Drilling drive system

Abstract

The present invention relates to the field of coal mine drilling, and discloses a drilling drive system, including a main shaft, a brake assembly, a gearbox, a chuck and a main power source, wherein the output shaft of the main power source meshes with the gearbox to drive the main shaft to rotate, the gearbox includes a gear shaft and a multi-stage transmission gear, a transmission shaft connected to the gear shaft is provided inside the brake assembly, and the brake assembly can perform rotational braking on the transmission shaft, an active drill rod is installed at the end of the main shaft, a receiving hole for the active drill rod to pass through is provided in the main shaft, a two-way joint is detachably connected at the end of the active drill rod, a chuck is arranged at the end of the main shaft, and a chuck pressure control system for controlling whether the chuck limits the active drill rod is provided. The drilling drive system is provided, which is easy to disassemble the active drill rod and has a long service life of the active drill rod.

Description

Technical Field

[0001] The invention relates to the field of coal mine drilling rigs, and in particular to a drilling drive system. Background Art

[0002] The power head is used to transmit the rotation and propulsion power required for assembly and disassembly to the drill rod. Most existing automatic drilling rigs use active drill rods to connect the power head and the drill rod. The emergence of automated directional drilling rigs integrates the needs of two drill rod connection methods: the chuck and the active drill rod: during normal automatic drilling, the active drill rod is used to load and unload ordinary drill rods from the front end of the power head; when using salvage drilling tools, the active drill rod is removed and the salvage drill rod is loaded and unloaded from the rear end of the power head using the chuck. The outer diameters of ordinary drill rods and salvage drill rods used in normal drilling are generally different, and the active drill rod often needs to be disassembled.

[0003] The existing technology is not good at disassembling and assembling quickly. When the active drill rod needs to be disassembled and switched to the chuck clamping working condition, the water braid must be removed from the rear end first, and then the end cover that fixes the active drill rod must be removed from the front end. Finally, the combination of the active drill rod and the connecting shaft must be pulled out from the front end of the chuck before the chuck can be used to clamp the drill rod for construction. Since the space from the front end of the chuck to the clamp is very limited and is generally located in the middle of the drilling rig, it is inconvenient to pull out the active drill rod and the connecting shaft, which can easily affect the construction efficiency. If the connecting shaft is removed separately from the rear end, since it is located inside the main shaft of the power head, it is not convenient to use larger manual tools such as pipe clamps, and disassembly is time-consuming. It may also require the removal of more peripheral parts. Similarly, when switching from the chuck clamping condition back to the active drill rod connection condition, the installation is also time-consuming. In addition, the active drill rod is a wearing part and is consumed in large quantities during the use of the drilling rig. Its service life directly affects the overall drilling efficiency and the maintenance cost of the drilling rig. It is a key part that drilling rig users pay close attention to. Therefore, it is necessary to provide a drilling drive system that is easy to disassemble the active drill rod and has a long service life of the active drill rod. Summary of the invention

[0004] The present invention intends to provide a drilling drive system, so as to provide a drilling drive system which is easy to disassemble an active drill rod and has a long service life of the active drill rod.

[0005] To achieve the above-mentioned purpose, the present invention adopts the following technical scheme: a drilling drive system, including a main shaft, a brake assembly, a gearbox, a chuck and a main power source, the output shaft of the main power source is meshed with the gearbox to drive the main shaft to rotate, the gearbox includes a gear shaft and a multi-stage transmission gear, a transmission shaft connected to the gear shaft is provided inside the brake assembly, the brake assembly can perform rotational braking on the transmission shaft, an active drill rod is installed at the end of the main shaft, a receiving hole for the active drill rod to pass through is opened in the main shaft, the end of the active drill rod is also detachably connected with a two-way joint, the chuck is arranged at the end of the main shaft, and a chuck pressure control system is provided to control whether the chuck limits the active drill rod.

[0006] The beneficial effects of this program are:

[0007] A transmission shaft connected to the gear shaft is provided inside the brake assembly. The brake assembly can perform rotational braking on the transmission shaft to cooperate with the directional drilling and drill rod connection and disconnection conditions of the drilling rig. When the active drill rod needs to be inspected and replaced, since a receiving hole for the active drill rod to pass through is opened in the main shaft, the staff can directly slide the active drill rod in the receiving hole and take it out from the rear of the main shaft, thereby increasing the speed of disassembly of the active drill rod. At the same time, the space at the rear end of the main shaft is relatively ample. If the active drill rod is taken out from the front of the main shaft according to the traditional method, on the one hand, the flange plate must be disassembled and tightened, and on the other hand, the space in the front is relatively limited, and it is inconvenient to install and remove the active drill rod. The above-mentioned arrangement can facilitate the staff to assemble the active drill rod and then reinstall it into the main shaft, thereby increasing the installation speed of the active drill rod. By setting the brake assembly, the start and stop of the active drill rod can be adjusted in time.

[0008] In the present technical solution, the end of the active drill rod is also detachably connected with a two-way joint. When the thread on one side of the two-way joint is worn to a certain extent, the two-way joint can be removed and the installation direction can be reversed. One end of the two-way joint is fixedly connected to the active drill rod by glue, so that the service life of the active drill rod is equivalent to twice that of the previous integral active drill rod, and there is no need to replace the rod body, which can save a lot of installation time and use costs, and can play an emergency role when constructing in some places where it is inconvenient to repair and replace the active drill rod.

[0009] Preferably, as an improvement, the chuck pressure control system comprises a pressure reducing valve, an electromagnetic reversing valve, a hydraulically controlled reversing valve, a main pump and an auxiliary pump; the electromagnetic reversing valve is a three-position four-way electromagnetic reversing valve with port A, port B, port P and port T, the hydraulically controlled reversing valve has port P, port T, port A and a hydraulically controlled port, the chuck has a control oil port, the port A of the hydraulically controlled reversing valve is connected to the control oil port of the chuck, and the main pump is connected to the port P of the hydraulically controlled reversing valve; the oil circuit of the auxiliary pump is divided into two streams, one is connected to the port P of the hydraulically controlled reversing valve, and the other is connected to the port P of the electromagnetic reversing valve through the pressure reducing valve; the oil drain port of the pressure reducing valve is connected to the port T of the electromagnetic reversing valve and drains oil; the oil output of the port A of the electromagnetic reversing valve is divided into two streams, one is connected to the port P of the hydraulically controlled reversing valve, and the other is connected to the hydraulically controlled port of the hydraulically controlled reversing valve; the port B of the electromagnetic reversing valve is connected to the port T of the hydraulically controlled reversing valve.

[0010] The beneficial effects are as follows: the hydraulically controlled reversing valve is a two-position three-way hydraulically controlled reversing valve, which can automatically switch the oil flow direction of the oil by controlling the oil circuit, and realizes precise adjustment of the chuck pressure through coordinated control of the electromagnetic reversing valve and the hydraulically controlled reversing valve to adapt to the needs of different working conditions. In normal drilling and salvage operations, the oil flow direction of the oil can be quickly switched to ensure that the chuck is adjusted to the required state in the shortest time, thereby improving work efficiency.

[0011] Preferably, as an improvement, the main pump flows to the P port of the hydraulically controlled reversing valve through the first one-way valve.

[0012] The beneficial effect is that the one-way valve can control the one-way flow of oil to ensure the smooth operation of the oil circuit.

[0013] Preferably, as an improvement, the oil circuit of the auxiliary pump is connected to the P port of the hydraulically controlled reversing valve via the second one-way valve.

[0014] Preferably, as an improvement, the A port of the electromagnetic reversing valve is connected to the P port of the hydraulically controlled reversing valve via a third one-way valve.

[0015] Preferably, as an improvement, the pressure reducing valve is a fixed value pressure reducing valve.

[0016] The beneficial effects are: the oil pressure can be adjusted to the set pressure, and a low-pressure circuit or a control oil circuit can be formed.

[0017] Preferably, as an improvement, the electromagnetic reversing valve has a Y1 position and a Y2 position.

[0018] Preferably, as an improvement, in the working condition, the Y1 and Y2 positions lose power, the pressure oil from the main pump reaches the P port of the hydraulically controlled reversing valve and is cut off, and the pressure oil from the auxiliary pump flows through the pressure reducing valve and reaches the P port of the electromagnetic reversing valve and is cut off.

[0019] The beneficial effects are as follows: when the left position Y1 and the right position Y2 of the electromagnetic reversing valve are both in the power-off state, the electromagnetic reversing valve is in the middle position, and the hydraulic control reversing valve works in the right position under the action of the spring force. When the pressure oil of the main pump passes through the one-way valve to reach the P port of the hydraulic control reversing valve, the oil is cut off. At the same time, a stream of pressure oil from the auxiliary pump flows through the one-way valve to reach the P port of the hydraulic control reversing valve, and the oil is cut off; another stream of pressure oil from the auxiliary pump flows through the pressure reducing valve to reach the P port of the electromagnetic reversing valve and is cut off. The pressure oil in the chuck returns through the right position of the hydraulic control reversing valve and the middle position of the electromagnetic reversing valve, and the chuck is in a loosened state. At the same time, the control oil of the hydraulic control reversing valve leaks through the middle position of the electromagnetic reversing valve.

[0020] Preferably, as an improvement, in working condition two, Y2 is energized, and the pressure oil from the main pump reaches the P port of the hydraulically controlled reversing valve and is cut off; one stream of pressure oil from the auxiliary pump reaches the P port of the hydraulically controlled reversing valve and is cut off, and the other stream flows through the pressure reducing valve, the electromagnetic reversing valve, and reaches the control port of the chuck through the hydraulically controlled valve.

[0021] The beneficial effects are as follows: when the electromagnetic reversing valve right position Y2 is energized, the electromagnetic reversing valve is in the right position working state, the hydraulic control reversing valve is in the right position working state under the action of the spring force, the pressure oil from the main pump flows through the one-way valve I to the P port of the hydraulic control reversing valve and is cut off, and the control oil of the hydraulic control reversing valve leaks through the right position of the electromagnetic reversing valve. One stream of the pressure oil from the auxiliary pump passes through the P port of the one-way valve hydraulic control reversing valve, and the oil is cut off; the other stream of oil is reduced to the set pressure through the pressure reducing valve, and then the pressure oil flows through the right position of the electromagnetic reversing valve, and then passes through the right position of the hydraulic control reversing valve to reach the chuck, and the chuck is in a low-pressure clamping state.

[0022] Preferably, as an improvement, in working condition three, Y1 is energized, and the pressure oil from the main pump flows into the control port of the chuck through the hydraulically controlled reversing valve, and one stream of pressure oil from the auxiliary pump reaches the control port of the hydraulically controlled reversing valve through the electromagnetic reversing valve to switch the working state of the hydraulically controlled reversing valve, and the other stream flows into the control port of the chuck through the hydraulically controlled reversing valve, and the hydraulic oils from the main pump and the auxiliary pump merge.

[0023] The beneficial effects are as follows: the chuck is in a high-pressure clamping state. When the electromagnetic reversing valve is in the left position and Y1 is energized, the electromagnetic reversing valve is in the left position working state. Under the action of the control oil, the hydraulic control reversing valve is in the left position working state. The pressure oil from the main pump flows through the one-way valve = and finally flows into the chuck through the left position of the hydraulic control reversing valve. The pressure oil from the auxiliary pump is divided into two oil circuits. One oil circuit is reduced in pressure by the pressure reducing valve, flows through the left position of the electromagnetic reversing valve to the control port of the hydraulic control reversing valve, so that the hydraulic control reversing valve is reversed and in the left position working state; the other oil circuit passes through the one-way valve and finally flows into the chuck through the left position of the hydraulic control reversing valve. In this state, the main and auxiliary pumps merge to form a high-pressure oil source, so that the chuck is in a high-pressure clamping state.

[0024] Preferably, as an improvement, the brake assembly includes a brake cover, a clamping piston and a releasing piston, a sliding shaft is provided inside the brake cover, one end of the transmission shaft extends into the center of the clamping piston, a plurality of cava are distributed circumferentially of the transmission shaft, the clamping piston is sleeved on the cava and can move axially, the surface of the cava away from the transmission shaft is an inclined surface, the surface of the clamping piston opposite to the cava is a slope surface matching the inclined surface of the cava, the clamping piston can slide through the cava to clamp the transmission shaft, the releasing piston is slidingly sleeved on the sliding shaft and can push the clamping piston to release the clamping.

[0025] The beneficial effects are as follows: the surface of the clamping piston opposite to the slip is a slope surface that matches the slope surface of the slip, and the clamping piston can slide so that the slope surface inside it contacts the slope surface of the slip, and the transmission shaft is clamped by radial movement of the slip, thereby limiting the rotation of the transmission shaft. The transmission shaft can be quickly clamped and released by the axial sliding of the clamping piston and the radial movement of the slip, and the cooperation between the slope surface and the slope surface provides a stable clamping force, ensuring that the transmission shaft will not slide during operation, ensuring the reliability of the clamping of the transmission shaft, and being adaptable to transmission shafts of different diameters. Even if the surface of the transmission shaft is worn, stable clamping can be achieved by extending the sliding distance of the clamping piston. It has strong versatility and can be applied to various types of drilling rig power heads.

[0026] Preferably, as an improvement, the brake cover is provided with oil inlet one and oil inlet two, and a first oil chamber is formed between the side of the release piston away from the clamping piston and the brake cover, and the oil inlet one can provide hydraulic oil to the first oil chamber, and a second oil chamber is provided on the side of the clamping piston away from the release piston, and the oil inlet two can provide hydraulic oil to the second oil chamber.

[0027] The beneficial effects are as follows: the pressure oil enters the second oil chamber from the oil inlet port 2, pushing the clamping piston to move toward the direction close to the slip, so that the internal slope surface contacts the inclined surface of the slip, thereby pushing the slip to move inward and limiting the radial displacement of the slip, thereby clamping the transmission shaft and achieving transmission shaft braking; the pressure oil enters the first oil chamber from the oil inlet port 1, pushing the release piston to move, and its end surface pushes the clamping piston to move away from the slip, releasing the radial displacement restriction on the slip, and thus releasing the rotation restriction on the transmission shaft. The automatic control of the brake assembly is achieved through the hydraulic system, which improves the automation level and efficiency of the operation. The hydraulic pressure can provide stable and adjustable pressure to ensure the accuracy of the clamping and releasing processes, and the hydraulic pressure has high stability and reliability, ensuring that the brake assembly can work stably under various working conditions, reducing the failure rate and maintenance costs.

[0028] Preferably, as an improvement, it also includes a water braid part for providing pressure fluid to the active drill rod, the water braid part includes a connecting shaft, a core shaft and a water inlet assembly, the core shaft and the connecting shaft are both hollow shafts, the core shaft is fixedly connected and communicated with the connecting shaft, the other end of the connecting shaft is connected to the active drill rod, the core shaft is communicated and rotatably connected with the water inlet assembly, a bearing seat is provided to support the core shaft, and a core shaft support bearing is provided in the bearing seat and is sleeved on the outer periphery of the core shaft.

[0029] The beneficial effects are as follows: by setting a connecting shaft and a water braid, the core shaft is fixedly connected and communicated with the connecting shaft, and the other end of the connecting shaft is connected to the active drill rod, so that the drilling medium flowing into the water braid is transmitted to the active drill rod, and the active drill rod and the water braid are connected. In this technical solution, the core shaft is connected to the active drill rod and rotates together with the active drill rod during operation. The core shaft support bearing can ensure smooth rotation of the core shaft, reduce friction and wear during the rotation process, and extend the service life of the equipment. Through the hollow design of the connecting shaft and the core shaft, the pressure fluid can be smoothly transmitted from the water inlet assembly to the active drill rod, ensuring that the drilling medium can be stably and continuously supplied, thereby improving the drilling efficiency.

[0030] Preferably, as an improvement, one end of the active drill rod is a male joint, and the other end is a female joint, the male joint and the two-way joint are detachably connected, a stopper is provided on the outer periphery of the active drill rod, the outer periphery cross-section of the stopper is polygonal, an end cover is provided on the end of the main shaft, the end cover includes a front end cover, the front end cover is fixed on the chuck, a limiting opening is opened on the front end cover, and the front end cover limits the rotation of the stopper through the limiting opening.

[0031] The beneficial effects are as follows: when the main shaft drives the end cover to stop rotating, the limit opening of the front end cover stops rotating synchronously, and the limit opening limits the rotation of the stop part, so that the active drill rod can stop rotating. The above method realizes the limitation of the rotation of the active drill rod, but does not limit the axial sliding of the active drill rod, so that the active drill rod can float axially for a certain distance during operation, which can effectively alleviate the axial impact of the drill rod during the threaded connection and disassembly process, thereby protecting the active drill rod and other connecting parts and extending the service life of the equipment; when the active drill rod produces axial floating, it can reduce the impact force on the water braid part, reduce the wear of the water braid part, and improve its overall durability and reliability.

[0032] Preferably, as an improvement, a limiting section is provided between the female joint and the stop block, the limiting section is located between the chucks, and when the chucks are clamped to the limit position, there is still a gap between the chucks and the outer periphery of the limiting section.

[0033] The beneficial effects are as follows: when the chuck moves to the extreme position, there is still a gap between the chuck and the outer periphery of the limit section, so that the limit section can slide axially along the chuck, and the active drill rod can float axially for a certain distance, so that the clamping force of the chuck will not directly act on the active drill rod, thereby avoiding the active drill rod directly bearing the strong clamping force of the chuck, and avoiding the metal fatigue deformation of the active drill rod during the reciprocating rotation process, thereby reducing fatigue damage and increasing the service life of the active drill rod; due to the axial floating design of the active drill rod, the impact force borne by the water braid during operation is reduced, which makes the force on the water braid more uniform.

[0034] Preferably, as an improvement, the length of the limiting section is greater than the width of the chuck.

[0035] The beneficial effect is that the length of the limit section is greater than the clamping width of the chuck, so that the active drill rod has a certain floating distance in the chuck, so as to alleviate the axial impact generated when the active drill rod is connected or disconnected with the drill rod, thereby protecting the active drill rod.

[0036] Preferably, as an improvement, a water inlet hole is opened at the end of the core shaft, and the water inlet assembly includes a shell, a water supply chamber connected to the water inlet hole is provided in the shell, the water supply chamber is connected to the water inlet hole, and an external thread for threaded connection with the rear end of the active drill rod is provided at a section of the connecting shaft close to the active drill rod; an internal thread for threaded connection with the core shaft is provided at one end of the connecting shaft close to the water braid portion.

[0037] Preferably, as an improvement, the water braid part is fixed to the gearbox through a connecting sleeve, and the connecting sleeve includes a connecting flange, and the connecting flange is provided with a waist-shaped hole for the bolt to pass through, and the center of the connecting sleeve is also provided with a hexagonal hole that cooperates with the anti-rotation part.

[0038] Preferably, as an improvement, a gap is left between the end surface of the connecting sleeve facing the active drill rod and the end surface of the connecting shaft.

[0039] The beneficial effects of the technical solution are as follows: in a directional drilling rig power head disclosed in the existing patent (publication number: CN116905958A), when it is necessary to replace the active drill rod, the staff needs to first remove the front end cover and then unlock the active drill rod. Since one end of the connecting shaft is threadedly connected to the active drill rod, and the other end is threadedly connected to the core shaft of the water braid, when the staff rotates the active drill rod to unlock it, the active drill rod and the connecting shaft cannot be accurately unlocked, and it is possible that the connecting shaft and the core shaft of the water braid are unlocked. Since the space from the front end of the chuck to the clamp is very limited, in the narrow operating space, even if the active drill rod is taken out alone, it will bring difficulty to the staff's operation. If the connecting shaft and the core shaft of the water braid are unlocked, the staff It becomes very difficult for the workers to take out the active drill rod and the connecting shaft from the front end. At the same time, if it is necessary to switch to the chuck to clamp the salvage drill rod for work, the workers need to remove the water braid from the rear end of the gearbox, take out the water braid and the connecting shaft from the rear end of the gearbox, and then remove the end cover to take out the active drill rod. In this process, it cannot be ensured that the connecting shaft is unlocked from the active drill rod. If the connecting shaft is unlocked from the core shaft of the water braid, the workers also need to take out the active drill rod and the connecting shaft from the front end of the gearbox together before they can load the salvage drill rod into the chuck and switch to the chuck to clamp the drill rod for work. Therefore, the existing technology is very difficult to replace the active drill rod or switch the chuck to clamp the salvage drill rod for work, which seriously affects the construction efficiency.

[0040] In this solution, when the active drill rod needs to be replaced, due to the wide operating space at the rear end of the gearbox, the staff only needs to loosen the chuck first, and then take out the water braid part, the connecting shaft and the active drill rod connection as a whole from the rear end of the gearbox, so as to quickly replace the damaged active drill rod, and then install the new active drill rod, the connecting shaft and the water braid connection as a whole into the gearbox from the rear end of the gearbox, and make the active drill rod pass through the main shaft, the chuck and the front end cover in sequence, so as to quickly complete the replacement of the active drill rod, reduce the uncontrollable factors in the replacement process, and increase the construction efficiency. When it is necessary to switch to the salvage drill rod work, the staff repeats the above disassembly process. During installation, it is only necessary to install the salvage drill rod from the rear end of the gearbox into the main shaft, and pass through the chuck and the front end cover in sequence, and finally clamp the salvage drill rod through the chuck to rotate. At the same time, a part of the active drill rod of the technical solution is located in the chuck and the main shaft, so that when the main shaft drives the active drill rod to rotate through the chuck, the rotation of the active drill rod is more stable and can be more accurately docked with the drill rod. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] Figure 1 is a cross-sectional view of an embodiment of the present invention;

[0042] Figure 2 A detailed view of a brake assembly according to an embodiment of the present invention;

[0043] Figure 3 A detailed view of an active drill rod according to an embodiment of the present invention;

[0044] Figure 4 This is a detailed view of the water braid portion of an embodiment of the present invention;

[0045] Figure 5 This is a schematic diagram of the connection of the water braid part of an embodiment of the present invention;

[0046] Figure 6 It is a right side view of the connecting sleeve according to an embodiment of the present invention;

[0047] Figure 7 It is a schematic diagram of the working condition of the present invention;

[0048] Figure 8 It is a schematic diagram of the working condition of the present invention;

[0049] Fig. 9 It is a schematic diagram of the working condition of the present invention;

[0050] Fig.10 This is a schematic diagram of gluing a bidirectional joint in an embodiment of the present invention. DETAILED DESCRIPTION

[0051] The following is further described in detail through specific implementation methods:

[0052] The figure marks in the drawings of the specification include: main power source 1, active drill rod 11, male connector 111, female connector 112, anti-rotation part 113, limit section 114, main shaft 12, accommodating hole 121, front end cover 123, chuck 124, two-way joint 13, gearbox 2, brake assembly 3, brake cover 31, clamping piston 32, releasing piston 33, sliding shaft 34, slip 35, transmission shaft 36, oil inlet 1 37, oil inlet 2 38, key 39, water braid 4, connecting shaft 41, core shaft 42, housing 431, water supply chamber 432, water inlet hole 433, bearing seat 44, core shaft support bearing 45, connecting sleeve 46, waist-shaped hole 461, grease nipple 462, pressure reducing valve 51, electromagnetic reversing valve 52, hydraulically controlled reversing valve 53, oil tank 54, and one-way valve 55.

[0053] Example

[0054] The embodiment is basically as follows Figure 1-Figure 9 As shown, Figure 1 The drilling rig power head shown includes a main shaft 12, a brake assembly 3, a gearbox 2 and a main power source 1. The output shaft of the main power source 1 is meshed with the gearbox 2 to drive the main shaft 12 to rotate. The main power source 1 can be various rotary power drive devices, such as: hydraulic motor, electric motor, etc. The main power source 1 of the present application is a hydraulic motor. The gearbox 2 includes a gear shaft and a multi-stage gear. A transmission shaft 36 connected to the gear shaft is provided inside the brake assembly 3. The transmission shaft 36 is connected to the gear shaft through a key 39 and rotates synchronously. The brake assembly 3 performs rotational braking on the transmission shaft 36. An active drill rod 11 is installed at the end of the main shaft 12. A receiving hole 121 for the active drill rod 11 to pass through is opened in the main shaft 12. The end of the active drill rod 11 is also detachably connected with a two-way joint 13. A chuck pressure control system is also provided to control whether the chuck limits the active drill rod.

[0055] Chuck pressure control system, such as Figure 7-8As shown, it includes a pressure reducing valve 51, an electromagnetic reversing valve 52, a hydraulically controlled reversing valve 53, a main pump and an auxiliary pump; the electromagnetic reversing valve 52 is a three-position four-way electromagnetic reversing valve 52 with ports A, B, P and T, the hydraulically controlled reversing valve 53 has ports P, T, A and a hydraulically controlled port, the chuck 124 has a control oil port, the port A of the hydraulically controlled reversing valve 53 is connected to the control oil port of the chuck 124, the main pump is connected to the port P of the hydraulically controlled reversing valve 53; the oil circuit of the auxiliary pump The oil is divided into two streams, one of which is connected to the P port of the hydraulically controlled reversing valve 53, and the other is connected to the P port of the electromagnetic reversing valve 52 through the pressure reducing valve 51; the oil drain port of the pressure reducing valve 51 is connected to the T port of the electromagnetic reversing valve 52 and drains oil; the oil output from the A port of the electromagnetic reversing valve 52 is divided into two streams, one of which is connected to the P port of the hydraulically controlled reversing valve 53, and the other is connected to the hydraulic control port of the hydraulically controlled reversing valve 53; the B port of the electromagnetic reversing valve 52 is connected to the T port of the hydraulically controlled reversing valve 53. The hydraulically controlled reversing valve 53 is a two-position three-way hydraulically controlled reversing valve 53, which can automatically switch the oil flow direction of the oil by controlling the oil circuit. Through the coordinated control of the electromagnetic reversing valve 52 and the hydraulically controlled reversing valve 53, the chuck pressure can be accurately adjusted to meet the needs of different working states. In normal drilling and fishing operations, the oil flow direction of the oil can be quickly switched to ensure that the chuck 124 is adjusted to the required state in the shortest time, thereby improving work efficiency. The main pump flows to the P port of the hydraulically controlled reversing valve 53 through the first one-way valve 55, and the oil circuit of the auxiliary pump is connected to the P port of the hydraulically controlled reversing valve 53 through the second one-way valve 55; the A port of the electromagnetic reversing valve 52 is connected to the P port of the hydraulically controlled reversing valve 53 through the third one-way valve 55; the pressure reducing valve 51 is a fixed value pressure reducing valve 51, which can adjust the oil pressure to 6Mpa in this embodiment; in this embodiment, the electromagnetic reversing valve 52 has Y1 and Y2 positions, and also includes an oil tank 54 for supplying oil to the main pump and the auxiliary pump.

[0056] like Figure 7 As shown, in the working condition, the Y1 and Y2 positions are de-energized, the pressure oil from the main pump reaches the P port of the hydraulic control reversing valve 53 and is cut off, and the pressure oil from the auxiliary pump flows through the pressure reducing valve 51 to reach the P port of the electromagnetic reversing valve 52 and is cut off. When the left position Y1 and the right position Y2 of the electromagnetic reversing valve 52 are both in the de-energized state, the electromagnetic reversing valve 52 is in the middle position, and the hydraulic control reversing valve 53 works in the right position under the action of the spring force. When the pressure oil of the main pump passes through the one-way valve 55 and reaches the P port of the hydraulic control reversing valve 53, the oil is cut off, and at the same time, a stream of pressure oil from the auxiliary pump flows through the one-way valve 55 to reach the P port of the hydraulic control reversing valve 53, and the oil is cut off; another stream of pressure oil from the auxiliary pump flows through the pressure reducing valve 51 to reach the P port of the electromagnetic reversing valve 52 and is cut off. The pressure oil in the chuck 124 returns through the right position of the hydraulic control reversing valve 53 and the middle position of the electromagnetic reversing valve 52, and the chuck 124 is in a loose state and will not clamp or limit the active drill rod 11.

[0057] like Figure 8As shown, in working condition 2, Y2 is energized, and the pressure oil from the main pump reaches the P port of the hydraulically controlled reversing valve 53 and is cut off; one stream of pressure oil from the auxiliary pump reaches the P port of the hydraulically controlled reversing valve 53 and is cut off, and the other stream flows through the electromagnetic reversing valve 52 through the pressure reducing valve 51, and reaches the control port of the chuck 124 through the hydraulically controlled valve; when the electromagnetic reversing valve 52 is in the right position and Y2 is energized, the electromagnetic reversing valve 52 is in the right position working state, and the hydraulically controlled reversing valve 53 is in the right position working state under the action of the spring force, and the pressure oil from the main pump flows through the one-way valve 55Ⅰ to the P port of the hydraulically controlled reversing valve 53 and is cut off, and the control oil of the hydraulically controlled reversing valve 53 is drained through the right position of the electromagnetic reversing valve 52. One stream of the pressure oil from the auxiliary pump passes through the P port of the one-way valve 55 and the hydraulically controlled reversing valve 53, and the oil is cut off; the other stream of oil is reduced to the set pressure through the pressure reducing valve 51, and then the pressure oil flows through the right position of the electromagnetic reversing valve 52, and then passes through the right position of the hydraulically controlled reversing valve 53 to reach the chuck 124. At this time, the chuck 124 is in a low-pressure clamping state, limiting the active drill rod 11.

[0058] like Fig. 9 As shown, in working condition three, Y1 is energized, and the pressure oil from the main pump flows into the control port of the chuck 124 through the hydraulic control reversing valve 53. One stream of pressure oil from the auxiliary pump reaches the control port of the hydraulic control reversing valve 53 through the electromagnetic reversing valve 52 to switch the working state of the hydraulic control reversing valve 53, and the other stream flows into the control port of the chuck 124 through the hydraulic control reversing valve 53 to merge with the hydraulic oil from the main pump and the auxiliary pump. The chuck 124 is in a high-pressure clamping state. When the electromagnetic reversing valve 52 is in the left position, Y1 is energized, the electromagnetic reversing valve 52 is in the left working state, and the hydraulic control reversing valve 53 is in the left working state under the action of the control oil. The pressure oil from the main pump flows through the one-way valve 55 and finally flows into the chuck 124 through the left position of the hydraulically controlled reversing valve 53. The pressure oil from the auxiliary pump is divided into two oil circuits. One oil circuit is reduced in pressure by the pressure reducing valve 51, flows through the left position of the electromagnetic reversing valve 52 and reaches the control port of the hydraulically controlled reversing valve 53, so that the hydraulically controlled reversing valve 53 is reversed and is in the left position working state; the other oil circuit passes through the one-way valve 55 and finally flows into the chuck 124 through the left position of the hydraulically controlled reversing valve 53. In this state, the main and auxiliary pumps merge to form a high-pressure oil source, so that the chuck 124 is in a high-pressure clamping state for salvage.

[0059] like Figure 2As shown, the brake assembly 3 includes a brake cover 31, a clamping piston 32 and a release piston 33. The brake cover 31 is provided with a sliding shaft 34. The left end of the transmission shaft 36 extends into the center of the clamping piston 32. A plurality of slips 35 are distributed circumferentially of the transmission shaft 36. In this embodiment, the number of slips 35 is 3. The clamping piston 32 is sleeved on the outside of the slips 35 and can move axially along the transmission shaft 36. The surface of the slips 35 away from the transmission shaft 36 is an inclined surface. The surface of the clamping piston 32 opposite to the slips 35 is an inclined surface. 5, the clamping piston 32 can slide by pushing the slip 35 to radially slide and clamp the transmission shaft 36, the releasing piston 33 is slidably sleeved on the sliding shaft 34 and can push the clamping piston 32 to release the clamping, the surface of the clamping piston 32 opposite to the slip 35 is a slope surface that matches the slope of the slip 35, the clamping piston 32 can slide so that the slope inside it contacts the slope of the slip 35, and the transmission shaft 36 is clamped by the radial movement of the slip 35, thereby limiting the rotation of the transmission shaft 36. The transmission shaft 36 can be quickly clamped and released through the axial sliding of the clamping piston 32 and the radial movement of the cava 35. The cooperation between the inclined surface and the slope surface provides a stable clamping force, ensuring that the transmission shaft 36 does not slide during operation, ensuring the reliability of the clamping of the transmission shaft 36, and being adaptable to transmission shafts 36 of different diameters. Even if the surface of the transmission shaft 36 is worn, stable clamping can be achieved by extending the sliding distance of the clamping piston 32. The transmission shaft 36 has strong versatility and can be applied to various types of drilling rig power heads.

[0060] The brake cover 31 is provided with an oil inlet 1 37 and an oil inlet 2 38. A first oil chamber is formed between the brake cover 31 and the side of the release piston 33 away from the clamping piston 32. The oil inlet 1 37 can provide hydraulic oil to the first oil chamber. The side of the clamping piston 32 away from the release piston 33 is provided with a second oil chamber. The oil inlet 2 38 can provide hydraulic oil to the second oil chamber. The inner wall and the outer wall of the release piston 33 are both provided with sealing rings. The outer wall sleeve of the clamping piston 32 is also provided with a sealing ring. The setting of the sealing ring effectively prevents leakage of hydraulic oil and ensures that the pressure in the hydraulic structure remains stable. The pressure oil enters the second oil chamber from the oil inlet 38, pushing the clamping piston 32 to move to the left, so that the slope inside it contacts the inclined surface of the cava 35, thereby pushing the cava 35 to move inward and limiting the radial displacement of the cava 35, thereby clamping the drive shaft 36 to achieve braking of the drive shaft 36; the pressure oil enters the first oil chamber from the oil inlet 37, pushing the release piston 33 to move, and its end face pushes the clamping piston 32 to move to the right, releasing the radial displacement restriction of the cava 35, thereby releasing the rotation restriction of the drive shaft 36, and realizing automatic control of the brake assembly 3 through hydraulic pressure, thereby improving the automation level and efficiency of the operation, and the hydraulic pressure can provide stable and adjustable pressure to ensure the accuracy of the clamping and releasing process, and the hydraulic pressure has high stability and reliability, ensuring that the brake assembly 3 can work stably under various working conditions, reducing the failure rate and maintenance cost.

[0061] It also includes a water braid 4 that provides pressure fluid to the active drill pipe 11, such as Figure 4 and Figure 5 As shown, the water braid part 4 includes a connecting shaft 41, a core shaft 42 and a water inlet assembly. The core shaft 42 and the connecting shaft 41 are both hollow shafts. The core shaft 42 is fixedly connected and communicated with the connecting shaft 41. The other end of the connecting shaft 41 is connected to the active drill rod 11. The core shaft 42 is communicated and rotatably connected with the water inlet assembly. A bearing seat 44 is provided to support the core shaft 42. A core shaft support bearing 45 is provided in the bearing seat 44 and is sleeved on the outer periphery of the core shaft 42. The core shaft 42 is fixedly connected and communicated with the connecting shaft 41. The other end of the connecting shaft 41 is connected to the active drill rod 11. The core shaft 42 is communicated and rotatably connected with the water inlet assembly. The water inlet assembly includes a housing 431, a water supply chamber 432 connected to the water inlet hole 433 is provided in the housing 431, and the water supply chamber 432 is connected to the water inlet hole 433. A section of the connecting shaft 41 near the active drill rod 11 is provided with an external thread for threaded connection with the rear end of the active drill rod 11; an end of the connecting shaft 41 near the water braid 4 is provided with an internal thread for threaded connection with the core shaft 42, which transmits the drilling medium flowing into the water braid 4 to the active drill rod 11, and connects the active drill rod 11 and the water braid 4. In this technical solution, the core shaft 42 is connected to the active drill rod 11 and rotates with the active drill rod 11 during operation. The core shaft support bearing 45 can ensure the smooth rotation of the core shaft 42, reduce friction and wear during the rotation process, and extend the service life of the equipment. The connecting shaft 41 and the core shaft 42 are hollow inside, and the pressure fluid can be smoothly transmitted from the water inlet assembly to the active drill rod 11, ensuring that the drilling medium can be stably and continuously supplied, thereby improving the drilling efficiency. The bearing seat 44 is provided with a grease nipple 462, which is connected to the inside of the bearing seat 44. The grease nipple 462 can provide lubricating oil to the spindle support bearing 45 to keep the spindle support bearing 45 lubricated, reduce the friction of the bearing under high load conditions, and extend the service life of the bearing; effective lubrication reduces the wear and heat accumulation of the bearing, avoids bearing damage caused by overheating, and improves the reliability and durability of the equipment. The water braid 4 is fixed to the gearbox 2 through the connecting sleeve 46, such as Figure 6 As shown, the connecting sleeve 46 includes a connecting flange, and waist-shaped holes 461 for bolts to pass through are opened on the upper and lower sides of the connecting flange to ensure the stability of the connection. A hexagonal hole that matches the end of the core shaft 42 is opened in the center of the connecting sleeve 46. The right end of the core shaft 42 is a regular hexagon that matches the hexagonal hole and is axially slidably connected to the hexagonal hole. When in use, the end of the core shaft 42 is inserted into the hexagonal hole so that the connecting sleeve 46 can drive the core shaft to rotate when it rotates with the main shaft 12, and the connecting flange is fixedly connected to the main shaft 12 with threads.

[0062] like Figure 3As shown, one end of the active drill rod 11 is a male connector 111, and the other end is a female connector 112. The male connector 111 is detachably connected to the bidirectional connector 13. A rotation-stopping portion 113 is provided on the outer periphery of the active drill rod 11. The outer periphery cross-section of the rotation-stopping portion 113 is polygonal. An end cover portion is provided on the end of the main shaft 12. The end cover portion includes a front end cover 123 and a chuck 124. The front end cover 123 is fixed on the chuck 124. A limiting opening is provided on the front end cover 123. The front end cover 123 limits the rotation of the rotation-stopping portion 113 through the limiting opening. When the main shaft 12 drives the end cover portion to stop rotating, the limiting opening of the front end cover 123 stops rotating synchronously. The limiting opening The hole limits the rotation of the stop portion 113, thereby allowing the active drill rod 11 to stop rotating. The above method realizes the limitation of the rotation of the active drill rod 11, but does not limit the axial sliding of the active drill rod 11, so that the active drill rod 11 can float axially for a certain distance during operation, which can effectively alleviate the axial impact generated by the drill rod during the threaded connection and disassembly process, thereby protecting the active drill rod 11 and other connecting parts and extending the service life of the equipment; when the active drill rod 11 produces axial floating, it can reduce the impact force on the water braid 4, reduce the wear of the water braid 4, and improve its overall durability and reliability. A limiting section 114 is provided between the female joint 112 and the stop block, and the limiting section 114 is located between the chuck 124. When the chuck 124 is clamped to the limit position, there is still a gap between the chuck 124 and the outer periphery of the limiting section 114. When the chuck 124 moves to the limit position, there is still a gap between the chuck 124 and the outer periphery of the limiting section 114. The length of the limiting section 114 is greater than the width of the chuck 124, so that the clamping force of the chuck 124 will not directly act on the active drill rod 11, thereby avoiding the active drill rod 11 directly bearing the strong clamping force of the chuck 124, and avoiding the metal fatigue deformation of the active drill rod 11 during the reciprocating rotation process, thereby reducing fatigue damage and increasing the service life of the active drill rod 11; due to the axial floating design of the active drill rod 11, the impact force borne by the water braid part 4 during the working process is reduced, which makes the water braid part 4 more evenly stressed, and the front end cover 123 includes an integrated flange and a jacket, and the front end cover 123 is threadedly fixedly connected to the chuck 124 through the flange to ensure the stability of the fixation. A gap M is left between the inner end surface of the connecting sleeve 46 facing the active drill rod 11 and the end surface of the connecting shaft 41, so that the limiting section 114 can slide axially along the chuck 124, so that the active drill rod 11 can float axially for a certain distance. The internal and external threads of the connecting shaft 41 cooperate to achieve a stable connection with the active drill rod 11 and the core shaft 42. The bearing seat 44 and the housing 431 are fixedly connected by bolts, and sealing rings are provided between the core shaft 42 and the housing 431 on both sides of the water inlet hole 433 to achieve sealing of the drilling medium.

[0063] The specific implementation process is as follows:

[0064] The brake assembly 3 is in the braking condition, the hydraulic motor cannot drive the active drill rod 11 to rotate, and the power head can also resist the counter-torque generated by the torsional deformation of the drill rod in the hole, which is suitable for the directional drilling condition of the drilling rig, and the power head does not drive the drill rod to rotate; the brake assembly 3 is in the loosening condition, and the hydraulic motor drives the active drill rod 11 to rotate forward and reverse; it is suitable for the rotary drilling and drill rod connection and disconnection conditions of the drilling rig, and the power head drives the drill rod to rotate, and the hydraulic system of the chuck 124 is in a low-pressure clamping state during the drilling process; during the drilling process, if the drill rod breaks and other accidents occur, resulting in the drill rod being unable to be removed, a special salvage drilling tool must be used for salvage drilling. Put the chuck 124 in a loose state, disassemble the water braid 4, the active drill rod 11, and the connecting shaft 41; use the chuck 124 to clamp the salvage drilling tool for drilling, and the chuck 124 is in a high-pressure clamping state.

[0065] A chuck 124 hydraulic system with a pressure graded control function is used to control the clamping pressure of the chuck 124. Combined with the setting that the diameter of the limit section 114 of the active drill rod 11 is slightly smaller than the clamping inner diameter of the chuck 124, it not only improves the stress condition of the active drill rod 11, but also avoids energy waste caused by long-term pressure holding of the chuck 124, and also improves the adaptability of the power head to various working conditions such as normal drilling and salvage drilling.

[0066] When the active drill rod 11 needs to be inspected and replaced, since the main shaft 12 is provided with a receiving hole 121 for the active drill rod 11 to pass through, the staff can directly slide the active drill rod 11 in the receiving hole 121 and take it out from the rear of the main shaft 12, thereby improving the speed of disassembling the active drill rod 11. At the same time, the space at the rear end of the main shaft 12 is relatively ample. If the active drill rod 11 is taken out from the front of the main shaft 12 according to the tradition, on the one hand, the front end cover 123 needs to be disassembled and tightened, and on the other hand, the space at the front is relatively limited, and it is inconvenient to install and disassemble the active drill rod 11. The above-mentioned arrangement can facilitate the staff to assemble the active drill rod 11 and then reinstall it into the main shaft 12, thereby improving the installation speed of the active drill rod 11. By setting the brake assembly 3, the start and stop of the active drill rod 11 can be adjusted in time.

[0067] In the technical solution, the end of the active drill rod 11 is also detachably connected to a two-way joint 13 by glue. When the thread on one side of the two-way joint 13 is worn to a certain extent, the two-way joint 13 can be removed and the installation direction can be reversed, and the end of the two-way joint 13 is fixedly connected to the active drill rod 11 by glue. Specifically: Fig.10As shown, a fastening glue is applied to the upper side of the two-way joint 13 along an axial straight line, and then the glue is applied symmetrically below the side joint. When the side joint is screwed with the female joint 112, the fastening glue at the left end of the glue-applied end will contact the thread of the female joint 112, and the fastening glue will be applied more widely along the tightening direction. The further to the right, the fewer the number of contacts between the fastening glue and the thread of the female joint 112, and the smaller the spread of the application. When the glue-applied side is screwed into the female joint 112 of the rod body, the fastening glue previously applied in a straight line will be spread out, forming a projection on the central symmetric plane of the joint. It is an approximately trapezoidal tape that is wider on the left and narrower on the right. When the other side is replaced, a similar method is used to apply glue, which just complements the strength of the thread itself, and better equalizes the strength of the threaded connection, which not only ensures the reversal anti-loosening strength, but also facilitates later disassembly, so that the service life of the active drill rod 11 is equivalent to twice that of the previous integral active drill rod 11, and there is no need to replace the rod body, which can save a lot of installation time and use costs, and can play an emergency role when constructing in some remote places where it is not convenient to repair and replace the active drill rod 11.

[0068] The above is only an embodiment of the present invention, and the common knowledge such as the known specific technical solutions and / or characteristics in the solution is not described in detail here. It should be pointed out that for those skilled in the art, without departing from the technical solution of the present invention, several modifications and improvements can be made, which should also be regarded as the protection scope of the present invention, and these will not affect the effect of the implementation of the present invention and the practicality of the patent. The scope of protection required by this application shall be based on the content of its claims, and the specific implementation methods and other records in the specification can be used to interpret the content of the claims.

Claims

1. A drilling drive system, characterized in that: The main drive mechanism comprises a main shaft, a brake assembly, a gearbox, a chuck and a main power source. The output shaft of the main power source meshes with the gearbox to drive the main shaft to rotate. The gearbox comprises a gear shaft and a multi-stage transmission gear. A transmission shaft connected to the gear shaft is arranged inside the brake assembly. The brake assembly can perform rotational braking on the transmission shaft. An active drill rod is installed at the end of the main shaft. A receiving hole for the active drill rod to pass through is opened in the main shaft. A two-way joint is detachably connected to the end of the active drill rod. The chuck is arranged at the end of the main shaft. A chuck pressure control system is also provided for controlling whether the chuck limits the active drill rod. The brake assembly comprises a brake cover, a clamping piston and a loosening piston. A sliding shaft is arranged inside the brake cover. One end of the transmission shaft extends into the clamping The center of the piston is provided with a plurality of cava distributed circumferentially of the transmission shaft. The clamping piston sleeve is arranged on the outer side of the cava and moves axially along the transmission shaft. The surface of the cava away from the transmission shaft is an inclined surface. The surface of the clamping piston opposite to the cava is a slope surface matching the inclined surface of the cava. The clamping piston can slide by pushing the cava to clamp the transmission shaft. The releasing piston sliding sleeve is arranged on the sliding shaft and can push the clamping piston to release the clamping. The brake cover is provided with an oil inlet 1 and an oil inlet 2. A first oil chamber is formed between the side of the releasing piston away from the clamping piston and the brake cover. The oil inlet 1 can provide hydraulic oil to the first oil chamber. A second oil chamber is provided on the side of the clamping piston away from the releasing piston. The oil inlet 2 can provide hydraulic oil to the second oil chamber.

2. The drilling drive system according to claim 1, characterized in that: The chuck pressure control system includes a pressure reducing valve, an electromagnetic reversing valve, a hydraulically controlled reversing valve, a main pump and an auxiliary pump; the electromagnetic reversing valve is a three-position four-way electromagnetic reversing valve with an A port, a B port, a P port and a T port, the hydraulically controlled reversing valve has a P port, a T port, an A port and a hydraulically controlled port, the chuck has a control oil port, the A port of the hydraulically controlled reversing valve is connected to the control oil port of the chuck, and the main pump is connected to the P port of the hydraulically controlled reversing valve; the oil circuit of the auxiliary pump is divided into two streams, one is connected to the P port of the hydraulically controlled reversing valve, and the other is connected to the P port of the electromagnetic reversing valve through the pressure reducing valve; the oil drain port of the pressure reducing valve is connected to the T port of the electromagnetic reversing valve and drains oil; the oil output from the A port of the electromagnetic reversing valve is divided into two streams, one is connected to the P port of the hydraulically controlled reversing valve, and the other is connected to the hydraulically controlled port of the hydraulically controlled reversing valve; the B port of the electromagnetic reversing valve is connected to the T port of the hydraulically controlled reversing valve.

3. The drilling drive system according to claim 2, characterized in that: The main pump flows to the P port of the hydraulically controlled reversing valve through the first one-way valve.

4. The drilling drive system according to claim 3, characterized in that: The oil circuit of the auxiliary pump is connected to the P port of the hydraulically controlled reversing valve through the second one-way valve, and the A port of the electromagnetic reversing valve is connected to the P port of the hydraulically controlled reversing valve through the third one-way valve.

5. The drilling drive system according to claim 4, characterized in that: The pressure reducing valve is a fixed value pressure reducing valve.

6. The drilling drive system according to claim 5, characterized in that: The solenoid directional control valve has Y1 and Y2 positions.

7. The drilling drive system according to claim 6, characterized in that: In the working condition, the Y1 and Y2 positions lose power, the pressure oil from the main pump reaches the P port of the hydraulically controlled reversing valve and is cut off, and the pressure oil from the auxiliary pump flows through the pressure reducing valve and reaches the P port of the electromagnetic reversing valve and is cut off.

8. The drilling drive system according to claim 6, characterized in that: Under working condition 2, Y2 is energized, and the pressure oil from the main pump reaches the P port of the hydraulically controlled reversing valve and is cut off; one stream of pressure oil from the auxiliary pump reaches the P port of the hydraulically controlled reversing valve and is cut off, and the other stream flows through the pressure reducing valve, the electromagnetic reversing valve, and reaches the control port of the chuck through the hydraulically controlled reversing valve.

9. The drilling drive system according to claim 6, characterized in that: In working condition three, Y1 is energized, and the pressure oil from the main pump flows into the control port of the chuck through the hydraulically controlled reversing valve. One stream of pressure oil from the auxiliary pump reaches the hydraulic control port of the hydraulically controlled reversing valve through the electromagnetic reversing valve to switch the working state of the hydraulically controlled reversing valve, and the other stream flows into the control port of the chuck through the hydraulically controlled reversing valve, and the hydraulic oil from the main pump and the auxiliary pump merge.

10. The drilling drive system according to any one of claims 1 to 9, characterized in that: It also includes a water braid part that provides pressure fluid to the active drill pipe. The water braid part includes a connecting shaft, a core shaft and a water inlet assembly. The core shaft and the connecting shaft are both hollow shafts. The core shaft is fixedly connected and communicated with the connecting shaft. The other end of the connecting shaft is connected to the active drill pipe. The core shaft is communicated and rotatably connected with the water inlet assembly. A bearing seat is provided to support the core shaft. The bearing seat is provided with a core shaft support bearing sleeved on the outer periphery of the core shaft.

11. The drilling drive system according to any one of claims 1 to 9, characterized in that: One end of the active drill rod is a male joint, and the other end is a female joint. The male joint and the two-way joint are detachably connected. A stopper is provided on the outer periphery of the active drill rod. The outer periphery cross-section of the stopper is polygonal. An end cover is provided on the end of the main shaft. The end cover includes a front end cover, which is fixed on the chuck. A limiting opening is provided on the front end cover. The front end cover limits the rotation of the stopper through the limiting opening.

12. The drilling drive system according to claim 11, characterized in that: A limit section is provided between the female joint and the anti-rotation block, and the limit section is located between the chucks. When the chucks are clamped to the limit position, there is still a gap between the chucks and the outer periphery of the limit section.

13. The drilling drive system according to claim 12, characterized in that: The length of the limiting section is greater than the width of the chuck.

14. The drilling drive system according to claim 10, characterized in that: A water inlet hole is opened at the end of the core shaft, and the water inlet assembly includes a shell, in which a water supply chamber connected to the water inlet hole is arranged, and the water supply chamber is connected to the water inlet hole. An external thread for connecting to the threaded connection with the rear end of the active drill rod is arranged at one end of the connecting shaft close to the active drill rod; an internal thread for connecting to the threaded connection with the core shaft is arranged at one end of the connecting shaft close to the water braid part.

15. The drilling drive system according to claim 10, characterized in that: The water braid part is fixed on the gearbox through a connecting sleeve. The connecting sleeve includes a connecting flange. The connecting flange is provided with a waist-shaped hole for bolts to pass through. The center of the connecting sleeve is also provided with a hexagonal hole that matches the end of the core shaft.

16. The drilling drive system according to claim 15, characterized in that: A gap is left between the end surface of the connecting sleeve facing the active drill rod and the end surface of the connecting shaft.

Images