Flushing assembly

Abstract

The invention relates to a flushing assembly which comprises a machine head, a flushing head arranged in the machine head, a bit shank copper sleeve arranged on the rear side of the tail of the flushing head and a machine head copper sleeve arranged on the front side of the head of the flushing head, and a bit shank is arranged in the machine head and sequentially penetrates through the bit shank copper sleeve, the flushing head and the machine head copper sleeve. The bit shank copper sleeve and the machine head copper sleeve are used for preventing radial deviation of the bit shank, a cavity is formed between the flushing head and the bit shank, the head and the tail of the flushing head are respectively provided with a U-shaped seal, a center hole extending towards the head of the bit shank is formed in a front-section rod body of the bit shank, the cavity is communicated with the center hole, and a flushing medium connector for providing flushing media for the cavity is formed in the machine head. The bit shank copper sleeve and the machine head copper sleeve are arranged in the machine head, radial deviation of the bit shank is prevented through the guiding effect of the bit shank copper sleeve and the machine head copper sleeve, the stability of the bit shank is improved, and meanwhile the service life of the bit shank is guaranteed.

Description

[0001] Divisional Application Instructions This application is a divisional application based on the Chinese patent invention application with application number CN202411122500.2, application date August 15, 2024, and invention name “A Hydraulic Rock Drill”. Technical Field

[0002] The invention relates to a flushing assembly and belongs to the technical field of rock drills. Background Art

[0003] When a hydraulic rock drill is in operation, the impact piston strikes the drill tail, and the rotary mechanism drives the drill tail to rotate, breaking the rock during the impact and rotation process. During this process, the drill tail undergoes continuous axial displacement and rotation within the drill head. However, existing hydraulic rock drill head structures typically lack guide support assemblies or only feature one-way support guides. As a result, after the drill tail is impacted by the impact piston and collides with the rock, it undergoes radial displacement. This causes wear during the subsequent return stroke and further strokes, significantly reducing the drill tail's actual service life. Summary of the Invention

[0004] The object of the present invention is to provide a flushing assembly, which prevents the shank from radially deviating by arranging a shank copper sleeve and a shank copper sleeve in the handpiece and utilizing the guiding function of the shank copper sleeve and the handpiece copper sleeve, thereby improving the stability of the shank during impact and rotation and ensuring the service life of the shank.

[0005] In order to achieve the above object, the technical solution adopted by the present invention is: A flushing assembly comprises a machine head, a flushing head arranged in the machine head, a shank copper sleeve arranged at the rear side of the tail of the flushing head, and a machine head copper sleeve arranged at the front side of the head of the flushing head. A shank is provided in the machine head, and the shank passes through the shank copper sleeve, the flushing head and the machine head copper sleeve in sequence. The shank copper sleeve and the machine head copper sleeve are used to prevent the shank from radially shifting. A cavity is formed between the flushing head and the shank. The head and tail of the flushing head are both provided with U-shaped seals. A central hole extending toward the head of the shank is formed on the front rod body of the shank, and the cavity is connected to the central hole. A flushing medium interface for providing flushing medium to the cavity is provided on the machine head.

[0006] Preferably, a flushing cavity is formed in the handpiece, a water hole connecting the flushing cavity and the central hole is formed on the flushing head, and a water inlet channel connecting the flushing medium interface and the flushing cavity is formed on the handpiece.

[0007] Preferably, the flushing cavity is annular.

[0008] Preferably, a U-shaped seal is also provided in the shank copper sleeve, and a flushing water leakage chamber is formed between the U-shaped seal in the shank copper sleeve and the U-shaped seal at the tail of the flushing head.

[0009] Preferably, an annular water return cavity is formed on the inner wall of the machine head outside the abutment between the shank copper sleeve and the flushing head, the flushing water leakage chamber is connected with the water return cavity, and a plurality of drainage channels connected with the water return cavity are provided on the machine head.

[0010] Preferably, a plurality of drain ports communicating with the water return chamber are formed around the shank copper sleeve, and the flushing water in the flushing water leakage chamber is discharged through the drain ports, the water return chamber and the drainage channel.

[0011] Preferably, the machine head is provided with a first oil filling port and a first oil filling plug arranged in the first oil filling port, and the first oil filling port is connected to the return water chamber to lubricate the area between the U-shaped seal in the shank copper sleeve and the U-shaped seal 69 at the tail of the flushing head.

[0012] Preferably, the handpiece is provided with a second oil filling port and a second oil filling plug arranged in the second oil filling port, and the second oil filling port is communicated with the flushing head and the abutting surface of the handpiece copper sleeve.

[0013] Preferably, sealing rings are provided on the outside of the head and tail of the flushing head for sealing with the machine head.

[0014] Preferably, the head of the machine head is provided with a protective cover for the shank to pass through.

[0015] The beneficial effects of the present invention are: 1. The various sections of the machine body are connected, and the assembly between the sections is more secure, which can improve the overall stability. It can also solve the problem of loose connection and poor stability caused by the deformation of the long screw due to the vibration of the machine body during heavy work, making it easier to repair and replace the components. At the same time, it can reduce the installation gap and facilitate the disassembly of a single component by simply disassembling the corresponding connector (without disassembling the entire unit). 2. The buffer assembly adopts a single-stage buffer design, which solves the problem of the existing double-stage buffer assembly requiring an additional separate buffer oil port. At the same time, the oil inlet and outlet of the buffer assembly are both realized through the oil inlet channel, eliminating the need for additional channels to achieve oil inlet and outlet at the buffer assembly, reducing processing difficulty. 3. The structural design of the impact assembly limits the stroke of the impact piston, making it have the characteristics of small impact energy and high frequency, which can reduce damage to the impact piston and drill tail and extend their service life; 4. The leakage oil of the cycloid motor is used to lubricate the large gear and the small gear. This eliminates the need for operators to inject additional grease for lubrication before each shift. This avoids the tedious process of injecting additional grease for lubrication of the large gear and the small gear in each shift. 5. The head of the cylinder liner extends into the tail cavity of the intermediate body and abuts against the intermediate body. When the bolts are loosened, this connection between the cylinder liner and the intermediate body can also effectively protect the impact piston from being damaged. 6. The flushing assembly can effectively flush the shank and adopts a no-flush joint design, which avoids the problem of flushing failure caused by the bolts at the connection between the existing flushing joint and the machine head easily falling off; 7. A dust ring is set on the abutment surface and air blowing is adopted. At the same time, the gap between the head of the shank and the head of the machine can be blown to reduce the risk of component damage and extend the service life. Furthermore, the purge gas can enter the gap between the buffer piston and the rear stop sleeve of the shank, the buffer piston, the large gear, and the gap between the shank and the large gear to cool the components and reduce the working temperature. 8. The number of parts in the hydraulic rock drill has been reduced to about 90, most of which can be purchased on the market with the same specifications, making replacement easier; and some optimized parts are also easy to process; 9. The interfaces of the oil inlet, oil outlet, leakage oil and air passages are concentrated at the tail of the machine. Therefore, it can be applied to the drilling rig regardless of which side the rig oil supply system and oil pipes are arranged on. The installation angle of the machine head can also be adjusted according to the placement of the flushing system, so that the water inlet channel can be more conveniently connected to the flushing medium, improving applicability. The overall machine body adopts a nearly symmetrical structural design, which is convenient for assembly to the rock drilling rig. 10. A Gly ring is installed at the fitting surface between the large gear and the inner cavity of the intermediate body, isolating the third chamber from the second chamber. This unique sealing design replaces the traditional skeleton oil seal and can withstand greater oil pressure. At the same time, multiple guide rings installed at the fitting surface can effectively support the large gear, enabling it to maintain axial stability during operation and extend its service life. 11. A brazing tail copper sleeve and a machine head copper sleeve are installed in the machine head. The brazing tail copper sleeve and the machine head copper sleeve replace the existing single support to play a guiding and supporting role, prevent the brazing tail from radial deviation, improve the stability of the brazing tail during impact and rotation, and ensure the service life of the brazing tail. 12. The seal (U-shaped seal) in the existing machine head used to prevent leakage of the flushing medium is extremely inconvenient to disassemble due to the machine body structure and component installation structure, which makes it inconvenient to replace the seal when it is worn and loses its sealing effect; therefore, in this application, the machine head and the gear box cover are detachably connected, so that the shank copper sleeve and the flushing head are easy to remove, thereby removing the U-shaped seal from the shank copper sleeve and the flushing head, and then replacing the U-shaped seal, which is simple and convenient to operate and reduces manpower and financial resources. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 It is a three-dimensional schematic diagram of a hydraulic rock drill; Figure 2 This is a cross-sectional view of a hydraulic rock drill from one perspective; Figure 3 A cross-sectional view of the hydraulic rock drill from another perspective; Figure 4 This is a half-section diagram of a hydraulic rock drill; Figure 5 It is a schematic diagram of the structure of the front and rear push rods; Figure 6 This is a structural diagram of a duct; Figure 7 This is a schematic diagram of the structure of channel two and channel three; Figure 8 It is a structural diagram of the cylinder liner and the impact piston; Figure 9 It is a structural diagram of the oil inlet channel and the oil outlet channel; Figure 10 It is a schematic diagram of the triangular sleeve structure; Figure 11 It is a cross-sectional view of the fastener connection; Figure 12 Schematic diagram of the air passage for supplying air to the air cavity.

[0017] The main reference numerals in the figures have the following meanings: 1. Tail, 2. Cylinder, 3. Intermediate, 4. Head, 5. Rear cover, 6. Cylinder, 7. Intermediate, 8. Gearbox cover, 9. Head, 10. Fasteners, 11. Dust seal, 12. Impact piston, 13. Boring tail, 14. Valve sleeve, 15. Valve body, 16. Cylinder liner, 17. Rear sealing sleeve, 18. Rear copper sleeve, 19. Piston front guide sleeve, 20. Front sealing guide sleeve, 21. Seal ring, 22. Step seal, 23. Rear high-pressure oil chamber, 24. Rear total return oil chamber, 25 , impact oil inlet interface, 26, impact oil return interface, 27, connecting channel, 28, rear push channel, 29, rear end oil return chamber, 30, middle oil return chamber, 32, front end oil return chamber, 33, front end high-pressure oil chamber, 34, channel one, 35, channel two, 36, channel three, 37, ring groove, 38, front push channel, 39, rear push rod, 40, front push rod, 41, rear stage, 42, front stage, 43, force surface A, 44, force surface C, 45, section B, 46, force surface B, 47 , inner stage D, 48, inner stage E, 49, leakage oil chamber, 50, leakage oil return joint, 51, leakage oil channel, 52, buffer chamber, 53, rear stop sleeve of shank tail, 54, buffer piston, 55, accumulator, 56, oil inlet channel, 57, oil outlet channel, 58, gearbox, 59, stop ring, 60, small gear, 61, large gear, 62, needle roller bearing, 63, tapered bearing, 64, inner copper sleeve, 65, triangular sleeve, 66, flushing head, 67, copper sleeve of shank tail, 68, machine head copper Sleeve, 69, U-shaped seal, 70, center hole, 71, flushing chamber, 72, water hole, 73, flushing medium interface, 74, protective cover; 75, cycloid motor, 76, gear pad, 77, lubrication chamber, 78, flushing water leakage chamber, 79, return water chamber, 80, drain port, 81, drain channel, 82, oil filling port, 83, oil filling plug, 84, purge air chamber, 85, purge air hole, 87, air channel, 88, air chamber, 89, guide ring, 90, oil seal, 91, grid ring. DETAILED DESCRIPTION

[0018] The present invention will be described in detail below with reference to the accompanying drawings and embodiments.

[0019] This embodiment provides a hydraulic rock drill, see Figure 1-12As shown, the machine body comprises a tail section 1, a cylinder section 2, an intermediate section 3, and a head section 4, which are connected in sections. Specifically, the tail section 1 includes a rear cover 5, the cylinder section 2 includes a cylinder 6, the intermediate section includes an intermediate body 7 and a gearbox cover 8, and the head section 4 includes a head 9. The tail section and the cylinder 6 are fixed together by multiple fasteners 10, and the cylinder 6 and the intermediate section 7 are fixed together by multiple fasteners 10. The intermediate section 7, the gearbox cover 8, and the head 9 are positioned sequentially by multiple internal locating pins and then fixed together by multiple fasteners 10. The tail section of the gearbox cover 8 is embedded in the head section of the intermediate section 7, and the tail section of the head 9 is embedded in the head section of the gearbox cover 8. Dust rings 11 are provided on the contact surfaces between the rear cover 5 and the cylinder 6, the contact surfaces between the cylinder 6 and the intermediate section 7, the contact surfaces between the intermediate section 7 and the gearbox cover 8, and the contact surfaces between the gearbox cover 8 and the head 9.

[0020] The body of the hydraulic rock drill is divided into multiple sections according to its structure, and these sections are connected to form an integral structure through independent fasteners 10, thereby replacing the method of using long screws to fix the multiple sections into one in the existing rock drill. By optimizing the structural force, the overall stability is improved, and the problem of loose connection and poor stability caused by the deformation of the long screw due to the vibration of the hydraulic rock drill body during heavy work is effectively solved. At the same time, it is convenient for the subsequent maintenance and replacement of components.

[0021] The tail section 1 and cylinder section 2 together form the impact assembly; the intermediate section 3 includes a rotary assembly and a buffer assembly, and the head section 4 includes a flushing assembly. The impact assembly and buffer assembly together form a first chamber for accommodating an impact piston 12 (with a central passage); the rotary assembly and flushing assembly together form a second chamber for accommodating a shank adapter 13, with the first and second chambers communicating with each other. Specifically, the tail section and cylinder section 6, the cylinder section 6 and intermediate section 7, and the intermediate section 7, gearbox cover 8, and head section 9 are secured together by fasteners 10, forming a connected first and second chambers.

[0022] The impact assembly also includes a valve sleeve 14, a valve body 15, a cylinder sleeve 16, and an impact piston 12. The valve sleeve 14 is positioned in the rear end of the cylinder body 6 and abuts the rear cover 5. The cylinder sleeve 16 is positioned in the head end of the cylinder body 6, with the rear end of the cylinder sleeve 16 abutting the head end of the valve sleeve 14. The head end of the cylinder sleeve 16 is inserted into the rear end of the intermediate body 7. The valve sleeve 14 and the cylinder sleeve 16 are positioned by locating pins to prevent relative rotation. A rear sealing sleeve 17 and a rear copper sleeve 18 are sequentially positioned in the rear end of the valve sleeve 14, from back to front. The valve body 15 is positioned in the head end of the valve sleeve 14, and a piston guide sleeve 19 and a front sealing sleeve 20 are sequentially positioned in the head end of the valve sleeve 14, from back to front. The impact piston 12 passes through the rear sealing sleeve 17, rear copper sleeve 18, valve body 15, piston guide sleeve 19, and front sealing sleeve 20, and extends into the second chamber.

[0023] The contact surfaces between the valve sleeve 14 and the rear cover 5, cylinder body 6, rear sealing sleeve 17, and rear copper sleeve 18, as well as the contact surfaces between the cylinder sleeve 16 and the cylinder body 6, intermediate body 7, piston front guide sleeve 19, and front sealing guide sleeve 20, are sealed by sealing rings 21. Sealing rings 21 do not block the flow of hydraulic oil or lubricating gas. Furthermore, grooves within the rear sealing sleeve 17 and front sealing guide sleeve 20 contain step seals 22 to ensure a seal with the impact piston 12 and prevent hydraulic oil leakage. In other words, the rear sealing sleeve 17 and rear copper sleeve 18, the piston front guide sleeve 19 and front sealing guide sleeve 20, and the corresponding sealing rings 21 and step seals 22 form a sealing assembly that prevents hydraulic oil leakage.

[0024] A rear high-pressure oil chamber 23 and a rear total oil return chamber 24 are formed between the valve sleeve 14 and the cylinder body 6, from rear to front. The rear cover 5 is provided with two impact oil inlet ports 25 (P) communicating with the rear high-pressure oil chamber 23, and two impact oil return ports 26 (T) communicating with the rear total oil return chamber 24. The head of the valve sleeve 14 has multiple communication passages 27 for connecting the rear high-pressure oil chamber 23 with the inner cavity of the head of the valve sleeve 14. Multiple rearward thrust passages 28 are axially formed around the head of the valve sleeve 14, and the rearward thrust passages 28 communicate with several of the communication passages 27.

[0025] A rear oil return chamber 29 is formed between the inner cavities of the valve sleeve 14 and the inner cavities of the cylinder sleeve 16, where they meet the valve body 15. An annular intermediate oil return chamber 30, a front oil return chamber 32, and a front high-pressure oil chamber 33 are radially formed in the cylinder sleeve 16 from rear to front, separated by the impact piston 12. The intermediate oil return chamber 30 communicates with the rear oil return chamber 29 via a first channel 34 in the cylinder sleeve 16, and with the rear main oil return chamber 24 via a second channel 35 in the valve sleeve 14, which communicates with the first channel 34, and a third channel 36 in the valve sleeve 14, which communicates with the second channel 35. An annular groove 37 is also formed in the cylinder body 6, communicating with the front high-pressure oil chamber 33. The annular groove 37 is also connected to the rear high-pressure oil chamber 23 and the impact oil inlet port 25 (P). The rear end of the cylinder body 6 has multiple forward thrust channels 38, each corresponding to the rear thrust channels 28, with both ends connected to the rear oil return chamber 29 and the intermediate oil return chamber 30.

[0026] A rear push rod 39 and a front push rod 40 are respectively embedded in each rear push channel 28 and each front push channel 38. The diameter of the front push rod 40 is larger than that of the rear push rod 39, and the rear push rod 39 and the front push rod 40 can move freely in the corresponding rear push channel 28 and the front push channel 38 (clearance fit); the valve body 15 can move freely in the head cavity of the valve sleeve 14 (clearance fit). In the initial state, the tail of the valve body 15 closes the connecting channel 27, and the head of the valve body 15 and the rear end of the cylinder sleeve 16 have a gap connecting the inner cavity of the valve body 15 and the rear end oil return cavity 29; a raised portion is formed on the outer periphery of the front end of the valve body 15, and the rear push rod 39 abuts against the rear end surface of the raised portion, and the front push rod 40 abuts against the front end surface of the raised portion. Under the action of hydraulic oil, the valve body 15 can axially displace relative to the impact piston 12 in the space formed by the front end cavity of the valve sleeve 14 and the rear end cavity of the cylinder sleeve 16.

[0027] The impact piston 12 has a rear stage 41 and a front stage 42. The rear end of the rear stage 41 of the impact piston 12 forms a force surface A43, and the front end forms a force surface C44. The rear end of the front stage 42 of the impact piston 12 forms a cross-section B45, and the front end forms a force surface B46. The force area of ​​the force surface A43 is larger than the force areas of the force surfaces C44 and B46. The rear stage 41 of the impact piston 12 can be axially displaced in the head cavity of the valve sleeve 14 and the tail cavity of the cylinder sleeve 16. The cylinder sleeve 16 has an inner stage D47 for separating the front oil return chamber 32 and the front high-pressure oil chamber 33, and an inner stage E48 for separating the front high-pressure oil chamber 33 and the head cavity of the cylinder sleeve 16. The front stage 42 of the piston can be axially displaced in the inner stage D47, the front high-pressure oil chamber 33 and the inner stage E48 of the cylinder sleeve 16.

[0028] The rear sealing sleeve 17 and the rear copper sleeve 18 together constitute the rear sealing assembly, the piston front guide sleeve 19 and the front sealing guide sleeve 20 together constitute the rear sealing assembly, and leakage oil chambers 49 are respectively formed between the rear sealing assembly, the front sealing assembly and the corresponding valve sleeve 14 inner cavity and the cylinder body 6 inner cavity; a leakage return oil joint 50 (Da) is provided on the rear cover 5, and a leakage oil channel 51 is formed on the cylinder body 6 and the intermediate body 7. The leakage oil chamber 49 is connected to the leakage oil channel 51 and communicates with the leakage return oil joint 50, which is used to discharge the hydraulic oil in the leakage oil chamber 49.

[0029] An annular buffer chamber 52 is radially formed in the inner cavity of the head of the intermediate body 7. The buffer assembly includes a shank rear stop sleeve 53 and a buffer piston 54. The impact piston 12 penetrates the buffer piston 54 and the shank rear stop sleeve 53. The buffer piston 54 is embedded in the inner cavity of the head of the intermediate body 7 and seals the buffer chamber 52. The shank rear stop sleeve 53 is arranged between the buffer piston 54 and the shank 13, and they abut each other. The buffer chamber 52 is filled with hydraulic oil that can push the buffer piston 54 to move axially forward to abut the shank rear stop sleeve 53. When the shank 13 rebounds, it strikes the shank rear stop sleeve 53 and acts on the buffer piston 54. The buffer piston 54 is impacted by the shank rear stop sleeve 53, causing it to move axially backward and squeeze the hydraulic oil out of the buffer chamber 52.

[0030] Two accumulators 55 are symmetrically mounted on the outside of the cylinder body 2. The cylinder body 6 and the intermediate body 7 together form a plurality of oil inlet channels 56 for supplying hydraulic oil to the rear high-pressure oil chamber 23, the front high-pressure oil chamber 33, and the buffer chamber 52. The oil inlet channels 56 are connected to the impact oil inlet port 25 (P). The cylinder body 6 also forms an oil outlet channel 57 for discharging hydraulic oil from the rear total return oil chamber 24. The oil outlet channel 57 is connected to the impact oil return port 26 (T). The rear high-pressure oil chamber 23, the front high-pressure oil chamber 33, and the buffer chamber 52 are all connected to the liquid phase side of the accumulator 55 via the oil inlet channels 56. Furthermore, the accumulator 55 is also equipped with a nitrogen charging head connected to the gas phase side to facilitate the charging of nitrogen into the gas phase side of the accumulator 55.

[0031] The rotary assembly includes a transmission mechanism and a shank 13. The shank 13 is horizontally and rotatably arranged in the transmission mechanism located in the intermediate body 7 and the machine head 9 and extends to the outside of the head of the machine head 9. The tail of the shank 13 abuts against the shank rear stop sleeve 53 and leaves a certain distance from the head of the impact piston 12 to be struck. When the impact piston 12 is axially displaced forward by the action of hydraulic oil, it acts on the shank 13 to cause axial displacement.

[0032] The transmission mechanism includes a cycloidal motor 75 mounted on the gear box 58 on the intermediate body 7 for driving the transmission assembly to rotate the shank 13, and a stop ring 59 located in the tail cavity of the head 9 for limiting the axial displacement distance of the shank 13.

[0033] The transmission assembly includes a pinion 60 and a large gear 61. The pinion 60 is located in the cavity above the gearbox 58 (the third cavity) and is connected to the cycloid motor 75 actuator shaft (the cycloid motor 75 actuator shaft and the inner cavity of the pinion end form meshing teeth). It is rotatably connected to the gearbox 58 through needle bearings 62 arranged on the outer ends. At the same time, a gear pad 76 is also provided in the cavity above the gearbox 58, one end of which is inserted into the pinion 60 to prevent the pinion 60 from shifting. The other end of the gear pad 76 abuts the inner wall of the cavity above the gearbox 58. The large gear 61 is located in the cavity below the gearbox 58 and meshes with the pinion 60. It is rotatably connected to the gearbox 58 through two tapered bearings 63 arranged on the outer circumference of each end, and the axial displacement of the large gear 61 is limited. The head of the large gear 61 extends into the inner cavity of the gearbox cover 8, and the tail abuts the buffer piston 54. The shank tail rear stop sleeve 53 is set in the tail cavity of the large gear 61. At the same time, two stages with increasing inner diameters are formed from back to front in the inner cavity of the head of the large gear 61. An inner copper sleeve 64 is embedded in the stage at the rear end, and a triangular sleeve 65 is embedded in the stage at the front end. There is no rotational fit between the triangular sleeve 65 and the large gear 61 (i.e., relative rotation cannot occur between the triangular sleeve 65 and the large gear 61). The tail of the drill tail 13 is inserted into the inner cavity of the triangular sleeve 65 and there is also no rotational fit (i.e., relative rotation cannot occur between the triangular sleeve 65 and the drill tail 13) and it can be axially displaced relative to the triangular sleeve 65. At the same time, a limiting portion is also formed at the tail of the drill tail 13 to limit the drill tail 13 from escaping from the triangular sleeve 65 after being hit.

[0034] On the outside of the cylinder body 2, there are an oil inlet port for supplying hydraulic oil to the cycloidal motor 75 and an oil drain port for draining the hydraulic oil from the cycloidal motor 75 (ports A / B can be selectively used as either the oil inlet or drain port. By changing the oil inlet and drain ports, the rotation direction of the cycloidal motor 75 can be changed. This is prior art, and the structure of the cycloidal motor 75 and the hydraulic drive reversing principle will not be further described). The oil inlet and drain ports are both connected to a channel on the intermediate body that is connected to the oil chamber of the cycloidal motor 75 via pipelines to facilitate the flow of hydraulic oil. The operation of the cycloidal motor 75 drives the pinion 60, which in turn drives the gear 61 to rotate. Since the tail of the shank 13 is inserted into the inner cavity of the triangular sleeve 65, and the triangular sleeve 65 and the gear 61 are not rotationally matched, the tail of the shank 13 is also inserted into the inner cavity of the triangular sleeve 65 without rotational matching and can axially move relative to the triangular sleeve 65. Therefore, when the gear 61 rotates, the shank 13 can be driven to rotate.

[0035] Furthermore, the head and tail of the large gear 61 are both fitted with the inner cavity of the intermediate body 7, and grid rings 91 are also provided at the fitting surfaces. The grid rings 91 isolate the cavity above the gear box 58 (the third cavity) from the second cavity, effectively replacing the traditional skeleton oil seal and being able to withstand greater oil pressure; a plurality of guide rings 89 are also provided at the fitting surface between the large gear 61 located on the outside of the two grid rings 91 and the inner cavity of the intermediate body 7, which can effectively support the large gear 61, so that it can maintain axial stability during operation and extend its service life. Due to the presence of the grid ring 91, a closed space is formed between the large gear 61 and the cavity above the gear box 58 (the third chamber). Since lubrication is also required between the large gear 61 and the small gear 60, the closed space can be used as a lubrication chamber 77, and the lubrication chamber 77 is connected to the leakage oil channel 51. During operation, the driving hydraulic oil of the cycloid motor 75 will leak into the lubrication chamber 77, and then the small gear 60 and the large gear 61 can be lubricated and discharged through the leakage oil channel 51.

[0036] The flushing assembly includes a handpiece 9 and a flushing head 66. The flushing head 66 is disposed in the inner cavity of the handpiece 9. A shank copper sleeve 67 and a handpiece copper sleeve 68 are disposed in the handpiece 9 to prevent axial displacement of the flushing head 66. The tail of the shank copper sleeve 67 abuts against the head of the stop ring 59, and the handpiece copper sleeve 68 is embedded in the head cavity of the handpiece 9. The shank 13 is sequentially inserted through the shank copper sleeve 67, the flushing head 66, and the handpiece copper sleeve 68. The shank copper sleeve 67 and the handpiece copper sleeve 68 further prevent the shank 13 from radially deflecting during impact and rotation, thereby improving working stability. U-shaped seals 69 are installed inside the flushing head 66 and the copper sleeve 67 of the shank adapter to prevent leakage of the flushing medium. Seal rings are also installed at the head and tail of the flushing head 66 to seal against the handpiece 9. A central hole 70 extending toward the head of the shank adapter 13 is formed on the front rod of the shank adapter 13. An annular flushing chamber 71 is formed in the inner cavity of the handpiece 9. A water hole 72 is provided in the flushing head 66 to connect the flushing chamber 71 with the central hole 70. A flushing medium interface 73 (F) is provided on the handpiece 9 for injecting flushing medium into the flushing chamber 71. Furthermore, a protective cover 74 is provided at the head of the handpiece 9 for the shank adapter 13 to pass through.

[0037] When the shank 13 is subjected to impact and rotation operations, flushing water is injected through the flushing medium interface 73 (F). The flushing water enters the flushing chamber 71 and enters the cavity formed between the flushing head 66 and the shank 13 through the water outlet 72. Due to the presence of the U-shaped seal 69 in the head and tail of the flushing head 66, the flushing water enters the center hole 70 on the shank 13, flushes the center hole 70, cools the shank 13, and is then discharged through the center hole 70.

[0038] In actual application, part of the flushing water will enter the copper sleeve 67 through the U-shaped seal 69 at the tail of the flushing head 66, at this time, a flushing water leakage chamber 78 will be formed between the U-shaped seal 69 in the copper sleeve 67 and the U-shaped seal 69 at the tail of the flushing head 66. In order to discharge the water in the flushing water leakage chamber 78, an annular backwater chamber 79 is formed on the inner wall of the machine head 9 outside the abutting position of the copper sleeve 67 and the flushing head 66, a plurality of water discharge openings 80 are formed on the copper sleeve 67 and communicate with the backwater chamber 79, and a plurality of water discharge channels 81 are formed on the machine head 9 and communicate with the backwater chamber 79. When there is flushing water in the flushing water leakage chamber 78, the flushing water can be discharged out of the machine body through the water discharge openings 80, the backwater chamber 79 and the water discharge channels 81.

[0039] At the same time, in order to lubricate the area formed by the drill bit 13, the copper sleeve 68, the flushing head 66, the machine head 9 and the area between the U-shaped seal 69 in the copper sleeve 67 and the U-shaped seal 69 at the tail of the flushing head 66, two oil injection openings 82 are formed on the machine head 9 and oil injection plugs 83 are installed in the oil injection openings 82. One of the oil injection openings 82 communicates with the backwater chamber 79, and the other oil injection opening 82 communicates with the abutting surface of the flushing head 66 and the copper sleeve 68.

[0040] The lubricating oil is injected when the hydraulic rock drill is in a non-working state. One of the lubricating oils is injected through the oil injection plug 83 and the oil injection opening 82 which communicate with the backwater chamber 79, and then enters the flushing water leakage chamber 78 through the backwater chamber 79 and the water discharge opening 80, thereby lubricating the area between the U-shaped seal 69 in the copper sleeve 67 and the U-shaped seal 69 at the tail of the flushing head 66. The other lubricating oil is injected through the oil injection plug 83 and the oil injection opening 82 which communicate with the abutting surface of the flushing head 66 and the copper sleeve 68. Since no sealing element is arranged at the abutting surface of the flushing head 66 and the copper sleeve 68 and between the copper sleeve 68 and the machine head 9, the lubricating oil can enter the gap and then lubricate the area formed by the drill bit 13, the copper sleeve 68, the flushing head 66 and the machine head 9.

[0041] When the hydraulic rock drill is working, dust will adhere to the surface of the machine body, and part of the dust will enter the machine body through the abutting surfaces of the rear cover 5 and the cylinder body 6, the cylinder body 6 and the intermediate body 7, the intermediate body 7 and the gear box cover 8, the gear box cover 8 and the machine head 9, the abutting surface of the trochoidal motor 75 and the intermediate body 7 (gear box 58) and the gap between the head of the drill bit 13 and the copper sleeve 68. At the same time, the temperature of the parts in the machine body will rise during operation, and the high temperature will affect the service life of the parts.

[0042] Based on this, an air passage 87 is opened in the rear cover 5, the cylinder body 6, the intermediate body 7, the gear box cover 8 and the machine head 9; and an annular purge air chamber 84 is radially formed in the machine head 9 outside the machine head copper sleeve 68, and a plurality of purge air holes 85 are opened around the machine head copper sleeve 68 to connect the purge air chamber 84 and the gap between the machine head copper sleeve 68 and the drill tail 13; at the same time, an annular air chamber 88 is formed in the second chamber where the large gear 61 abuts the buffer piston 54, and the impact piston 12 also has a central channel. The interface (AIR) of the air outlet channel 87 is set on the rear cover 5. After the purge gas enters through the interface of the air outlet channel 87, a part of the gas is first guided to the abutment surface between the rear cover 5 and the cylinder body 6 through the air outlet channel 87 and blown out from the abutment surface between the rear cover 5 and the cylinder body 6. The remaining gas continues to move forward along the air outlet channel 87, and a part of the gas is guided to the abutment surface between the accumulator 55 and the cylinder body 6 on both sides of the cylinder body 6 through the branch channel connected to the air outlet channel 87 and blown out from the abutment surface between the accumulator 55 and the cylinder body 6. The remaining gas continues to move forward along the gas passage 87 and enters the gas chamber 88. The gas passage 87 on the cylinder body 6 that introduces the purge gas into the gas chamber 88 is located on the opposite side of the gas passage 87 on the intermediate body 7. Then the purge gas can act on the entire gas chamber 88 to achieve sufficient cooling of the cylinder liner 16; the purge gas further passes through the subsequent gas passage 87 connected to the gas chamber 88 to introduce the gas into the abutment surface between the buffer piston 54, the large gear 61 and the rear stop sleeve 53 of the shank, and enters through the gap at the abutment surface, and then can contact the impact The piston 12 and the shank tail 13 and other components are in contact to cool them down; further, the intermediate body 7 is provided with an air guide channel that connects the area where the buffer piston 54 and the large gear 61 and the abutment surface of the shank tail rear stop sleeve 53 are connected to the abutment surface of the cycloid motor 75 and the intermediate body 7 (gear box 58), so the purge gas entering the area where the buffer piston 54 and the large gear 61 and the abutment surface of the shank tail rear stop sleeve 53 can enter the abutment surface of the cycloid motor 75 and the intermediate body 7 (gear box 58) through the air guide channel and purge it. At the same time, there is also a gap between the shank 13 and the triangular sleeve 65, so the incoming purge gas can pass through the gap between the shank 13 and the triangular sleeve 65 into the cavity between the triangular sleeve 65 and the stop ring 59, and pass through the gap formed between the gear box cover 8, the machine head 9, the stop ring 59 and the large gear 61 and the subsequent air passage 87 connected to the gap to enter the purge gas chamber 84, and is guided to the gap between the shank 13 and the machine head copper sleeve 68 through the purge air hole 85 for air purge; further, a branch channel is formed at the gear box cover 8 to guide the purge gas to the abutment surface of the intermediate body 7 and the gear box cover 8, and the purge gas will pass through the abutment surface of the gear box cover 8 and the machine head 9 on the path leading to the head of the shank 13, so that the purge gas will be blown out through the two abutment surfaces to realize air blowing.

[0043] To prevent purge gas from entering the hydraulic oil chambers behind the piston's front guide sleeve 19 and the front sealing guide sleeve 20, an oil seal 90 is embedded in the head of the front sealing guide sleeve 20. The impact piston 12 passes through the oil seal 90. The oil seal 90 has an inwardly formed annular groove. The tail of the oil seal 90 is embedded in the front sealing guide sleeve 20, and the head of the front sealing guide sleeve 20 is embedded in the annular groove. In addition to preventing purge gas from entering the rear hydraulic oil chamber, the oil seal 90 further prevents hydraulic oil leakage if a gap is created by wear in the step seal 22 between the front sealing guide sleeve 20 and the impact piston 12.

[0044] The piston impact process is further described below.

[0045] Stroke, reversing The first stage: the high-pressure hydraulic oil enters the rear end high-pressure oil chamber 23 through the impact oil inlet interface 25 (P) on the rear cover 5, and the high-pressure oil enters the connecting channel 27. At this time, the valve body 15 closes the inner mouth of the connecting channel 27, and the high-pressure oil will enter the left end chamber of the rear push channel 28 connected to the connecting channel 27. Since the forward push channel 38 is connected to the front end oil return chamber 32, the middle oil return chamber 30, the rear end oil return chamber 29 and the rear end total oil return chamber 24 and is connected to the impact return oil interface 26 (T) on the rear cover 5, there is no high-pressure oil in the right end chamber of the forward push channel 38.

[0046] The second stage: high-pressure oil always enters the left end chamber of the rear push channel 28 to push the rear push rod 39 to move axially to the right, and then pushes the valve body 15 to move axially to the right. After the valve body 15 moves to the right, it abuts against the tail of the cylinder sleeve 16, and then the gap between the head of the valve body 15 and the tail of the cylinder sleeve 16 that originally connected the inner cavity of the valve body 15 and the middle oil return cavity 30 is closed. At this time, the connecting channel 27 and the inner cavity of the head of the valve sleeve 14 are connected, so that high-pressure oil can enter the inner cavity of the head of the valve sleeve 14. Since the force area of ​​the force surface A43 is greater than the force area of ​​the force surface B46, the impact piston 12 is pushed to move axially to the right.

[0047] The third stage: During the forward movement of the impact piston 12, when the cross section B45 passes the front end surface of the inner stage D47, the high-pressure oil in the front high-pressure oil chamber 33 enters the front oil return chamber 32 and enters the right end chamber of the forward push channel 38. Since the diameter of the front push rod 40 is larger than that of the rear push rod 39, under the condition of equal pressure, the front push rod 40 will push the valve body 15 to the left until the valve body 15 closes the inner opening of the communication channel 27 again. At this time, there is a gap between the head of the valve body 15 and the tail of the cylinder liner 16. The gap between the inner cavity of the connecting valve body 15 and the rear end oil return chamber 29 is restored, so that the hydraulic oil located in the inner cavity of the valve body 15 can enter the rear end oil return chamber 29 through the gap, and then the force surface A43 is pressure-free. The force surface C44 is acted upon by the high-pressure oil that enters the front end oil return chamber 32 through the front end high-pressure oil chamber 33 and acts on the force surface C44 through the gap between the impact piston 12 and the cylinder sleeve 16, so that the impact piston 12 decelerates until it hits the shank tail 13 and changes direction. After the impact, the shank tail 13 will move to the right to impact the target object.

[0048] Return, reversing Stage 1: After the impact piston 12 is reversed, since only the force surface C44 is affected by the oil pressure, the impact piston 12 accelerates to the left. During the process of the impact piston 12 moving to the left, when the cross section B45 passes the front end surface of the inner stage D47, only the force surface B46 is affected by the oil pressure. Since the area of ​​the force surface B46 is smaller than the area of ​​the force surface A43, the acceleration of the return motion of the impact piston 12 decreases at this time.

[0049] The second stage: as the impact piston 12 continues to move to the left, when the force surface C44 passes over the front end surface of the intermediate oil return chamber 30, the high-pressure oil originally in the right end chamber of the forward thrust channel 38 enters the intermediate oil return chamber 30, reducing the leftward force acting on the front thrust rod 40; and since high-pressure oil always enters the left end chamber of the backward thrust channel 28, it will push the valve body 15 to the right. Therefore, the valve body 15 moves to the right at this time. When it reaches a certain position, a closed space filled with hydraulic oil will be formed by the impact piston 12, the valve sleeve 14, the valve body 15, and the cylinder sleeve 16, causing the impact piston 12 to brake.

[0050] When the valve body 15 continues to move rightward, the inner port of the communication channel 27 is opened, and the high-pressure oil enters the inner cavity of the head of the valve sleeve 14, acts on the force surface A43, and causes the impact piston 12 to reverse and start a new round of stroke movement.

[0051] The above is only a preferred embodiment of the patent of the present invention. 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 patent of the present invention. These improvements and modifications should also be regarded as the scope of protection of the patent of the present invention.

Claims

1. A flushing assembly, characterized in that: The invention comprises a machine head, a flushing head arranged in the machine head, a shank copper sleeve arranged at the rear side of the tail of the flushing head, and a machine head copper sleeve arranged at the front side of the head of the flushing head. A shank is provided in the machine head, and the shank passes through the shank copper sleeve, the flushing head and the machine head copper sleeve in sequence. The shank copper sleeve and the machine head copper sleeve are used to prevent the shank from radially shifting. A cavity is formed between the flushing head and the shank. The head and the tail of the flushing head are both provided with U-shaped seals. A central hole extending toward the head of the shank is formed on the front rod body of the shank, and the cavity is connected to the central hole. A flushing medium interface for providing flushing medium to the cavity is provided on the machine head.

2. The flushing assembly according to claim 1, characterized in that: A flushing cavity is formed in the handpiece, a water hole communicating with the flushing cavity and the central hole is formed on the flushing head, and a water inlet channel communicating with the flushing medium interface and the flushing cavity is formed on the handpiece.

3. The flushing assembly according to claim 2, characterized in that: The flushing cavity is annular.

4. The flushing assembly according to claim 1, characterized in that: A U-shaped seal is also provided in the brazing tail copper sleeve, and a flushing water leakage chamber is formed between the U-shaped seal in the brazing tail copper sleeve and the U-shaped seal at the tail of the flushing head.

5. The flushing assembly according to claim 4, characterized in that: An annular water return cavity is formed on the inner wall of the machine head outside the abutment between the shank copper sleeve and the flushing head. The flushing water leakage chamber is connected to the water return cavity. A plurality of drainage channels connected to the water return cavity are provided on the machine head.

6. The flushing assembly according to claim 5, characterized in that: The shank copper sleeve is surrounded by a plurality of drain ports connected to the water return chamber, and the flushing water in the flushing water leakage chamber is discharged through the drain ports, the water return chamber and the drainage channel.

7. The flushing assembly according to claim 5, characterized in that: The machine head is provided with a first oil filling port and a first oil filling plug arranged in the first oil filling port, and the first oil filling port is communicated with the return water chamber to lubricate the area between the U-shaped seal in the shank copper sleeve and the U-shaped seal at the tail of the flushing head.

8. The flushing assembly according to claim 1, characterized in that: The machine head is provided with a second oil filling port and a second oil filling plug arranged in the second oil filling port, and the second oil filling port is communicated with the flushing head and the abutting surface of the machine head copper sleeve.

9. The flushing assembly according to claim 1, characterized in that: The head and tail of the flushing head are both provided with sealing rings for sealing with the machine head.

10. The flushing assembly according to claim 1, characterized in that: The head of the machine head is provided with a protective cover for the shank to pass through.

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