Drill shank rotation structure of hydraulic rock drill
By using hydraulic oil to leak into the lubrication chamber in the hydraulic rock drill, automatic lubrication of the meshing area of the large gear and pinion is achieved, and the problem of repeated injection of butter in each shift in the prior art is solved, and the working efficiency is improved.
Patent Information
- Application Number
- CN202421980726.1
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-08-15
- Publication Date
- 2025-06-17
- Estimated Expiration
- 2034-08-15
AI Technical Summary
In existing hydraulic rock drills, the meshing area of large gears and pinion gears requires repeated injection of butter for each shift to achieve lubrication, which is more cumbersome.
The hydraulic oil that drives the rotation of the cycloid motor leaks into the lubrication chamber, lubrication of the meshing area of the large gear and pinion gear is achieved.
It effectively solves the cumbersome problem of repeated injection of butter for each shift, realizes automatic lubrication of the meshing area of large gears and pinions, and improves work efficiency.
Smart Images
Figure CN222991445U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to a rotary structure of a shank end of a hydraulic rock drill, belonging to the technical field of hydraulic rock drills. Background Art
[0002] A rock drill works according to the impact crushing principle. During operation, the impact piston makes high-frequency reciprocating motions and continuously impacts the shank end. Under the action of the impact force, the head of the shank end crushes the rock and drills into a certain depth, forming a dent. After the impact piston retracts, the shank end rotates by a certain angle. When the piston moves forward and impacts the shank end again, a new dent is formed. The fan-shaped rock block between the two dents is sheared by the horizontal component force generated on the shank end. The impact piston continuously impacts the shank end, and compressed air or pressure water is continuously input from the central hole of the shank end to discharge the rock slag out of the hole, thus forming a circular drill hole with a certain depth.
[0003] The rotation of the shank end needs to be driven by a rotary structure, and extra yellow grease needs to be added at the meshing part of the large gear and the small gear to achieve lubrication. Therefore, the operation of injecting yellow grease needs to be repeated in each shift, which is rather cumbersome. Summary of the Utility Model
[0004] The purpose of the utility model is to provide a rotary structure of a shank end of a hydraulic rock drill, which uses the hydraulic oil leaking from the driving cycloid motor to the lubrication chamber to lubricate the meshing area of the large gear and the small gear, and solves the problem that it is rather cumbersome to repeat the injection of yellow grease in each shift to lubricate the meshing area of the large gear and the small gear in the existing hydraulic rock drill.
[0005] In order to achieve the above purpose, the technical solution adopted by the utility model is as follows:
[0006] A rotary structure of a shank end of a hydraulic rock drill includes an intermediate body, a gear box cover installed at the head of the intermediate body, and a shank end that penetrates through the gear box cover and extends into the intermediate body, and is relatively slidable and rotatable with respect to the gear box cover and the intermediate body; it also includes a cycloid motor, a small gear and a large gear;
[0007] A first chamber for accommodating the large gear is formed between the intermediate body and the gear box cover, and a second chamber for accommodating the small gear is formed on the intermediate body; the small gear is rotatably arranged in the second chamber, and the large gear is rotatably embedded in the first chamber and separates the first chamber from the second chamber;
[0008] There is no rotational fit between the tail of the shank end and the large gear, and it will not separate from the large gear after being impacted by the impact piston; the large gear and the small gear are meshed with each other, and the cycloid motor is installed on the intermediate body corresponding to the second chamber, and is used to drive the small gear to rotate forward or backward, and then drive the large gear and the shank end to rotate synchronously;
[0009] A lubricating chamber is formed between the large gear and the second chamber, and the lubricating chamber is communicated with the leakage oil passage of the hydraulic rock drill; the hydraulic oil leaked from the cycloid motor is driven into the lubricating chamber to lubricate the small gear and the large gear and is led out through the leakage oil passage.
[0010] Preferably, a triangular sleeve is embedded in the head cavity of the large gear, and there is no rotational fit between the triangular sleeve and the large gear; the tail of the drill steel penetrates through the triangular sleeve and a anti-disengagement part is formed at the end to prevent the drill steel from disengaging from the triangular sleeve after being impacted.
[0011] Preferably, the gearbox cover is connected to the head of the hydraulic rock drill, and a stop ring for preventing the axial displacement of the triangular sleeve is embedded at the tail of the head.
[0012] Preferably, two needle roller bearings are arranged in the second chamber, and both ends of the small gear penetrate through the corresponding needle roller bearings on each side.
[0013] Preferably, a gear pad for preventing the small gear from shifting is arranged in the second chamber and inserted into the small gear.
[0014] Preferably, two tapered bearings are arranged in the intermediate body located in the lubricating chamber, and both ends of the large gear penetrate through the corresponding tapered bearings on each side.
[0015] Preferably, both ends of the large gear are in contact with the inner wall of the cavity of the intermediate body located outside the lubricating chamber, and a Gleitring for preventing the lubricating oil in the lubricating chamber from leaking and a plurality of guide rings for guiding the large gear are arranged at the contact surface.
[0016] Preferably, a buffer assembly is further included, and the buffer assembly includes a rear stop sleeve for the drill steel and a buffer piston;
[0017] The rear stop sleeve for the drill steel is embedded in the tail cavity of the large gear and abuts against the tail of the drill steel to limit the axial displacement of the drill steel backward;
[0018] An annular buffer cavity is formed radially in the intermediate body located behind the large gear, and the buffer piston is embedded in the head cavity of the intermediate body and closes the buffer cavity;
[0019] The buffer cavity is filled with hydraulic oil that can push the buffer piston to axially displace forward to abut against the rear stop sleeve for the drill steel; when the drill steel rebounds, it impacts the rear stop sleeve for the drill steel and acts on the buffer piston, and the buffer piston is axially displaced backward by the impact of the rear stop sleeve for the drill steel and extrudes the hydraulic oil out of the buffer cavity.
[0020] Preferably, a Strseal for preventing the hydraulic oil from leaking is arranged at the contact surface between the buffer piston and the intermediate body on both sides of the buffer cavity.
[0021] Preferably, an annular air passage chamber is formed radially in the inner cavity of the intermediate body located between the large gear and the buffer piston, and an air inlet passage communicating with the air passage chamber is provided on the intermediate body. The air inlet passage is communicated with the total air inlet of the hydraulic rock drill;
[0022] After the gas enters the air passage chamber through the air inlet passage, it then enters the inner cavity of the impact piston and the inner cavity of the large gear through the gap between the large gear and the buffer piston for cooling.
[0023] The beneficial effects of the present utility model are as follows:
[0024] 1. A lubricating chamber is formed between the large gear and the second chamber, and the hydraulic oil for driving the cycloid motor can leak into the lubricating chamber to lubricate the small gear and the large gear. Therefore, it effectively solves the problem that it is more cumbersome to inject yellow grease repeatedly in the meshing area of the large gear and the small gear of the existing hydraulic rock drill every shift to achieve lubrication;
[0025] 2. A Gleitring is provided at the joint surface between the large gear and the inner cavity of the intermediate body. The third chamber is isolated from the second chamber through the Gleitring. This unique sealing design replaces the traditional skeleton oil seal and can withstand greater oil pressure; at the same time, a plurality of guide rings provided at the joint surface can effectively support the large gear, enabling it to maintain axial stability during operation and extending its service life;
[0026] 3. The stop ring and the tapered bearing can ensure the normal operation between the large gear and the drill tail; the needle bearing and the gear pad can effectively ensure the normal operation of the small gear and improve the working stability;
[0027] 4. The buffer assembly adopts a single-stage buffer design, which solves the problem that the existing double-stage buffer assembly needs to separately open an additional buffer oil port;
[0028] 5. By cooling the components with the gas that enters the air passage chamber through the air inlet passage and then enters the inner cavity of the impact piston and the inner cavity of the large gear through the gap between the large gear and the buffer piston, the working temperature can be reduced and the service life of the components can be guaranteed.
[0029] 6. Using the intermediate body to replace the original organic body + gearbox structure can reduce the use of parts, lower the processing difficulty and cost, and ensure the installation concentricity. Description of the Drawings
[0030] Figure 1 It is a sectional view of the rotary structure;
[0031] Figure 2 It is a sectional view of the intermediate body;
[0032] Figure 3 It is a schematic diagram of the three-sided sleeve structure;
[0033] Figure 4 It is a cross-sectional view of a hydraulic rock drill with a slewing structure.
[0034] The meanings of the main reference numerals in the figure are as follows:
[0035] 1. Intermediate body, 2. Gearbox cover, 3. Tool shank, 4. Cycloid motor, 5. Pinion, 6. Gear, 7. Needle bearing, 8. Gear pad, 9. Taper bearing, 10. Triangular sleeve, 11. Drill head, 12. Stop ring, 13. Lubrication chamber, 14. Leakage oil passage, 15. Glyd ring, 16. Guide ring, 17. Rear retaining sleeve of tool shank, 18. Buffer piston, 19. Buffer chamber, 20. Stem seal, 21. Oil inlet passage, 22. Air passage, 23. Air inlet passage, 24. Accumulator. Specific embodiments
[0036] The following specifically introduces the present utility model in conjunction with the accompanying drawings and embodiments.
[0037] This embodiment provides a tool shank slewing structure of a hydraulic rock drill, as Figures 1-4 shown, which includes an intermediate body 1, a gearbox cover 2 installed at the head of the intermediate body 1, and a tool shank 3 that penetrates through the gearbox cover 2 and extends into the intermediate body 1, and is relatively slidable and rotatable with the gearbox cover 2 and the intermediate body 1; it also includes a cycloid motor 4, a pinion 5 and a gear 6.
[0038] A first chamber for accommodating the gear 6 is formed between the intermediate body 1 and the gearbox cover 2, and a second chamber for accommodating the pinion 5 is formed on the intermediate body 1; the pinion 5 is rotatably arranged in the second chamber, and two needle bearings 7 are arranged in the second chamber, and both ends of the pinion 5 penetrate through the corresponding needle bearings 7 on the side; at the same time, a gear pad 8 for preventing the pinion 5 from shifting is arranged in the second chamber and inserted into the pinion 5. The gear 6 is rotatably embedded in the first chamber and separates the first chamber from the second chamber, and two taper bearings 9 are arranged in the intermediate body 1 located in the lubrication chamber 13, and both ends of the gear 6 penetrate through the corresponding taper bearings 9 on the side.
[0039] A triangular sleeve 10 is embedded in the head cavity of the gear 6, and there is no rotational fit between the triangular sleeve 10 and the gear 6 (that is, no relative rotation can occur between the triangular sleeve 10 and the gear 6); the tail of the tool shank 3 penetrates through the triangular sleeve 10 and a anti-disengagement portion for preventing the tool shank 3 from disengaging from the triangular sleeve 10 after being impacted is formed at the end, and at the same time, there is no rotational fit between the tail of the tool shank 3 and the gear 6 (that is, no relative rotation can occur between the triangular sleeve 10 and the tool shank 3 either). The gearbox cover 2 is connected to the drill head 11 of the hydraulic rock drill, and a stop ring 12 for preventing the axial displacement of the triangular sleeve 10 is embedded at the tail of the drill head 11.
[0040] The large gear 6 meshes with the small gear 5. The cycloid motor 4 is installed on the intermediate body 1 corresponding to the second chamber. The actuating shaft of the cycloid motor 4 is drivingly connected to the small gear 5 (the end of the actuating shaft of the cycloid motor 4 is inserted into the inner cavity of the end of the small gear 5, and meshing teeth are formed at the end of the actuating shaft and in the inner cavity of the end of the small gear 5), so as to drive the small gear 5 to rotate forward or backward and then drive the large gear 6 and the drill steel tail 3 to rotate synchronously. In actual application, the cycloid motor 4 realizes forward or backward rotation by changing the flow direction of the inlet and outlet oil. The driving mode of the cycloid motor 4 is prior art and will not be elaborated here.
[0041] Since the cycloid motor 4 is directly installed on the intermediate body 1, the hydraulic oil for driving the cycloid motor 4 to rotate can directly leak into the second chamber. And a lubricating chamber 13 is formed between the large gear 6 and the second chamber, and the lubricating chamber 13 is also connected to the leakage oil passage 14 of the hydraulic rock drill. Further, both ends of the large gear 6 are in contact with the inner wall of the cavity of the intermediate body 1 located outside the lubricating chamber 13, and at the contact surface, a Gleitring 15 for preventing the lubricating oil in the lubricating chamber 13 from leaking and a plurality of guide rings 16 for guiding the large gear 6 are provided. The hydraulic oil for driving the cycloid motor 4 leaks into the lubricating chamber 13 and can then lubricate the meshing area of the small gear 5 and the large gear 6, and finally can be led out through the leakage oil passage 14.
[0042] After the drill steel tail 3 is impacted and acts on the rock, a reaction force will be generated to make the drill steel tail 3 move towards the inside of the machine body. In order to reduce this acting force and prevent damage to the machine body, a buffer assembly is added to the slewing structure. The buffer assembly includes a drill steel tail rear retaining sleeve 17 and a buffer piston 18; the drill steel tail rear retaining sleeve 17 is embedded in the tail cavity of the large gear 6 and abuts against the tail of the drill steel tail 3 to limit the axial displacement of the drill steel tail 3 backward; an annular buffer cavity 19 is formed radially in the intermediate body 1 behind the large gear 6, and the buffer piston 18 is embedded in the head cavity of the intermediate body 1 and closes the buffer cavity 19; the buffer cavity 19 is filled with hydraulic oil that can push the buffer piston 18 to axially displace forward to abut against the drill steel tail rear retaining sleeve 17; when the drill steel tail 3 rebounds, it impacts the drill steel tail rear retaining sleeve 17 and acts on the buffer piston 18, and the buffer piston 18 is impacted by the drill steel tail rear retaining sleeve 17 and axially displaces backward and squeezes the hydraulic oil out of the buffer cavity 19. At the same time, at the contact surface between the buffer piston 18 and the intermediate body 1 on both sides of the buffer cavity 19, a Step seal 20 for preventing the leakage of hydraulic oil is provided.
[0043] In actual application, the inlet and outlet oil of the buffer cavity 19 are both realized through the oil inlet passage 21 on the hydraulic rock drill, and the oil inlet passage 21 is also connected to an accumulator installed on the body of the hydraulic rock drill. Then, when the buffer piston 18 is impacted by the drill steel tail rear retaining sleeve 17 and axially displaces backward, the hydraulic oil squeezed out of the buffer cavity 19 will be led to the liquid phase side of the accumulator through the oil inlet passage 21, thereby realizing buffering.
[0044] When the hydraulic rock drill is working, some components at the rotary structure will heat up. Therefore, an annular air passage 22 is formed radially in the inner cavity of the intermediate body 1 between the large gear 6 and the buffer piston 18, and the intermediate body 1 is provided with an air inlet passage 23 communicating with the air passage 22. The air inlet passage 23 is communicated with the total air inlet of the hydraulic rock drill. In this way, the introduced gas can enter the air passage 22 through the air inlet passage 23, and then enter the inner cavity of the impact piston and the inner cavity of the large gear 6 through the gap between the large gear 6 and the buffer piston 18 for cooling.
[0045] In actual application, front and rear sealing components for isolating oil and gas can be arranged in the hydraulic rock drill. At the same time, air passageways can be further opened to direct the gas to the connection surfaces between the cycloid motor 4 and the intermediate body 1, between the intermediate body 1 and the gearbox cover 2, and between the gearbox cover 2 and the drill head 11, so as to blow the dust infiltrated at the connection surfaces by the gas.
[0046] The above are only the preferred embodiments of the utility model patent. It should be noted that for those of ordinary skill in the art, without departing from the principle of the utility model patent, several improvements and refinements can be made, and these improvements and refinements should also be regarded as the protection scope of the utility model patent.
Claims
1. A hydraulic rock drill tail rotary structure, characterized in that: It includes an intermediate body, a gear box cover installed on the head of the intermediate body, and a shank inserted through the gear box cover and extending into the intermediate body, and is relatively slidable and rotatable with the gear box cover and the intermediate body; it also includes a cycloidal motor, a small gear and a large gear; A first chamber for accommodating a large gear is formed between the intermediate body and the gear box cover, and a second chamber for accommodating a small gear is formed on the intermediate body; the small gear is rotatably arranged in the second chamber, and the large gear is rotatably embedded in the first chamber and isolates the first chamber from the second chamber; There is no rotational fit between the tail of the shank and the large gear, and the shank will not separate from the large gear after being impacted by the impact piston; the large gear and the small gear mesh with each other, and the cycloidal motor is installed on the intermediate body corresponding to the second chamber, which is used to drive the small gear to rotate forward or reverse, and then drive the large gear and the shank to rotate synchronously; A lubrication chamber is formed between the large gear and the second chamber, and the lubrication chamber is connected to the leakage oil channel of the hydraulic rock drill; the hydraulic oil driven by the cycloid motor leaks into the lubrication chamber to lubricate the small gear and the large gear and is discharged through the leakage oil channel.
2. The hydraulic rock drill tail rotary structure according to claim 1, characterized in that: A triangular sleeve is embedded in the head cavity of the large gear, and the triangular sleeve and the large gear are non-rotationally matched; the tail of the drill tail is inserted through the triangular sleeve and an anti-dropping part is formed at the end to prevent the drill tail from falling out of the triangular sleeve after being hit.
3. The hydraulic rock drill tail rotary structure according to claim 1, characterized in that: The gear box cover is connected to the head of the hydraulic rock drill, and a stop ring is embedded at the tail of the head to prevent the axial displacement of the triangular sleeve.
4. The hydraulic rock drill tail rotary structure according to claim 1, characterized in that: Two needle bearings are arranged in the second chamber, and the two ends of the pinion gear are inserted through the needle bearings on the corresponding sides.
5. The hydraulic rock drill tail rotary structure according to claim 1, characterized in that: A gear washer inserted into the pinion gear to prevent the pinion gear from shifting is arranged in the second cavity.
6. The hydraulic rock drill tail rotary structure according to claim 1, characterized in that: Two tapered bearings are arranged in the intermediate body located in the lubrication chamber, and the two ends of the large gear are inserted through the tapered bearings on the corresponding sides.
7. The hydraulic rock drill tail rotary structure according to claim 1, characterized in that: Both ends of the large gear are fitted with the inner wall of the intermediate body located outside the lubrication chamber, and Gly rings for preventing leakage of lubricating oil in the lubrication chamber and multiple guide rings for guiding the large gear are arranged on the fitting surfaces.
8. The hydraulic rock drill tail rotary structure according to claim 1, characterized in that: It also includes a buffer assembly, which includes a rear stopper sleeve of the shank end and a buffer piston; The rear stopper sleeve of the shank tail is embedded in the tail cavity of the large gear and abuts against the tail of the shank tail to limit the axial displacement of the shank tail backwards; An annular buffer cavity is formed radially in the intermediate body located at the rear side of the large gear, and a buffer piston is embedded in the head cavity of the intermediate body and closes the buffer cavity; The buffer chamber is filled with hydraulic oil that can push the buffer piston to move axially forward to abut against the rear stop sleeve of the shank; when the shank rebounds, it hits the rear stop sleeve of the shank and acts on the buffer piston. The buffer piston is hit by the rear stop sleeve of the shank and moves axially backward to squeeze the hydraulic oil out of the buffer chamber.
9. The hydraulic rock drill tail rotary structure according to claim 8, characterized in that: Step seals for preventing hydraulic oil leakage are arranged at the fitting surfaces of the buffer piston and the intermediate body on both sides of the buffer cavity.
10. The hydraulic rock drill tail rotary structure according to claim 8, characterized in that: The inner cavity of the intermediate body between the large gear and the buffer piston is formed with an annular air cavity along the radial direction, and the intermediate body is provided with an air intake channel connected with the air cavity, and the air intake channel is connected with the total air intake of the hydraulic rock drill; After the gas enters the air chamber through the air intake passage, it enters the inner cavity of the impact piston and the inner cavity of the large gear through the gap between the large gear and the buffer piston for cooling.