity is connected to the abutment surface between the accumulator and the tail;

[0047] An air chamber is formed between the head of the cylinder body and the tail of the gear box. A plurality of air passages are correspondingly provided on the tail and the cylinder body to connect the air intake cavity and the air chamber. The air passages are respectively connected to the abutment surface between the tail and the cylinder body, and the abutment surface between the cylinder body and the gear box.

[0048] The air chamber is connected to the outside atmosphere through the gap between the impact piston and the shank and the large gear, as well as the gap between the shank and the copper sleeve and the front gear.

[0049] An air inlet connected to the air inlet chamber is provided on the tail of the machine for introducing gas into the air inlet chamber. The introduced gas is blown out through the abutting surfaces of the air inlet chamber, the accumulator and the tail of the machine, the abutting surfaces of the tail of the machine and the cylinder body, the abutting surfaces of the cylinder body and the gear box, the gap between the impact piston and the shank and the large gear, and the gap between the shank and the copper sleeve.

[0050] The beneficial effects of the present invention are:

[0051] 1. The rock drill is shorter in overall length and lighter in weight, achieving a "convenient" effect. It also features a simple structure, fewer components, a simple design, and reduced processing difficulty. The shorter overall length brings the following advantages: shorter impact piston stroke—faster impact reciprocating time; higher impact frequency—greater rock drill power and less impact energy loss; and lower impact energy—less damage to the impact piston and drill adapter.

[0052] 2. Improved flushing structure: Flushing water is directly connected to the drill tail, reducing the number of "water seals" in the original structure that are easily damaged, solving the problem of "short life and difficult replacement" of water seals, and preventing other parts from rusting and being scrapped due to leakage of flushing water. At the same time, the structure in which the water needle is installed inside the impact piston and the drill tail can better limit the radial displacement of the impact piston and the drill tail, thereby extending the working life of the impact piston and the drill tail. The flushing water can also better remove the heat of the impact piston during operation, reduce the working temperature, and better improve the service life of the impact piston.

[0053] 3. New oil seal design: adopts "shaft seal (rubber material) + retaining ring" instead of the original "spring (iron) + retaining ring" structure. When the retaining ring is damaged and causes the shaft seal to fall off, the iron material will not cause squeezing damage to other parts;

[0054] 4. The star-shaped ring set in the shank can also play a sealing and supporting role, which can better support the water needle and limit the radial displacement of the water needle. BRIEF DESCRIPTION OF THE DRAWINGS

[0055] Figure 1 It is a perspective view of a hydraulic rock drill;

[0056] Figure 2 This is a three-dimensional image of a hydraulic rock drill from another perspective;

[0057] Figure 3 is a cross-sectional view of a hydraulic rock drill;

[0058] Figure 4 A cross-sectional view of the hydraulic rock drill from another perspective;

[0059] Figure 5 It is a structural diagram of the valve sleeve;

[0060] Figure 6 It is a cross-sectional view of the valve sleeve;

[0061] Figure 7 This is a cross-sectional view of the cylinder liner from one perspective;

[0062] Figure 8 It is a cross-sectional view of the cylinder liner from another perspective;

[0063] Figure 9 This is a cross-sectional view of the cylinder liner from the third perspective;

[0064] Figure 10 It is a structural diagram of the impact piston and cylinder body;

[0065] Figure 11 It is a structural diagram of the drill tail and the triangular sleeve.

[0066] The main reference numerals in the figures have the following meanings:

[0067] 1. Machine base, 2. Cylinder body, 3. Gearbox, 4. Gearbox cover, 5. Machine head, 6. Dowel pin, 7. Long screw assembly, 8. Short screw assembly, 9. Bolt, 10. Impact piston, 11. Boring tail, 12. Center hole, 13. Flushing chamber, 14. Water needle, 15. Water inlet chamber, 16. Water inlet, 17. Valve sleeve, 18. Valve body, 19. Cylinder sleeve, 20. Piston guide sleeve, 21. Seal guide sleeve, 22. Step seal, 23. Oil seal , 24, rear end high pressure oil chamber, 25, rear end total return oil chamber, 26, oil inlet, 27, oil outlet, 28, high pressure oil channel, 29, rear thrust channel, 30, rear end return oil chamber, 31, middle return oil chamber, 32, front end return oil chamber, 33, front end high pressure oil chamber, 34, channel one, 35, channel two, 36, channel three, 37, transition oil chamber, 38, oil hole, 39, accumulator, 40, oil passage, 41, forward thrust channel, 42 , rear end leakage oil chamber, 43, inclined hole, 44, through hole, 45, rear push rod, 46, front push rod, 47, rear stage, 48, front stage, 49, force surface A, 50, force surface C, 51, section B, 52, force surface B, 53, inner stage D, 54, inner stage E, 55, cycloid motor, 56, small gear, 57, large gear, 58, needle roller bearing, 59, tapered bearing, 60, triangular sleeve, 61, rear Snap sleeve, 62, teeth, 63, tooth grooves, 64, inner convex ring, 65, lubricating oil chamber, 66, lubricating oil injection plug, 67, shaft seal, 68, snap ring, 69, sealing sleeve, 70, plug, 71, anti-slip ring, 72, anti-slip part, 73, water seal, 74, water inlet hole, 75, copper sleeve, 76, snap ring, 77, front end leakage oil chamber, 78, air intake chamber, 79, air chamber, 80, air passage, 81, air inlet, 82, star ring. DETAILED DESCRIPTION

[0068] The present invention will be described in detail below with reference to the accompanying drawings and embodiments.

[0069] This embodiment provides a direct-thrust hydraulic rock drill. Figure 1-11 As shown, it includes a body consisting of a tail portion, a cylinder portion, a gear box portion and a head portion. Specifically, it is a body consisting of a base 1, a cylinder body 2, a gear box 3, a gear box cover 4 and a head 5 connected in sequence. Among them, the tail of the cylinder body 2 is embedded in the front end inner cavity of the base 1, the tail of the gear box 3 is embedded in the front end inner cavity of the cylinder body 2, the gear box cover 4 is installed on the head of the gear box 3, and the tail of the head 5 is embedded in the front end inner cavity of the gear box cover 4. The base 1, the cylinder body 2 and the gear box 3 are positioned at the abutting ends by a plurality of locating pins 6 and are assembled into one by four long screw assemblies 7. The gear box 3 and the gear box cover 4 are assembled into one by four short screw assemblies 8. The head 5 is mounted to the gear box cover 4 by a plurality of bolts 9.

[0070] The tail section and the cylinder section together form an impact assembly, and the gearbox section includes a rotary assembly. The impact assembly forms a first chamber for accommodating an impact piston 10. The rotary assembly and the head section together form a second chamber for accommodating a shank 11, and the first chamber is connected to the second chamber. The impact assembly introduces hydraulic oil into the first chamber, and the impact piston 10 can reciprocate along the central axis of the first chamber under the push of the hydraulic oil, and the head of the impact piston 10 can pass through the first chamber into the second chamber and impact the tail of the shank 11. After being impacted by the impact piston 10, the shank 11 displaces linearly along the central axis of the second chamber and rotates forward or reversely along the central axis of the second chamber under the drive of the rotary assembly.

[0071] The impact piston 10 has a center hole 12, and the shank 11 has a flushing chamber 13; a water needle 14 is provided in the machine body, one end of which is fixed to the tail of the machine, and the tube body passes through the center hole 12 of the impact piston 10 and extends into the shank 11 and is connected to the flushing chamber 13. A water inlet chamber 15 isolated from the first chamber is formed at the tail of the machine, and the water inlet chamber 15 is connected to the water needle 14; a water inlet 16 connected to the water inlet chamber 15 is opened at the tail of the machine, which is used to pass flushing water into the water inlet chamber 15 and the water needle 14 to cool the impact piston 10 and the shank 11, and to flush the shank 11.

[0072] Specifically, the impact assembly includes a valve sleeve 17, a valve body 18, a cylinder sleeve 19 and an impact piston 10; the valve sleeve 17 is embedded in the machine base 1, and the head is embedded in the rear end inner cavity of the cylinder body 2; the valve body 18 is installed in the front end inner cavity of the valve sleeve 17; the cylinder sleeve 19 is arranged in the cylinder body 2 and the tail is abutted against the head of the valve sleeve 17 and is also positioned by the locating pin 6, and the head is abutted against the inner step surface on the rear side of the head cavity of the cylinder body 2; the inner cavity of the valve sleeve 17 is connected to the inner cavity of the cylinder sleeve 19.

[0073] To prevent leakage of the hydraulic oil driving the reciprocating motion of the impact piston 10, a restricted area is formed between the front end of the cylinder liner 19 and the inner step on the front side of the cylinder body 2. A piston guide sleeve 20 is embedded in the front end of the cylinder liner 19, and a sealing guide sleeve 21 is embedded in the inner step on the front side of the cylinder body 2. The tail end of the sealing guide sleeve 21 is embedded in the front end of the cylinder liner 19 and abuts against the piston guide sleeve 20 and the sealing guide sleeve 21. The impact piston 10 is mounted within the valve sleeve 17 and the inner cavities of the cylinder liner 19, passing through the piston guide sleeve 20 and the sealing guide sleeve 21. Step seals 22 are installed in the two grooves at the rear end of the valve body 18 and in the two grooves of the sealing guide sleeve 21 to prevent hydraulic oil leakage. Furthermore, an oil seal 23, through which the impact piston 10 passes, is embedded at the front end of the sealing guide sleeve 21 to further prevent hydraulic oil leakage.

[0074] An annular rear high-pressure oil chamber 24 and a rear total return oil chamber 25 are radially formed between the engine base 1 and the valve sleeve 17, and between the engine base 1, the valve sleeve 17, and the tail of the cylinder body 2. An oil inlet 26 communicating with the rear high-pressure oil chamber 24 and an oil outlet 27 communicating with the rear total return oil chamber 25 are provided on one side of the engine base 1. In actual use, oil inlet and return oil blocks (conventional components in this field) are installed at the oil inlets and outlets to facilitate oil pipe installation. Multiple high-pressure oil passages 28 are provided on the valve sleeve 17 for connecting the rear high-pressure oil chamber 24 with the inner cavity of the valve sleeve 17. Four rearward thrust passages 29 are provided at the head of the valve sleeve 17, and the four rearward thrust passages 29 are correspondingly connected to four of the high-pressure oil passages 28.

[0075] A rear oil return chamber 30 is formed between the inner cavities of the valve sleeve 17 and the inner cavities of the cylinder sleeve 19, and the valve body 18. An annular intermediate oil return chamber 31, a front oil return chamber 32, and a front high-pressure oil chamber 33 are radially formed in order from rear to front within the cylinder sleeve 19, separated by the impact piston 10. The intermediate oil return chamber 31 communicates with the rear oil return chamber 30 via a first port 34 within the cylinder sleeve 19, and communicates with the rear main oil return chamber 25 via a second port 35 within the valve sleeve 17, which communicates with port 1 34, and a third port 36 connected to port 2 35.

[0076] A transition oil chamber 37 is formed between the cylinder liner 19 and the cylinder body 2. An oil hole 38 is provided in the cylinder liner 19, connecting the transition oil chamber 37 with the front high-pressure oil chamber 33. An accumulator 39 is installed on one side of the base 1 (with a nitrogen charging connector on the outside for easy replacement. If damaged, the nitrogen charging connector can be replaced by construction personnel without delaying work). The rear high-pressure oil chamber 24 is connected to the liquid side of the accumulator 39. The accumulator 39, a common structure in existing rock drills, serves as a liquid compensation device, eliminating pulsation, reducing noise, absorbing hydraulic shock, and acting as a hydraulic air spring. Oil passages 40 are also provided in the base 1 and cylinder body 2, connecting the rear high-pressure oil chamber 24 with the transition oil chamber 37. The rear end of the cylinder body 2 is provided with multiple forward thrust passages 41, each corresponding to the rear thrust passages 29 and connected to the front oil return chamber 32.

[0077] An annular rear end leakage oil chamber 42 is formed between the valve sleeve 17 located on the front side of the step seal 22 and the impact piston 10. The rear end leakage oil chamber 42 is connected to the rear end total return oil chamber 25 through an inclined hole 43 on the valve sleeve 17; a front end leakage oil chamber 77 is formed between the piston guide sleeve 20, the sealing guide sleeve 21 and the inner cavity of the cylinder sleeve 19. The front end leakage oil chamber 77 is connected to the middle return oil chamber 31 through a through hole 44 opened on the cylinder sleeve 19.

[0078] A rear push rod 45 and a front push rod 46 are respectively embedded in each rear push channel 29 and each front push channel 41. The diameter of the front push rod 46 is larger than the diameter of the rear push rod 45, and the rear push rod 45 and the front push rod 46 can move freely in the corresponding rear push channel 29 and the front push channel 41 (clearance fit); the valve body 18 is installed in the front end inner cavity of the valve sleeve 17 and can move freely in the front end inner cavity of the valve sleeve 17 (clearance fit). In the initial state, the rear end of the valve body 18 abuts against the front end inner cavity of the valve sleeve 17, closing the inner end of the high-pressure oil channel 28, and the front end of the valve body 18 and the rear end of the cylinder sleeve 19 have a gap connecting the inner cavity of the valve body 18 and the rear end oil return cavity 30; an annular protrusion is formed on the outer periphery of the front end of the valve body 18, the rear push rod 45 abuts against the rear end surface of the protrusion, and the front push rod 46 abuts against the front end surface of the protrusion. Under the action of hydraulic oil, the valve body 18 can be axially displaced relative to the impact piston 10 in the space formed by the front end inner cavity of the valve sleeve 17 and the rear end inner cavity of the cylinder sleeve 19.

[0079] The impact piston 10 has a rear stage 47 and a front stage 48. The rear end of the rear stage 47 forms a force-bearing surface A49, and the front end forms a force-bearing surface C50. The rear end of the front stage 48 forms a cross-section B51, and the front end forms a force-bearing surface B52. The force-bearing area of the force-bearing surface A49 is greater than the force-bearing areas of the force-bearing surfaces C50 and B52. Furthermore, the rear stage 47 of the impact piston 10 is axially displaceable within the front end inner cavity of the valve body 18 and the rear end inner cavity of the cylinder liner 19. The cylinder liner 19 has an inner step D53 for separating the front return oil chamber 32 from the front high-pressure oil chamber 33, and an inner step E54 for separating the front high-pressure oil chamber 33 from the front end inner cavity of the cylinder liner 19. The front stage 48 of the impact piston 10 is axially displaceable within the inner step D53, the front high-pressure oil chamber 33, and the inner step E54 of the cylinder liner 19.

[0080] The shank tail 11 is horizontally and rotatably arranged in the gear box 3, the gear box cover 4 and the machine head 5. A certain distance is left between the rear end of the shank tail 11 and the front end of the impact piston 10 for a predetermined distance to be struck. When the impact piston 10 is axially displaced forward by the hydraulic oil, it acts on the shank tail 11 to cause axial displacement.

[0081] The rotary assembly includes a cycloidal motor 55, a pinion 56, and a large gear 57. The pinion 56 is located in the upper cavity of the gearbox 3 and is rotatably connected to the upper cavity of the gearbox 3 via needle bearings 58 disposed on the outer sides of both ends. The large gear 57 is clamped in the lower cavity of the gearbox 3 and meshes with the pinion 56. It is arranged to rotate relative to the gearbox 3 via tapered bearings 59 disposed on the outer sides of both ends. The shank adapter 11 is inserted through the large gear 57 and has a non-rotating and clearance fit with the large gear 57. The cycloidal motor 55 is installed outside the upper cavity of the gearbox 3, and the actuator shaft is inserted into the pinion 56 and meshes with the pinion 56. It is used to drive the pinion 56 to rotate in the forward or reverse direction, thereby driving the large gear 57 and the shank adapter 11 to rotate synchronously.

[0082] The rotary assembly also includes a triangular sleeve 60 and a rear stop sleeve 61; the triangular sleeve 60 is embedded in the front end inner cavity of the large gear 57, the drill tail 11 is inserted through the triangular sleeve 60, and meshing teeth and groove structures are formed on the inner cavity of the triangular sleeve 60 and the drill tail 11; in this embodiment, a tooth 62 structure is formed on the drill tail 11, and a tooth groove 63 structure is formed in the inner cavity of the triangular sleeve 60, and the two are non-rotating and clearance-fitted through the meshing of the teeth 62 and the tooth groove 63, that is, relative rotation cannot occur between the large gear 57 and the drill tail 11.

[0083] The rear stop sleeve 61 is arranged in the inner cavity of the large gear 57 at the rear end of the triangular sleeve 60 to limit the rearward axial displacement distance of the shank 11; the inner cavity of the head 5 is formed with an inner convex ring 64 to limit the forward axial displacement distance of the shank 11.

[0084] The head of the large gear 57 extends into the gearbox cover 4, forming a lubricating oil chamber 65 between the large gear 57 and the small gear 56. A lubricating oil filling plug 66 is provided on the gearbox 3. A shaft seal 67 (made of rubber) is provided in the rear end inner cavity of the gearbox 3 and the rear end inner cavity of the gearbox cover 4. It abuts the outer circumference of the corresponding end of the large gear 57 to prevent lubricating oil leakage from the lubricating oil chamber 65. A retaining ring 68 is embedded in the rear end inner cavity of the gearbox 3 and the rear end inner cavity of the gearbox cover 4, located behind the shaft seal 67, to prevent displacement of the shaft seal 67. A sealing sleeve 69 is also provided outside the tapered bearing 59 located outside the head of the large gear 57. It abuts and seals against the inner walls of the gearbox 3 and the gearbox cover 4 to prevent lubricating oil leakage from the lubricating oil chamber 65.

[0085] A plug 70 is provided on the machine base 1, and the tail of the water needle 14 is inserted into the plug 70. The tail of the water needle 14 extends outward to form an anti-slip ring 71. An anti-slip part 72 is provided in the plug 70. The anti-slip part 72 is sleeved on the outside of the water needle 14 and abuts against the anti-slip ring 71. Water seals 73 for preventing flushing water from leaking into the impact assembly and the rotary assembly are provided in the machine base 1 and the inner cavity of the shank 11, through which the water needle 14 passes. At the same time, a star-shaped ring 82 for supporting the water needle is also provided in the shank to better support the water needle and limit the radial displacement of the water needle. A water inlet hole 74 for connecting the water inlet cavity 15 with the water needle 14 is provided on the water needle 14 located in the water inlet cavity 15 outside the anti-slip part 72.

[0086] Flushing water is introduced into the water inlet chamber 15 through the water inlet 16, and the flushing water enters the water needle 14 through the water inlet hole 74 and finally flows out through the flushing chamber 13 of the shank 11. During the flushing process, the flushing water can also take away the heat of some components in the body, cool these components, and thus extend their service life.

[0087] A copper sleeve 75 for the drill tail 11 to pass through is embedded in the front cavity of the machine head 5, and a retaining ring 76 is embedded in the head cavity of the machine head 5 to prevent the copper sleeve 75 from falling off. An air intake chamber 78 is also formed in the machine base 1. The air intake chamber 78 is located at the end of the first chamber. The valve body 18 closes the air intake chamber 78, and the air intake chamber 78 is connected to the abutment surface of the accumulator 39 and the machine base 1; an air chamber 79 is formed between the head of the cylinder body 2 and the tail of the gear box 3, and a plurality of air passages 80 for connecting the air intake chamber 78 and the air chamber 79 are correspondingly opened on the machine base 1 and the cylinder body 2; and the air passages 80 are respectively connected to the abutment surface between the machine base 1 and the cylinder body 2, and the abutment surface between the cylinder body 2 and the gear box 3; the air chamber 79 is formed by impact The gaps between the piston 10, the shank 11 and the large gear 57, and the gap between the shank 11 and the copper sleeve 75 are connected to the external atmosphere. An air inlet 81 connected to the air inlet chamber 78 is provided on the machine base 1 for introducing gas into the air inlet chamber 78. The introduced gas is blown out through the abutting surfaces between the air inlet chamber 78, the accumulator 39 and the machine base 1, the abutting surfaces between the machine base 1 and the cylinder body 2, the abutting surfaces between the cylinder body 2 and the gear box 3, and the gaps between the piston 10, the shank 11 and the large gear 57, and the gap between the shank 11 and the copper sleeve 75.

[0088] The following further describes the movement process of the impact piston 10. The direction of movement toward the machine head 5 is taken as the displacement direction toward the front end, and the direction of movement toward the machine base 1 is taken as the displacement direction toward the rear end.

[0089] Stroke, reversing

[0090] Phase 1: High-pressure hydraulic oil enters the rear high-pressure oil chamber 24 through the oil inlet 26 on the machine base 1 and then enters the high-pressure oil channel 28. At this point, the valve body 18 seals the inner end of the high-pressure oil channel 28, and the high-pressure oil enters the left end chamber of the rear thrust channel 29, which is connected to the high-pressure oil channel 28. Since the forward thrust channel 41 is connected to the front oil return chamber 32, the middle oil return chamber 31, and the rear total oil return chamber 25 and is connected to the oil outlet 27 on the machine base 1, there is no high-pressure oil in the right end chamber of the forward thrust channel 41.

[0091] Second stage: High-pressure oil continuously flows into the left end chamber of the rearward thrust passage 29, pushing the rearward thrust rod 45 to displace axially forward, which in turn pushes the valve body 18 to displace axially forward. After the valve body 18 displaces forward, it abuts against the rear end of the cylinder sleeve 19, closing the gap between the front end of the valve body 18 and the rear end of the cylinder sleeve 19, which originally connected the inner cavity of the valve body 18 and the rear end oil return chamber 30. At this point, the high-pressure oil passage 28 is connected to the inner cavity of the front end of the valve sleeve 17, allowing high-pressure oil to enter the inner cavity of the front end of the valve sleeve 17. Since the force-bearing area of the force-bearing surface A49 is greater than the force-bearing area of the force-bearing surface B52, the impact piston 10 is pushed axially forward.

[0092] The third stage: During the forward movement of the impact piston 10, when the section B51 passes the front end surface of the inner platform stage D53, the high-pressure oil in the front high-pressure oil chamber 33 enters the front return oil chamber 32 and enters the right end chamber of the forward push channel 41. Since the diameter of the front push rod 46 is greater than the diameter of the rear push rod 45, under the condition of equal pressure, the front push rod 46 will push the valve body 18 to move toward the rear end until the valve body 18 closes the inner end of the high-pressure oil channel 28 again. At this time, the gap between the front end of the valve body 18 and the rear end of the cylinder liner 19 that originally connected the inner cavity of the valve body 18 and the rear end oil return cavity 30 is restored, so that the hydraulic oil located in the inner cavity of the valve body 18 can enter the rear end oil return cavity 30 through the gap, and then the force surface A49 is pressure-free, and the force surface C50 is affected by the high-pressure oil that enters the front end oil return cavity 32 through the front end high-pressure oil cavity 33, passes through the gap between the impact piston 10 and the cylinder liner 19, and acts on the force surface C50, so that the impact piston 10 slows down until it hits the shank tail 11 and changes direction. After being hit, the shank tail 11 will move toward the front end to impact the target object.

[0093] Return, reversing

[0094] The first stage: After the impact piston 10 is reversed, since only the force surface C50 is affected by the oil pressure, the impact piston 10 accelerates to the rear end. During the movement of the impact piston 10 to the rear end, when the cross section B51 passes the front end surface of the inner stage D53, only the force surface B52 is affected by the oil pressure. Since the area of the force surface B52 is smaller than the area of the force surface A49, the acceleration of the return movement of the impact piston 10 decreases at this time.

[0095] The second stage: as the impact piston 10 continues to move toward the rear end, when the force surface C50 passes over the front end surface of the intermediate oil return chamber 31, the high-pressure oil originally in the right end chamber of the forward thrust channel 41 enters the intermediate oil return chamber 31, reducing the force acting toward the rear end on the front thrust rod 46; and since high-pressure oil always enters the left end chamber of the backward thrust channel 29, it will push the valve body 18 toward the front end. Therefore, at this time, the valve body 18 moves toward the front end. When it reaches a certain position, a closed space filled with hydraulic oil will be formed by the impact piston 10, the valve sleeve 17, the valve body 18, and the cylinder sleeve 19, causing the impact piston 10 to brake.

[0096] When the valve body 18 continues to move forward, the inner end of the high-pressure oil channel 28 is opened, and the high-pressure oil enters the inner cavity of the valve body 18, acting on the force surface A49, causing the impact piston 10 to reverse and start a new round of stroke movement.

[0097] The above is only a preferred embodiment of the present utility model patent. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present utility model patent. These improvements and modifications should also be regarded as the scope of protection of the present utility model patent.

Claims

1. A direct impact hydraulic rock drill, characterized in that: The machine body comprises a tail portion, a cylinder portion, a gear box portion and a head portion, wherein the tail portion and the cylinder portion together constitute an impact assembly, and the gear box portion includes a rotary assembly; The impact assembly forms a first chamber for accommodating the impact piston; the rotary assembly and the head of the machine jointly form a second chamber for accommodating the shank, and the first chamber is connected to the second chamber; The impact assembly introduces hydraulic oil into the first chamber. The impact piston can reciprocate along the central axis of the first chamber under the push of the hydraulic oil, and the head of the impact piston can pass through the first chamber into the second chamber and impact the tail of the shank. The shank adaptor is linearly displaced along the central axis of the second chamber after being struck by the impact piston, and is driven by the rotary assembly to rotate in a positive or reverse direction along the central axis of the second chamber; The impact piston has a center hole, and the shank has a flushing cavity; a water needle is provided in the machine body, one end of which is fixed at the tail of the machine, and the tube body passes through the center hole of the impact piston and extends into the shank and is connected with the flushing cavity. A water inlet cavity isolated from the first chamber is formed at the tail of the machine, and the water inlet cavity is connected with the water needle; a water inlet connected with the water inlet cavity is opened at the tail of the machine, which is used to pass flushing water into the water inlet cavity and the water needle to cool the impact piston and the shank, and to flush the shank.

2. A direct impact hydraulic rock drill according to claim 1, characterized in that: The tail portion includes a base, the cylinder portion includes a cylinder, the gear box portion includes a gear box and a gear box cover, and the head portion includes a head; The tail of the cylinder body is embedded in the front inner cavity of the machine base, the tail of the gear box is embedded in the front inner cavity of the cylinder body, the gear box cover is installed on the head of the gear box, and the tail of the machine head is embedded in the front inner cavity of the gear box cover; The impact assembly includes a valve sleeve, a valve body, a cylinder sleeve and an impact piston; The valve sleeve is embedded in the machine base, with its head embedded in the rear end inner cavity of the cylinder body; the valve body is installed in the front end inner cavity of the valve sleeve; the cylinder sleeve is arranged in the cylinder body, with its tail abutting against the head of the valve sleeve, and its head abutting against the inner wall of the cylinder body; the inner cavity of the valve sleeve is connected to the inner cavity of the cylinder sleeve; the impact piston is installed in the inner cavity of the valve sleeve and the cylinder sleeve; An annular rear high-pressure oil chamber and a rear total oil return chamber are sequentially formed along the radial direction between the engine base and the valve sleeve, and between the engine base, the valve sleeve and the tail of the cylinder body. A rear end oil return cavity is formed between the inner cavity of the valve sleeve and the inner cavity of the cylinder sleeve and the valve body; The cylinder liner is radially formed with an annular middle oil return chamber, a front oil return chamber and a front high-pressure oil chamber in sequence from the rear to the front, and is isolated by an impact piston. The middle oil return chamber, the rear oil return chamber and the rear main oil return chamber are connected; The valve sleeve is provided with a plurality of high-pressure oil channels for connecting the rear high-pressure oil chamber with the inner cavity of the valve sleeve; The valve body closes the high-pressure oil channel. After the hydraulic oil is injected into the rear high-pressure oil chamber, it pushes the valve body to move axially forward to open the high-pressure oil channel. The rear high-pressure oil chamber is connected to the inner cavity of the valve sleeve. The hydraulic oil enters the inner cavity of the valve sleeve and pushes the impact piston to move axially forward. When the impact piston moves forward a preset distance, the front high-pressure oil chamber is connected to the front oil return chamber, and the hydraulic oil pushes the valve body to move axially backward to close the high-pressure oil channel. The impact piston completes the impact under the action of the hydraulic oil and retreats backward; When the impact piston retreats a preset distance, the front oil return chamber is connected with the middle oil return chamber, the rear oil return chamber, and the rear total oil return chamber; the high-pressure oil injected into the rear high-pressure oil chamber pushes the valve body to move axially forward to open the high-pressure oil channel so that the rear high-pressure oil chamber is connected with the inner cavity of the valve sleeve, and the hydraulic oil enters the inner cavity of the valve sleeve and pushes the impact piston to move axially forward, and the cycle repeats.

3. A direct impact hydraulic rock drill according to claim 2, characterized in that: A plurality of back-thrust passages are distributed axially and circumferentially in the head of the valve sleeve and are connected to the high-pressure oil passage and the rear end oil return chamber; A plurality of forward thrust passages are distributed axially and circumferentially in the rear end of the cylinder liner, communicating with the rear end oil return chamber and the front end oil return chamber; A rear push rod and a front push rod are respectively slidably arranged in the rear push channel and the front push channel for pushing the valve body axial displacement under the action of hydraulic oil, wherein the diameter of the front push rod is larger than that of the rear push rod; An accumulator is installed on the side of the engine base, and the liquid side of the accumulator is connected to the rear high-pressure oil chamber; and an oil inlet channel for connecting the rear high-pressure oil chamber and the front high-pressure oil chamber is formed on the valve body and the cylinder sleeve; An oil inlet communicated with the rear high-pressure oil chamber and an oil outlet communicated with the rear total return oil chamber are provided on the side of the machine base.

4. A direct impact hydraulic rock drill according to claim 3, characterized in that: A plurality of step seals are embedded in the rear end inner cavity of the valve sleeve to prevent the hydraulic oil from leaking to the rear end, and a sealing component is embedded in the inner cavity where the cylinder sleeve and the cylinder body abut against each other to prevent the hydraulic oil from leaking to the front end; An annular rear end leakage oil chamber is formed in the rear end inner cavity of the valve sleeve located at the front end of the step seal; a front end leakage oil chamber is formed between the sealing assembly and the cylinder sleeve; The front leakage oil chamber is connected to the rear total oil return chamber; the rear leakage oil chamber is connected to the middle oil return chamber, and is connected to the rear total oil return chamber through the middle oil return chamber and the rear oil return chamber.

5. The direct impact hydraulic rock drill according to claim 3, characterized in that: The rotary assembly includes a cycloid motor, a pinion gear, and a gear; The pinion is arranged in the upper cavity of the gear box, and needle bearings are arranged on the outer sides of both ends of the pinion. The pinion rotates relative to the upper cavity of the gear box through the needle bearings. The large gear is clamped in the gear box and meshes with the small gear. Conical bearings are provided on the outside of both ends of the large gear. The large gear rotates relative to the gear box through the conical bearings. The tail of the shank is inserted into the large gear and has a clearance fit with the large gear without any rotation; The cycloid motor is installed outside the upper cavity of the gearbox, and the actuator shaft is inserted into the pinion and meshes with the pinion to drive the pinion to rotate forward or reverse, thereby driving the large gear and the shank to rotate synchronously.

6. A direct impact hydraulic rock drill according to claim 5, characterized in that: The rotary assembly also includes a triangular sleeve and a rear stop sleeve; The triangular sleeve is embedded in the front end inner cavity of the large gear, and the drill tail is inserted through the triangular sleeve. Teeth are formed around the drill tail along the length direction, and tooth grooves are formed in the inner cavity of the triangular sleeve. The drill tail is engaged with the tooth grooves of the triangular sleeve to achieve non-rotational and clearance fit. The rear stop sleeve is arranged in the inner cavity of the large gear at the rear end of the triangular sleeve to limit the axial displacement distance of the shank backward; the inner cavity of the head is formed with an inner convex ring to limit the axial displacement distance of the shank forward.

7. The direct impact hydraulic rock drill according to claim 5, characterized in that: A lubricating oil cavity is formed between the large gear and the small gear; A shaft seal is provided in the rear end inner cavity of the gearbox and the rear end inner cavity of the gearbox cover, which is in contact with the outer peripheral body of the corresponding end of the large gear and is used to prevent the lubricating oil in the lubricating oil cavity from leaking. A retaining ring is also embedded in the rear end inner cavity of the gearbox and the rear end inner cavity of the gearbox cover at the rear end of the shaft seal to prevent the displacement of the shaft seal. A sealing sleeve is provided outside the tapered bearing located outside the large gear head, which is in contact with and sealed against the inner wall of the gear box and the gear box cover to prevent leakage of lubricating oil in the lubricating oil cavity.

8. The direct impact hydraulic rock drill according to claim 1, characterized in that: A plug is provided at the tail of the machine, the tail of the water needle is inserted into the plug, and the tail of the water needle extends outward to form an anti-slip ring; An anti-slip part is provided in the plug, which is sleeved outside the water needle and abuts against the anti-slip ring; Water seals are provided in the tail of the machine and in the inner cavity of the shank, through which water supply needles are inserted, respectively, to prevent flushing water from leaking into the impact assembly and the rotary assembly; A water supply needle is also provided in the shank, through which a star-shaped ring for supporting the water needle is inserted; A water inlet hole for connecting the water inlet cavity and the water needle is provided on the water needle located in the water inlet cavity outside the anti-slip component.

9. The direct impact hydraulic rock drill according to claim 7, characterized in that: A copper sleeve for the shank to pass through is embedded in the front cavity of the machine head, and a retaining ring for preventing the copper sleeve from falling off is embedded in the head cavity of the machine head.

10. The direct impact hydraulic rock drill according to claim 9, characterized in that: An air intake cavity is also formed in the tail of the machine, the valve body closes the air intake cavity, and the air intake cavity is connected to the abutment surface of the accumulator and the tail of the machine; An air chamber is formed between the head of the cylinder body and the tail of the gear box. A plurality of air passages are correspondingly provided on the tail and the cylinder body to connect the air intake cavity and the air chamber. The air passages are respectively connected to the abutment surface between the tail and the cylinder body, and the abutment surface between the cylinder body and the gear box. The air chamber is connected to the outside atmosphere through the gap between the impact piston and the shank and the large gear, as well as the gap between the shank and the copper sleeve and the front gear. An air inlet connected to the air inlet chamber is provided on the tail of the machine for introducing gas into the air inlet chamber. The introduced gas is blown out through the abutting surfaces of the air inlet chamber, the accumulator and the tail of the machine, the abutting surfaces of the tail of the machine and the cylinder body, the abutting surfaces of the cylinder body and the gear box, the gap between the impact piston and the shank and the large gear, and the gap between the shank and the copper sleeve.

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