Drill pipe mounting system

Abstract

A drill pipe mounting system, comprising a frame, a power unit (1), and dual grippers. An active drill pipe (10) comprises a limiting section (103) and an anti-rotation section (104). A chuck (14) is provided at one end of a main shaft (11). A front end cover (13) is provided at one end of the chuck (14). The chuck (14) is clamped on the limiting section (103). The front end cover (13) is slidably connected to the anti-rotation section (104). The front end cover (13) drives the active drill pipe (10) to rotate. The chuck (14) is connected to a staged hydraulic system. The staged hydraulic system can control the clamping pressure of the chuck (14) on the limiting section (103). The front gripper comprises a front support plate (203) and a rear support plate (205) that are spaced apart. The front support plate (203) and the rear support plate (205) are both provided with an opening, and the widths of the openings are both greater than or equal to the diameter of a large-scale drilling tool. The drill pipe mounting system further comprises a swinging body (22), wherein the swinging body (22) can swing outside the front support plate (203) and the rear support plate (205). The front gripper is connected to a clamping oil cylinder. An anti-slip hydraulic system is provided between a hydraulic motor (17) and the clamping oil cylinder. During clamping, the clamping oil cylinder is pressurized by means of the hydraulic motor reversing an oil path. The mounting system solves the shortcomings of existing drill pipe systems in terms of mounting and maintenance efficiency.

Description

Drill rod installation system TECHNICAL FIELD

[0001] The present application relates to the field of coal mine drilling machines, in particular to a drill rod installation system. BACKGROUND

[0002] The power head and the gripper are important components for installing drill rods on a coal mine drilling machine. The power head is used to transmit the rotation and thrust power required for assembly and disassembly to the drill rod, while the gripper is responsible for clamping the drill rod and cooperating with the power head to realize the connection and disconnection of the drill rod joint and to prevent the drill rod from slipping.

[0003] Currently, with the emergence of automatic directional drilling machines, the chuck and the active drill rod two drill rod connection methods are integrated: when drilling normally, the active drill rod is used to assemble and disassemble the ordinary drill rod from the front end of the power head; when fishing drill tools, the active drill rod is removed and the chuck is used to assemble and disassemble the fishing drill rod from the rear end of the power head. The outer diameters of the ordinary drill rod used during normal drilling and the fishing drill rod are generally different. In order to enable the power head of the automatic directional drilling machine to be applicable to the ordinary drill rod and the fishing drill rod, a drill rod connection mechanism combining the chuck and the active drill rod has emerged, which has the active drill rod fixedly connected to the front end of the chuck. By installing and disassembling the active drill rod, the use of the active drill rod and the chuck is switched to achieve the purpose of connecting drill rods of different outer diameters.

[0004] However, the existing technology has deficiencies in the speed of disassembly and assembly. The existing active drill rods are of an integral structure, and the main body and the joint are formed as a whole by machining or welding. As described in the patent with application number 202010733745.4, the active drill rod is a whole, and if it is damaged during construction, the active drill rod needs to be replaced as a whole after the active drill rod fixing parts are removed, which is time-consuming and inefficient, and the cost of spare parts for maintenance is also high. For example, in the patent with application number 202011156490.6, although the active drill rod is divided into a drill rod joint and a main body, it is actually formed as a whole by welding, only the machining difficulty and amount are reduced during processing. In addition to the structural deficiencies, the existing power head hydraulic system is also difficult to adapt to the demand of switching between the chuck and the active drill rod for connecting the drill rod. The existing power head has a hierarchical hydraulic system with only two states of loosening and clamping, and does not have a hierarchical control function. Long-term high-pressure clamping not only easily damages the active drill rod, but also produces unnecessary energy consumption, which is not suitable for power heads with both chuck and active drill rod drill rod connection methods.

[0005] Regarding the clamp, due to the complexity of the drill pipe handling technology of the directional drilling machine, both ordinary drill pipes and large drill tools with larger length or outer diameter than ordinary drill pipes, such as hole bottom motors, need to be handled. The outer diameters and lengths of various drill tools are different, which leads to the following deficiencies of the clamp used in the directional drilling machine: First, the core drill tool of the directional drilling, i.e. the hole bottom motor, has a larger length and outer diameter than ordinary drill pipes, and cannot be disassembled by the method of generally disassembling the drill pipe from the rear end or the middle of the rack. The distance from the front end of the clamp to the hole wall is very limited, and it is difficult to directly assemble the hole bottom motor into the clamp. Second, the clamp generally adopts the structure form of installing slips on the surface of the slip seat. After assembly, it can only be used for clamping drill pipes with one outer diameter. If other drill tools with different outer diameters, such as hole bottom motors and fishing drill pipes, need to be replaced, complex operations of disassembling and replacing slips will be required, which will consume a lot of time and energy. Finally, during the operation of the clamp, the drill pipe needs to be continuously inserted into and withdrawn from the clamp. Since the slips on both sides of the clamp need to be frequently opened and closed, the distance between them changes frequently, and therefore the clamp generally does not have a guiding function. A guiding sleeve generally needs to be separately arranged in front of the clamp for guiding the clamp during the insertion and withdrawal of the drill pipe to prevent the drill pipe from deviating from the axis during the transition, causing damage to the clamp and the power head. Similarly, in addition to the structural deficiencies of the clamp, the existing double-clamp hydraulic system also has certain defects, which leads to the slipping of the drill pipe during the disconnection of the thread. This is mainly because: when the drill pipe is disconnected, the clamping force of the clamp needs to overcome the torque of the fully tightened thread at the threaded joint of the drill pipe. The power head needs to provide a large reverse torque to complete the disconnection. Correspondingly, the clamp also needs to provide a large and stable clamping force to ensure that the drill pipe clamped by the power head does not rotate with the power head, i.e. does not slip. However, during the period when the clamp clamps the drill pipe by the clamping oil cylinder under the action of hydraulic pressure and is preserved by the hydraulic lock, the hydraulic lock or the clamping oil cylinder will inevitably have different degrees of leakage. Moreover, as the use time increases, the leakage amount and speed of the hydraulic oil will gradually increase. Therefore, from clamping to reverse disconnection, the clamping force of the clamp will decrease, leading to the slipping of the clamp during the disconnection of the drill pipe, ultimately resulting in the failure of the disconnection, and even causing safety accidents.

[0006] Therefore, the existing drill clamp has many deficiencies in the convenience of installing large drill tools, the adaptability of multiple specifications of drill tools, and the guiding performance. At the same time, due to the defects of the hydraulic system, the drill pipe slips during disconnection, affecting the efficiency and safety of the site. SUMMARY

[0007] The present application aims to provide a drill pipe installation system to solve the problem of the low efficiency of the existing drill pipe system composed of a power head and a clamp in installation and maintenance.

[0008] To achieve the above object, the present application adopts the following technical scheme: a drill rod installation system, comprising a rack, a power head and a double holder respectively arranged at two ends of the rack, the power head comprising a main shaft, a water braid and a driving drill rod, the inside of the main shaft being provided with a connecting shaft, the water braid and the driving drill rod being respectively connected to two ends of the connecting shaft, the driving drill rod comprising a limiting section and a rotation-stopping section, one end of the main shaft being provided with a chuck, one end of the chuck being provided with a front end cover, the chuck being clamped on the limiting section, the front end cover being slidingly connected to the rotation-stopping section, the front end cover being capable of driving the driving drill rod to rotate, the chuck being connected with a staged hydraulic system, the staged hydraulic system being capable of controlling the clamping pressure of the chuck on the limiting section;

[0009] The double holder comprises a front holder and a rear holder, the front holder comprising front and rear support plates arranged at intervals, and the front and rear support plates each being provided with a through hole; two through holes each being provided with an opening, and the width of the opening being greater than or equal to the diameter of a large drill tool; the front and rear support plates each being provided with an oscillating body, and the oscillating body being capable of oscillating out of the front and rear support plates;

[0010] The front and rear holders each being connected with a clamping oil cylinder, the power head further comprising a hydraulic motor, a slip-preventing hydraulic system being arranged between the hydraulic motor and the clamping oil cylinder, the slip-preventing hydraulic system being capable of pressurizing the clamping oil cylinder through a reverse oil path of the hydraulic motor during clamping operation.

[0011] The beneficial effects of the present scheme are as follows: 1. The structure of the power head, the structure of the holder and the control hydraulic system of the chuck are all improved and upgraded, the convenience of installation and replacement of the drill rod is realized in the limited structure of the original drilling machine, different controls are performed in the process of construction according to different construction requirements, the present scheme is suitable for mine drilling machines that need to replace drill tool specifications during downhole construction, especially for directional drilling machines that use ordinary drill rods and large drill tools including special drill tools such as fishing drill rods and hole bottom motors, thereby solving the problems of low installation and maintenance efficiency of the drill rod system composed of the existing power head and holder and low on-site construction efficiency.

[0012] 2. The driving drill rod and the chuck are combined in a form that can be quickly disassembled, the driving drill rod connection device of the power head can be quickly replaced, the drill tool specifications can be easily replaced on the construction site, the torque is transmitted through the cooperation of the front end cover, and the driving drill rod and the chuck are clamped and loosened, the driving drill rod and the connecting shaft are disassembled and assembled from the rear end of the power head, the disassembly and assembly process is greatly simplified, and the disassembly and assembly efficiency is improved.

[0013] 3. The staged hydraulic system with pressure grading control function controls the clamping pressure of the chuck, improves the stress condition of the driving drill rod, avoids energy waste caused by long-term pressure holding of the chuck, and improves the adaptability of the power head to normal drilling and fishing drilling and other working conditions.

[0014] 4. The swing body in the holder can swing out of the base, and the upwardly open through holes on the front support plate and the rear support plate can be combined to leave a large space inside and above the holder, so that the holder can meet the installation requirements of large drill tools and other special drill tools.

[0015] 5. By connecting the reverse oil path in the hydraulic motor controlled by hydraulic oil in the drilling machine with the clamping oil path in the top clamp holder, a new anti-slip hydraulic system of the holder is formed, and the problem of slip of the existing top clamp holder during the reverse rotation of the power head to release the drill rod is solved.

[0016] Preferably, the driving drill rod comprises a rod body and a double-end joint arranged at one end of the rod body, the limiting section and the rotation-stopping section are arranged on the rod body, a hexagonal shape is arranged on the outer periphery of the rotation-stopping section, a hexagonal through hole is arranged in the inner portion of the front end cover, the diagonal distance of the hexagonal shape on the outer periphery of the rotation-stopping section is smaller than the diameter of the chuck after being loosened, the outer diameters of the shaft sections on both sides of the limiting section are larger than the minimum diameter of the chuck after being clamped, and the width of the limiting section is slightly larger than the clamping width of the chuck.

[0017] Preferably, the hydraulic motor is connected with a gearbox, the gearbox comprises a gear shaft and multiple gear stages, the power of the hydraulic motor is transmitted to the driving drill rod after being speed-converted and torque-increased, and the main shaft is arranged in the inner portion of the gearbox.

[0018] Preferably, the water braid comprises a mandrel and a water inlet assembly, the mandrel is fixedly connected with the connecting shaft and is in communication with the connecting shaft, and the mandrel is in communication with and rotatably connected with the water inlet assembly; the water inlet assembly comprises a shell and a water inlet hole, the shell is internally provided with a water supply cavity in communication with the water inlet hole; the water braid further comprises a bearing seat, the bearing seat supports the mandrel, the bearing seat is provided with a grease nipple in communication with the inner portion of the bearing seat.

[0019] Preferably, the water braid further comprises a connecting sleeve, the connecting sleeve connects the water braid to the end of the gearbox away from the hydraulic motor; the connecting sleeve comprises a connecting flange, the connecting flange is provided with a waist-shaped hole for the bolt to pass through, and the end face of the connecting sleeve facing the driving drill rod and the end face of the connecting shaft are left with a gap.

[0020] Preferably, the brake assembly comprises a brake cover, a clamping piston and a loosening piston, the brake cover is internally provided with a sliding shaft, one end of the transmission shaft extends into the center of the clamping piston, the transmission shaft is circumferentially provided with multiple brake slips, the clamping piston is sleeved on the brake slips and can move in the axial direction, the surface of the brake slip away from the transmission shaft is a slope, the surface of the clamping piston opposite to the brake slip is a slope surface matched with the slope of the brake slip, the clamping piston can slide through the brake slip to clamp the transmission shaft, and the loosening piston is slidably sleeved on the sliding shaft and can push the clamping piston to release the clamping.

[0021] Preferably, the graded hydraulic control system includes a pressure reducing valve, a solenoid directional valve, a hydraulically controlled directional valve, a main pump, and an auxiliary pump. The solenoid directional valve is a three-position four-way solenoid directional valve with ports A, B, P, and T, and has Y1 and Y2 positions. The hydraulically controlled directional valve is a hydraulically controlled directional valve with ports P, T, A, and a hydraulic control port. The chuck has a control port, and the A port of the hydraulically controlled directional valve is connected to the control port of the chuck. The main pump is connected to the P port of the hydraulically controlled directional valve. The auxiliary pump's oil circuit is divided into two streams: one connected to the P port of the hydraulically controlled directional valve, and the other connected to the P port of the solenoid directional valve via the pressure reducing valve. The drain port of the pressure reducing valve is connected to and drains oil from the T port of the solenoid directional valve. The oil outlet of the A port of the solenoid directional valve is divided into two streams: one connected to the P port of the hydraulically controlled directional valve, and the other connected to the hydraulic control port of the hydraulically controlled directional valve. The B port of the solenoid directional valve is connected to the T port of the hydraulically controlled directional valve.

[0022] Preferably, when the chuck is released, positions Y1 and Y2 are de-energized, the pressure oil from the main pump reaches the P port of the hydraulic directional valve and stops, and the pressure oil from the auxiliary pump flows through the pressure reducing valve to the P port of the solenoid directional valve and stops.

[0023] Preferably, when the chuck is clamped under low pressure, Y2 is energized, and the pressure oil from the main pump reaches the P port of the hydraulic control directional valve and is cut off; one stream of pressure oil from the auxiliary pump reaches the P port of the hydraulic control directional valve and is cut off, while the other stream flows through the pressure reducing valve, the solenoid directional valve, and the hydraulic control valve to the control port of the chuck.

[0024] Preferably, when the chuck is clamped under high pressure, Y1 is energized, and the pressure oil from the main pump flows into the control port of the chuck through the hydraulic control directional valve. One stream of pressure oil from the auxiliary pump reaches the control port of the hydraulic control directional valve through the solenoid directional valve to switch the working state of the hydraulic control directional valve, and the other stream flows into the control port of the chuck through the hydraulic control directional valve. The hydraulic oil from the main pump and the auxiliary pump merges.

[0025] Preferably, the swing body includes two support plates symmetrically arranged front and rear, each support plate having a guide mounting hole; a flipping shaft seat is provided on one side of the support plate, and a front cylinder mounting plate is connected to the outer end face of each of the two support plates, the front cylinder mounting plate having a front clamping cylinder, and a swinging ear seat is provided below the front cylinder mounting plate near the flipping shaft seat, with a swinging cylinder rotatably connected inside the swinging ear seat; a flipping plate is connected to the front support plate and the rear support plate near the flipping shaft seat, the flipping plate having a flipping hole, and a flipping pin being provided inside the flipping hole.

[0026] Preferably, each opening is detachably connected to a reinforcing plate, and the top of the front support plate and the rear support plate are provided with several matching grooves and protrusions between the bottom of the reinforcing plate.

[0027] Preferably, each of the two through holes is provided with a guide sleeve assembly, which includes an outer guide sleeve and an inner guide sleeve. The outer diameter of the inner guide sleeve is divided into two stages. The smaller diameter section of the inner guide sleeve mates with the guide mounting hole on the swing body, and the larger diameter section of the inner guide sleeve mates with the through holes on the front support plate and the rear support plate.

[0028] Preferably, the outer diameter of the outer guide sleeve is divided into two stages. The large diameter section of the outer guide sleeve is provided with a countersunk connecting hole, which is used to connect the outer guide sleeve and the inner guide sleeve to the swing body. The inner diameter of the inner guide sleeve is also divided into two stages. The small diameter section of the inner diameter is a through hole of equal diameter, which mates with the small diameter section of the outer guide sleeve. The large diameter section of the inner diameter is a countersunk stage, which mates with the large diameter section of the outer guide sleeve.

[0029] Preferably, the clamp mounting part includes a rear clamp mounting part, which includes a symmetrically arranged front side plate and a rear side plate. A U-shaped hole is provided in the middle of the front side plate and the rear side plate, and the U-shaped hole makes the top of the front side plate and the rear side plate completely open. A rear hydraulic cylinder mounting plate is connected to the outer end face of both sides of the front side plate and the rear side plate.

[0030] Preferably, a semi-circular guide sleeve is connected to each U-shaped hole. The outer diameter of the semi-circular guide sleeve is divided into two stages. The smaller diameter section of the semi-circular guide sleeve mates with the U-shaped hole, while the larger diameter section of the semi-circular guide sleeve is used to fix the semi-circular guide sleeve to the front or rear side plate.

[0031] Preferably, the piston rod in the clamping cylinder is detachably connected to an outer slip, and an inner slip is detachably connected to the inner side of the outer slip; the diameter of the arc segment on the inner surface of the outer slip matches the outer diameter of the inner slip, and the outer slip is provided with a countersunk hole, in which the piston rod of the clamping cylinder is detachably connected; both the upper and lower ends of the inner slip are provided with bosses, and both the upper and lower ends of the outer slip are provided with grooves, in which the bosses are detachably connected.

[0032] Preferably, the anti-slip hydraulic system includes a branch oil circuit located between the reversing oil circuit connected to the hydraulic motor and the clamping oil circuit connected to the clamping oil cylinder. The branch oil circuit is equipped with a check valve, which allows oil from the reversing oil circuit to flow into the clamping oil circuit in only one direction. A hydraulic lock is connected to both the clamping oil circuit and the releasing oil circuit.

[0033] The beneficial effects of this solution are as follows: By connecting the reverse oil circuit of the power head motor and the clamping oil circuit of the clamp, and by setting a one-way valve and cooperating with the hydraulic lock, a hydraulic system for preventing slippage of the top clamp is formed, in which the reverse linkage pressurization, forward rotation and the individual action of the clamp do not affect each other. This solves the problem of slippage caused by the decrease in clamping force due to leakage of the clamping cylinder and hydraulic lock in the existing hydraulic system of the top clamp, ensuring on-site construction safety and further improving construction efficiency.

[0034] Preferably, the opening pressure of the inlet valve of the one-way valve is higher than the return pressure in the reverse oil circuit.

[0035] Preferably, a front check valve is provided between the clamping oil circuit and the reversing oil circuit of the front clamping cylinder, and a rear check valve is provided between the clamping oil circuit and the reversing oil circuit of the rear clamping cylinder, and the front check valve and the rear check valve are interconnected. Attached Figure Description

[0036] Figure 1 is a three-dimensional view of the drilling rig in an embodiment of the present invention;

[0037] Figure 2 is a schematic diagram of the power head in an embodiment of the present invention;

[0038] Figure 3 is a schematic diagram of the active drill pipe in an embodiment of the present invention;

[0039] Figure 4 is a schematic diagram of the front cover in an embodiment of the present invention;

[0040] Figure 5 is a detailed view of the water braid in an embodiment of the present invention;

[0041] Figure 6 is a schematic diagram of the water braid connection according to an embodiment of the present invention;

[0042] Figure 7 is a schematic diagram of the connecting sleeve in an embodiment of the present invention;

[0043] Figure 8 is a structural diagram of the brake assembly according to an embodiment of the present invention;

[0044] Figure 9 is a schematic diagram of the graded hydraulic system when the chuck is released in an embodiment of the present invention;

[0045] Figure 10 is a schematic diagram of the graded hydraulic system during low-pressure clamping of the chuck in an embodiment of the present invention;

[0046] Figure 11 is a schematic diagram of the graded hydraulic system during high-pressure clamping of the chuck in an embodiment of the present invention;

[0047] Figure 12 is a three-dimensional view of the dual clamps in an embodiment of the present invention;

[0048] Figure 13 is a three-dimensional view of the base in an embodiment of the present invention;

[0049] Figure 14 is a three-dimensional view of the swing body in an embodiment of the present invention;

[0050] Figure 15 is a three-dimensional view of the external clasp in an embodiment of the present invention;

[0051] Figure 16 is a three-dimensional view of the inner cavitation valve in an embodiment of the present invention;

[0052] Figure 17 is a schematic diagram of the internal structure of the dual clamp in an embodiment of the present invention;

[0053] Figure 18 is a three-dimensional view of the outer guide sleeve in an embodiment of the present invention;

[0054] Figure 19 is a three-dimensional view of the inner guide sleeve in an embodiment of the present invention;

[0055] Figure 20 is a three-dimensional view of the semi-ring guide sleeve in an embodiment of the present invention;

[0056] Figure 21 is a schematic diagram of the hydraulic system in an embodiment of the present invention. Detailed Implementation

[0057] The following detailed description illustrates the specific implementation method:

[0058] The reference numerals in the accompanying drawings include: power head 1, active drill rod 10, rod body 101, female connector 102, anti-rotation section 103, limiting section 104, double-ended connector 105, connecting shaft 11, water braid 12, mandrel 121, housing 122, water supply chamber 123, water inlet 124, bearing seat 125, grease nipple 1251, mandrel support bearing 126, front end cover 13, hexagonal through hole 131, hexagonal outer sleeve 132, chuck 14, spindle 15, gearbox 16, hydraulic motor 17, brake assembly 18, brake cover 181, clamping piston 182, releasing piston 183, sliding shaft 184, brake slip 185, drive shaft 186, first oil inlet 187, second oil inlet 188, key 189, connecting sleeve 19, oblong hole 191, base 2, mounting plate 201, flip plate 202, front support. Plate 203, Reinforcing Plate 204, Rear Support Plate 205, Rear Liner Plate 206, Rear Side Plate 207, Rear Cylinder Mounting Plate 208, Front Side Plate 209, Outer Guide Sleeve 21, Inner Guide Sleeve 210, Swing Body 22, Support Plate 221, Front Cylinder Mounting Plate 222, Front Liner Plate 223, Swing Ear Seat 224, Tilting Shaft Seat 25, Swing Cylinder 226, Tilting Pin 227, Front Clamping Cylinder 23, Rear Clamping 230 hydraulic cylinder, 24 outer slip, 240 inner slip, 25 semi-ring guide sleeve, 3 frame, 41 pressure reducing valve, 42 electromagnetic directional valve, 43 hydraulic directional valve, 44 oil tank, 45 first check valve, 46 second check valve, 47 third check valve, 51 forward rotation oil circuit, 52 reverse rotation oil circuit, 53 front hydraulic lock, 54 front check valve, 55 rear check valve, 56 rear hydraulic lock, 57 clamping oil circuit, 58 releasing oil circuit.

[0059] Example

[0060] The embodiment is basically as shown in Figures 1-2. As shown in Figure 1, the drill pipe installation system includes a frame 3, a power head 1, a clamp, a staged hydraulic system, and an anti-slip hydraulic system. The power head 1 is connected to the drill pipe and transmits the rotational and locating power required for loading and unloading. The clamp is responsible for holding the drill pipe and works with the power head 1 to connect and disconnect the drill pipe joint while preventing it from slipping. The power head 1 and the clamp are respectively installed at both ends of the frame 3. By improving the structure of the power head 1 and the clamp, and by adding a staged hydraulic system and an anti-slip hydraulic system, the success rate of drill pipe installation and disconnection is improved, and the operational complexity is reduced, thereby optimizing the construction of existing coal mine drilling rigs.

[0061] First, the improved structure of the power head 1 will be explained with reference to Figure 2-8.

[0062] As shown in Figure 2, the power head 1 includes a spindle 15, a water braid 12, an active drill rod 10, a hydraulic motor 17, a brake assembly 18, and a gearbox 16. The hydraulic motor 17 is the power source of the power head 1, providing the driving force for the rotation of the active drill rod 10. The output shaft of the hydraulic motor 17 meshes with the gearbox 16, which includes a gear shaft and multi-stage gears. The gearbox 16 transmits the power from the hydraulic motor 17 to the active drill rod 10 after speed change and torque amplification to meet the drilling requirements. The gearbox 16 also serves as the mounting and support structure for other parts of the power head 1. The brake assembly 18 is used to brake the rotation of the gearbox 16. The brake assembly 18 has a drive shaft 186 connected to the gear shaft. The drive shaft 186 is connected to the gear shaft via a key 189 to achieve synchronous rotation. The brake assembly 18 brakes the rotation of the drive shaft 186 and simultaneously prevents the spindle 15 from rotating under the reverse torque of the drill rod. The main spindle 15 has a connecting shaft 11 inside, and the water braid 12 and the active drill rod 10 are respectively connected to the two ends of the connecting shaft 11. The main spindle 15 has a receiving hole that allows the active drill rod 10 to pass through.

[0063] As shown in Figure 3, the active drill pipe 10 includes a rod body 101 and a double-ended connector 105 located at one end of the rod body 101. Both ends of the rod body 101 are provided with female connectors 102. The female connector 102 at the left end is connected to the connecting shaft 11. In this embodiment, the female connectors 102 all use the same tapered thread connection method as the drill pipe. The female connector 102 at the right end is connected to the double-ended connector 105 and is connected to the working drill pipe through the double-ended connector 105. The rod body 101 includes a limiting section 104 and an anti-rotation section 103. The outer circumferential cross-section of the anti-rotation section 103 is polygonal (hexagonal in this embodiment). Referring to Figure 2, one end of the spindle 15 is connected to a chuck 14, and one end of the chuck 14 is connected to a front end cap 13. The chuck 14 is a normally open chuck 14. Referring to Figure 4, the front cover 13 has a hexagonal through hole 131 inside. The hexagonal through hole 131 cooperates with the anti-rotation section 103 to achieve a sliding connection between the front cover 13 and the active drill rod 10, while also limiting the rotation of the active drill rod 10. The rear end of the front cover 13 has a hexagonal outer sleeve 132, and the front end of the chuck 14 has a hexagonal inner hole. The hexagonal outer sleeve 132 cooperates with the hexagonal inner hole to transmit the rotational power of the power head 1 to the front cover 13, and then to the active drill rod 10 to achieve the rotation of the active drill rod 10. The outer diameter of the left-end female connector 102 is smaller than the diameter of the chuck 14 after it is released, ensuring that the active drill rod 10 can be pulled out from behind the power head 1. At the same time, the outer diameter of the left-end female connector 102 is larger than the minimum diameter of the chuck 14 after it is clamped, so as to achieve axial limitation of the active drill rod 10 when the chuck 14 is clamped. The diagonal distance of the hexagonal side of the anti-rotation section 103 is smaller than the diameter of the chuck 14 after it is released, to ensure that the active drill rod 10 can be pulled out from behind the power head 1. The outer diameters of the shaft sections on both sides of the limiting section 104 (i.e., the outer diameter of the female connector 102 and the hexagonal side distance of the anti-rotation section 103) are both larger than the minimum diameter of the chuck 14 after it is clamped, and the width of the limiting section 104 is slightly larger than the clamping width of the chuck 14.

[0064] By improving the drill rod structure, as well as the front cover 13 and chuck 14, the rotation of the active drill rod 10 is restricted while allowing axial sliding. This enables the active drill rod 10 to float axially a certain distance during operation, effectively mitigating the axial impact generated during threaded connection and disassembly. This protects the active drill rod 10 and other connecting components, extending the equipment's service life. When the active drill rod 10 floats axially, the impact force on the water braid 12 is reduced, decreasing wear on the water braid 12 and improving the overall service life and reliability of the drilling rig. The limiting section 104 is located between the chucks 14. When the chuck 14 is clamped to the limit position, there is still a gap between it and the outer periphery of the limiting section 104. This prevents the clamping force of the chuck 14 from acting directly on the active drill rod 10, thus avoiding the active drill rod 10 from directly bearing the strong clamping force of the chuck 14. This avoids the metal fatigue deformation of the active drill rod 10 during reciprocating rotation, thereby reducing fatigue damage and increasing the service life of the active drill rod 10. Due to the axial floating design of the active drill rod 10, the impact force on the water braid 12 during operation is reduced, which makes the force on the water braid 12 more uniform and achieves axial force balance of the water braid 12.

[0065] In addition, the double-ended connector 105 has identical male connectors at both ends, which match the female connector 102 of the rod body 101 and the internal thread of the working drill rod used by the drilling rig. During normal use, one end is glued to its external thread and screwed into the female connector 102 of the rod body 101, while the other end connects to the female connector 102 of the drill rod preceding the active drill rod 10, thus enabling the power head 1 to drive the drill rod. When the external thread connecting the connector to the drill rod wears to a certain extent, the threaded connection between the connector and the rod body 101 is loosened, the male connectors at both ends are swapped, and then glued again before connecting them to the rod body 101. Since the threads of the male connector previously connected to the rod body 101 are fixed during operation and do not wear, swapping the threads at both ends is equivalent to the double-ended connector 105 being usable twice, and its lifespan is twice that of the previous integral active drill rod 10. This reduces the consumption of the active drill rod 10 by the original drilling rig, thereby reducing resource waste and drilling rig operating costs.

[0066] Additionally, when the threads on one side of the double-ended connector 105 are worn and need to be removed and the installation direction reversed, the worn section of the double-ended connector 105 is fixed to the active drill rod 10 with adhesive. Specifically, fastening adhesive is applied axially along the upper part of one side of the connector 105, and then symmetrically applied below that side. When the connector on this side is tightened to the female connector 102, the fastening adhesive on the left end of the adhesive-applied end will contact the threads of the female connector 102, and the fastening adhesive will spread more widely along the tightening direction. The further to the right, the fewer turns the fastening adhesive makes contact with the threads of the female connector 102, and the smaller the spread of the adhesive. When the adhesive-applied side is screwed into the rod body... After connecting the female connector 102 of 101, the previously applied adhesive in a straight line will be spread out, forming an approximately trapezoidal tape projected onto the symmetrical plane of the connector's center, wider on the left and narrower on the right. One side of the tape is applied as described above, and the other side is applied using a similar method. This complements the varying stress levels of the threads themselves, effectively homogenizing the strength of the threaded connection. This ensures both anti-loosening strength and eases disassembly, saving significant installation time and operating costs. Furthermore, it can serve as an emergency measure in remote locations where maintenance and replacement of the active drill rod 10 are inconvenient. After connecting the construction drill rod to the active drill rod 10, adhesive is applied to the connection point using the same method, further securing the active drill rod 10 and the construction drill rod with the adhesive on top of the threaded connection, preventing reversal.

[0067] As shown in Figures 5 and 6, the water braid 12 includes a mandrel 121 and a water inlet assembly. The mandrel 121 is fixedly connected to and communicates with the connecting shaft 11, meaning both the mandrel 121 and the connecting shaft 11 are hollow shafts. The other end of the connecting shaft 11 is connected to the active drill rod 10. The mandrel 121 is connected to and rotatably connected to the water inlet assembly. A bearing seat 125 is also provided to support the mandrel 121, and a mandrel support bearing 126 is sleeved on the outer circumference of the mandrel 121 inside the bearing seat 125. The water inlet assembly includes a housing 122 and a water inlet hole 124. The housing 122 has a water supply chamber 123 communicating with the water inlet hole 124. The connecting shaft 11 has an external thread near the active drill rod 10 for threaded connection with the rear end of the active drill rod 10. The connecting shaft 11 has an internal thread near the water braid 12 for threaded connection with the mandrel 121, so as to transfer the drilling medium flowing into the water braid 12 to the active drill rod 10 and connect the active drill rod 10 and the water braid 12. The mandrel 121 is connected to the active drill rod 10 and rotates together with it during operation. The mandrel support bearing 126 ensures smooth rotation of the mandrel 121, reducing friction and wear during rotation and extending the service life of the equipment. The connecting shaft 11 and the hollow interior of the mandrel 121 allow pressurized fluid to be smoothly transmitted from the water inlet assembly to the active drill rod 10, ensuring a stable and continuous supply of drilling media and improving drilling efficiency. A grease nipple 1251 is provided on the bearing housing 125, communicating with the interior of the bearing housing 125. The grease nipple 1251 provides lubricating oil to the mandrel support bearing 126, maintaining lubrication, reducing friction under high load conditions, and extending the bearing's service life. Effective lubrication reduces bearing wear and heat accumulation, preventing bearing damage due to overheating and improving the reliability and durability of the equipment.

[0068] The water braid 12 is fixed to the gearbox 16 by a connecting sleeve 19, as shown in Figure 7. The connecting sleeve 19 includes a connecting flange, with oblong holes 191 on both the upper and lower sides for bolts to pass through, ensuring connection stability. A hexagonal hole is located in the center of the connecting sleeve 19. The right end of the mandrel 121 is a regular hexagon that mates with the hexagonal hole and is axially slidably connected to it. In use, the end of the mandrel 121 is inserted into the hexagonal hole, allowing the connecting sleeve 19 to rotate with the spindle 15, thus driving the mandrel 121 to rotate. The connecting flange is threadedly fixed to the spindle 15. A gap (at point M in Figure 6) is left between the inner end face of the connecting sleeve 19 facing the active drill rod 10 and the end face of the connecting shaft 11, allowing the limiting section 104 to slide axially along the chuck 14, enabling the active drill rod 10 to float axially a certain distance. The internal and external threads of the connecting shaft 11 achieve a stable connection with the active drill rod 10 and the mandrel 121. The bearing housing 125 and the housing 122 are fixedly connected by bolts. The mandrel 121 on both sides of the water inlet hole 124 is fitted with a sealing ring between itself and the housing 122 to achieve sealing of the drilling medium.

[0069] As shown in Figure 8, the brake assembly 18 includes a brake cover 181, a clamping piston 182, and a releasing piston 183. A sliding shaft 184 is provided inside the brake cover 181. The left end of the drive shaft 186 extends into the center of the clamping piston 182. Multiple brake slips 185 are distributed circumferentially on the drive shaft 186. In this embodiment, the number of brake slips 185 is three. The clamping piston 182 is sleeved on the outside of the brake slip 185 and can move axially along the drive shaft 186. The surface of the brake slip 185 away from the drive shaft 186 is an inclined surface. The surface of the clamping piston 182 opposite to the brake slip 185 is a slope that matches the inclined surface of the brake slip 185. The clamping piston 182 can slide to clamp the drive shaft 186 by pushing the brake slip 185 radially. The releasing piston 183 is slidably sleeved on the sliding shaft 184 and can push the clamping piston 182 to release the clamping. The surface of the clamping piston 182 opposite to the brake slip 185 is a slope that matches the inclined surface of the brake slip 185. The clamping piston 182 can slide so that its internal slope contacts the inclined surface of the brake slip 185. The drive shaft 186 is clamped by the radial movement of the brake slip 185, thereby restricting the rotation of the drive shaft 186. The axial sliding of the clamping piston 182 and the radial movement of the brake slip 185 enable rapid clamping and release of the drive shaft 186. The cooperation between the inclined plane and the slope provides a stable clamping force, ensuring that the drive shaft 186 will not slip during operation, ensuring the reliability of clamping the drive shaft 186, and adapting to drive shafts 186 of different diameters. Even if the surface of the drive shaft 186 is worn, stable clamping can be achieved by extending the sliding distance of the clamping piston 182. It has strong versatility and can be applied to various types of drilling rig power heads 1.

[0070] The brake cover 181 has a first oil inlet 187 and a second oil inlet 188. The first oil chamber is formed between the side of the release piston 183 away from the clamping piston 182 and the brake cover 181. The first oil inlet 187 can supply hydraulic oil to the first oil chamber. The side of the clamping piston 182 away from the release piston 183 has a second oil chamber. The second oil inlet 188 can supply hydraulic oil to the second oil chamber. Both the inner and outer walls of the release piston 183 are provided with sealing rings. The outer wall of the clamping piston 182 is also provided with sealing rings. The sealing rings effectively prevent hydraulic oil leakage and ensure that the pressure in the hydraulic structure remains stable. Pressurized oil enters the second oil chamber through the second inlet 188, pushing the clamping piston 182 to the left, causing its internal slope to contact the inclined surface of the brake slip 185. This pushes the brake slip 185 inward and restricts its radial displacement, thereby clamping the drive shaft 186 and braking it. Pressurized oil enters the first oil chamber through the first inlet 187, pushing the release piston 183 to move. Its end face pushes the clamping piston 182 to the right, releasing the radial displacement restriction on the brake slip 185 and thus releasing the rotation restriction on the drive shaft 186. The automatic control of the brake assembly 18 is achieved through hydraulic pressure, improving the automation level and efficiency of the operation. Hydraulic pressure provides stable and adjustable pressure, ensuring the accuracy of the clamping and releasing process. Furthermore, hydraulic pressure has high stability and reliability, ensuring that the brake assembly 183 can work stably under various operating conditions, reducing the failure rate and maintenance costs.

[0071] In existing directional drilling rig power heads 1 (such as the patent with publication number CN116905958A), when it is necessary to replace the active drill rod 10, the front end cover 13 needs to be removed before unlocking the active drill rod 10. Since one end of the connecting shaft 11 is threaded to the active drill rod 10 and the other end is threaded to the spindle 121 of the water braid 12, when rotating the active drill rod 10 to unlock it, it is not possible to accurately unlock the active drill rod 10 from the connecting shaft 11. It is possible that the connecting shaft 11 is unlocked from the spindle 121 of the water braid 12. Since the space from the front end of the chuck 14 to the clamp is very limited, even removing the active drill rod 10 alone in the narrow operating space will bring difficulties to the operation. If the connecting shaft 11 is unlocked from the spindle 121 of the water braid 12, the active drill rod 10 is removed from the front end. Removing the active drill rod 10 along with the connecting shaft 11 becomes extremely difficult. Furthermore, if it is necessary to switch to the chuck 14 to clamp the drill rod for operation, the water braid 12 needs to be removed from the rear end of the gearbox 16, and the water braid 12 and connecting shaft 11 need to be removed from the rear end of the gearbox 16. Then, the end cover needs to be removed to take out the active drill rod 10. During this process, it cannot be guaranteed that the connecting shaft 11 will be unlocked from the active drill rod 10. If the connecting shaft 11 is unlocked from the spindle 121 of the water braid 12, the active drill rod 10 and connecting shaft 11 need to be removed from the front end of the gearbox 16 together before the drill rod can be installed into the chuck 14 and switched to the chuck 14 for clamping. Therefore, the existing technology makes it very difficult to replace the active drill rod 10 or switch to the chuck 14 to clamp the drill rod for operation, which seriously affects the construction efficiency.

[0072] In this embodiment, after improving the power head 1, when the active drill rod 10 needs to be replaced, due to the ample operating space at the rear end of the gearbox 16, it is only necessary to first loosen the chuck 14, and then remove the entire assembly connecting the water braid 12, connecting shaft 11, and active drill rod 10 from the rear end of the gearbox 16. This allows for the rapid replacement of the damaged active drill rod 10. Then, the new active drill rod 10, connecting shaft 11, and water braid 12 are installed into the gearbox 16 from the rear end, and the active drill rod 10 is then passed sequentially through the main shaft 15, chuck 14, and front end cover 13, thus quickly completing the replacement of the active drill rod. The replacement of rod 10 reduces uncontrollable factors during the replacement process and increases construction efficiency. When it is necessary to switch to the work of retrieval drill rod, the above disassembly process is repeated. During installation, the retrieval drill rod only needs to be inserted into the main shaft 15 from the rear end of the gearbox 16, and then passed through the chuck 14 and the front cover 13 in sequence. Finally, the retrieval drill rod is clamped by the chuck 14 and rotated. At the same time, part of the active drill rod 10 in this technical solution is located in the chuck 14 and the main shaft 15, so that when the main shaft 15 drives the active drill rod 10 to rotate through the chuck 14, the rotation of the active drill rod 10 is more stable and can be more accurately connected with the drill rod.

[0073] Next, the hydraulic system connected to the chuck 14 of the existing power head 1 usually only has two states: loose and clamp, and does not have a graded control function. In actual operation, the hydraulic system controls the chuck 14 to clamp under high pressure for a long time, which can easily damage the active drill rod 10 and generate unnecessary energy consumption.

[0074] As shown in Figure 9-11, the staged hydraulic system includes a pressure reducing valve 41, a solenoid directional valve 42, a hydraulically controlled directional valve 43, a main pump, and an auxiliary pump. The solenoid directional valve 42 is a three-position four-way solenoid directional valve with ports A, B, P, and T. The hydraulically controlled directional valve 43 has ports P, T, A, and a hydraulically controlled port. The chuck 14 has a control port. Port A of the hydraulically controlled directional valve 43 is connected to the control port of the chuck 14. The main pump is connected to port P of the hydraulically controlled directional valve 43. The auxiliary pump's oil circuit is divided into two streams: one connects to the P port of the hydraulic directional valve 43, and the other connects to the P port of the solenoid directional valve 42 via the pressure reducing valve 41. The drain port of the pressure reducing valve 41 is connected to the T port of the solenoid directional valve 42 for draining oil. The oil outlet of the A port of the solenoid directional valve 42 is divided into two streams: one connects to the P port of the hydraulic directional valve 43, and the other connects to the hydraulic control port of the hydraulic directional valve 43. The B port of the solenoid directional valve 42 is connected to the T port of the hydraulic directional valve 43. The hydraulic directional valve 43 is a two-position three-way hydraulic directional valve 43. By controlling the oil circuit, it can automatically switch the direction of oil flow. Through the coordinated control of the solenoid directional valve 42 and the hydraulic directional valve 43, it can achieve precise adjustment of the pressure of the chuck 14, adapting to the needs of different working conditions. In normal drilling and fishing operations, it can quickly switch the direction of oil flow, ensuring that the chuck 14 is adjusted to the required state in the shortest possible time, thus improving work efficiency. The main pump flows to the P port of the hydraulic directional valve 43 via the first check valve 45, and the oil circuit of the auxiliary pump is connected to the P port of the hydraulic directional valve 43 via the second check valve 46; the A port of the solenoid directional valve 42 is connected to the P port of the hydraulic directional valve 43 via the third check valve 47; the pressure reducing valve 41 is a fixed-value pressure reducing valve 41, which can adjust the oil pressure to 6 MPa in this embodiment; in this embodiment, the solenoid directional valve 42 has Y1 position and Y2 position, and also includes an oil tank 44 for storing oil. The oil tank 44 is used to supply oil to the main pump and the auxiliary pump, and the oil supply flows back to the oil tank 44.

[0075] As shown in Figure 9, when the chuck 14 is released, positions Y1 and Y2 are de-energized. When both the left position Y1 and the right position Y2 of the solenoid directional valve 42 are de-energized, the solenoid directional valve 42 is in the neutral position, and the hydraulic directional valve 43 operates in the right position under the action of the spring force. When the pressure oil P1 from the main pump passes through the first check valve 45 to the outlet of the second check valve 46, the outlet of the third check valve 47, and the P port of the hydraulic directional valve 43, the oil flow is cut off. At the same time, one stream of pressure oil from the auxiliary pump P2 flows through the second check valve 46 to the outlet of the first check valve 45, the outlet of the third check valve 47, and the P port of the hydraulic directional valve 43, and the oil flow is cut off; another stream of pressure oil from the auxiliary pump P2 flows through the pressure reducing valve 41 to the P port of the solenoid directional valve 42, which is also cut off. The pressurized oil in the chuck 14 returns to the oil tank 44 through the right position of the hydraulic directional valve 43 and the middle position of the solenoid directional valve 42, and the chuck 14 is in the released state. At the same time, the control oil of the hydraulic directional valve 43 is discharged to the oil tank 44 through the middle position of the solenoid directional valve 42. The chuck 14 is in the released state and will not clamp or limit the active drill rod 10.

[0076] As shown in Figure 10, under the condition of low-pressure clamping of chuck 14, Y2 is energized. When Y2 is energized in the right position of solenoid directional valve 42, solenoid directional valve 42 is in the right-position working state, and hydraulic directional valve 43 is in the right-position working state under the action of spring force. The pressure oil from main pump P1 flows through the first check valve 45 to the outlet of the second check valve 46 and the outlet of the third check valve 47, and is cut off at port P of hydraulic directional valve 43. The control oil of hydraulic directional valve 43 is discharged to oil tank 44 through the right position of solenoid directional valve 42. One stream of pressurized oil from the auxiliary pump P2 passes through the second check valve 46 to the outlet of the first check valve 45, the outlet of the third check valve 47, and the P port of the hydraulic directional valve 43, where the oil flow is cut off. Another stream of oil passes through the pressure reducing valve 41 to the set pressure of 6MPa. Then, the pressurized oil flows through the right position of the solenoid directional valve 42 and then through the right position of the hydraulic directional valve 43 to the chuck 14. At this time, the chuck 14 is in a low-pressure clamping state of 6MPa, which limits the movement of the active drill rod 10.

[0077] As shown in Figure 11, under the condition of high-pressure clamping of chuck 14, Y1 is energized, solenoid directional valve 42 is in the left-hand working state, and hydraulic directional valve 43 is in the left-hand working state under the action of control oil. The pressure oil P1 from the main pump flows through the first check valve 45 to the outlet of the second check valve 46 and the outlet of the third check valve 47, and finally flows into chuck 14 through the left-hand position of hydraulic directional valve 43. The pressure oil P2 from the auxiliary pump is divided into two oil paths. One oil path is reduced to 6MPa through pressure reducing valve 41, flows through the left-hand position of solenoid directional valve 42 to the control port of hydraulic directional valve 43, causing hydraulic directional valve 43 to switch and be in the left-hand working state; the other oil path is through the second check valve 46 to the outlet of the first check valve 45 and the outlet of the third check valve 47, and finally flows into chuck 14 through the left-hand position of hydraulic directional valve 43. In this state, the main and auxiliary pumps merge to form a high-pressure oil source, which puts the chuck 14 in a high-pressure clamping state for retrieval.

[0078] The graded hydraulic system controls the chuck 14 to switch between three states: loose, low-pressure clamping, and high-pressure clamping. The loose state is primarily used when the power head 1 is not operating or when drill rods are being loaded into the chuck 14. Low-pressure clamping is primarily used when drilling is performed using the active drill rod 10 connected to the drill rod. High-pressure clamping is primarily used when the chuck 14 is holding the drill rod during drilling. By controlling the clamping pressure of the chuck 14 in stages, and by setting the diameter of the active drill rod 10's limiting section 104 to be slightly smaller than the inner diameter of the chuck 14's clamping mechanism, the system improves the stress distribution on the active drill rod 10, avoids energy waste caused by prolonged pressure buildup in the chuck 14, and enhances the adaptability of the power head 1 to various working conditions, including normal drilling and retrieval drilling.

[0079] Next, referring to Figures 12-20, improvements to the existing clamping device will be explained based on its shortcomings in drill pipe assembly and disassembly.

[0080] As shown in Figure 12, the clamp is a double clamp, including a base 2, a front clamp, and a rear clamp. The base 2 has a front clamp mounting part and a rear clamp mounting part, which are used to install the front clamp and the rear clamp, respectively. Referring to Figure 13, the bottom surface of the base 2 is a mounting plate 201. The front clamp mounting part includes a front support plate 203 and a rear support plate 205 symmetrically spaced on the mounting plate 201. Both the front support plate 203 and the rear support plate 205 have a through hole, and the two through holes are coaxial. An opening is provided at the upper end of each through hole, and the width of the opening is greater than or equal to the diameter of the large drill bit (in this embodiment, the large drill bit is a bottom hole motor). The added opening makes the through holes of the front support plate 203 and the rear support plate 205 that accommodate the drill rod open upwards, allowing the drilling rig to be operated from top to bottom when changing large-diameter drill rods, such as bottom hole motors.

[0081] Due to the limitations of the drilling rig structure, there are generally two methods used when replacing drill rods with larger diameter ones at existing construction sites: one is to tilt the bottom-hole motor at a certain angle relative to each axis (i.e., the drilling axis) of the chuck's through hole before inserting it into the chuck. However, this method has a very limited scope of application; when the distance between the chuck and the hole wall is too small, the excessively tilted bottom-hole motor will not be able to align with the inner hole of the chuck. The other method is to remove the entire chuck, install the bottom-hole motor and send it into the hole, and then reinstall the chuck. This method has a wider scope of application and can be used even when the distance between the chuck and the hole wall is very small. However, the chuck is large, heavy, and complex in structure, and disassembling it completely consumes a lot of manpower and construction time, seriously reducing construction efficiency. The operation also poses significant safety hazards and is quite difficult. This embodiment adds an opening, changing the original method of pulling and disassembling the drill rod along the front and rear ends of the through hole axis to directly taking it out or putting it in from above the through hole, greatly reducing the space required for disassembly and also reducing the difficulty of replacing the drill rod.

[0082] As shown in Figure 13, a reinforcing plate 204 can be detachably connected to the openings of both through holes. Taking the front support plate 203 as an example, the connection method of the reinforcing plate 204 is as follows: a protrusion and a groove are provided on the top of the front support plate 203, and a groove and a protrusion matching the protrusion and groove on the top of the front support plate 203 are provided on the bottom of the reinforcing plate 204. The upper and lower protrusions and grooves interlock and nest to form a complete plane, which not only improves the overall structural strength of the support plate 221, but also facilitates the positioning assistance when installing the reinforcing plate 204. Finally, the reinforcing plate 204 is fixed to the front support plate 203 with screws or pins. The reinforcing plate 204 ensures the integrity of the through holes during drilling operations and avoids safety accidents caused by the through holes breaking open.

[0083] As shown in Figures 12 and 14, a swing body 22 is provided between the front support plate 203 and the rear support plate 205. The swing body 22 includes two support plates 221 arranged symmetrically front and rear. Both support plates 221 have guide mounting holes, and connecting flanges are provided in the guide mounting holes. In the direction of Figure 14, a flipping shaft seat 25 is provided on the lower right side of the support plate 221. A front cylinder mounting plate 222 is connected to the outer end face of each of the two support plates 221. A front clamping cylinder 23 is bolted to the front cylinder mounting plate 222. A swing lug seat 224 is fixedly connected to the lower part of the front cylinder mounting plate 222 near the flipping shaft seat 25. A swing cylinder 226 is rotatably connected to the swing lug seat 224 through a rotating shaft. Four front liner plates 223 are symmetrically arranged between the two support plates 221. The four front liner plates 223 are spliced ​​to form a guide space for the movement of the piston rod of the clamping cylinder, while also providing support for the swing component structure. Meanwhile, as shown in Figure 13, a flip plate 202 is fixedly connected to the front support plate 203 and the rear support plate 205 near the flip shaft seat 25. The flip plate 202 is provided with a flip hole, and a flip pin 227, which serves as the flip axis of the swing body 22, is installed in the flip hole. The swing body 22 is the main connecting component of the various parts in the front clamp, connecting the front clamping cylinder 23 and the base 2 into one unit, and connecting the front clamp and the frame 3 of the drilling rig into one unit through the swing cylinder 226.

[0084] As shown in Figure 12, the swing cylinder 226 is the driving element that drives the swing body 22 to rotate around the flip pin 227. The piston rod of the swing cylinder 226 is hinged to the swing lug 224 of the swing body 22 via a pin, and the cylinder barrel of the swing cylinder 226 is hinged to the frame 3 of the drilling rig via a pin. The flip pin 227 is the axis of the swing body 22's rotation. One end of the flip pin 227 near the swing body 22 is inserted into the flip shaft seat 25 of the swing body 22, and the other end is inserted into the through hole of the flip plate 202 of the base 2, and is limited at the end by a cotter pin or retaining ring. The swing body 22 mechanically swings out of the base 2 by switching the rotation center. Combined with the detachable reinforcing plate 204 structure of the base 2, a large amount of space is freed up inside and above the front clamp, enabling the installation of the hole-bottom motor from top to bottom. This process only requires disassembling and assembling a few parts, which reduces the space requirement of the front end of the clamp for the hole-bottom motor installation and saves a lot of time and manpower for the overall removal of the clamp.

[0085] The gripper clamps the drill pipe by connecting slips to the piston rods of two symmetrically arranged clamping cylinders. To address the need for larger diameter drill pipes in drilling rigs, this embodiment further improves the design of the slips in the gripper. As shown in Figures 15 and 16, each slip includes an outer slip 24 and an inner slip 240. The inner surface of the outer slip 24 has several protrusions or small sharp teeth to increase the friction between the slip and the drill pipe. The diameter of the arc segment on the inner surface of the outer slip 24 matches the outer diameter of the inner slip 240. Three countersunk holes are formed on the inner surface of the outer slip 24 for installing screws connecting the piston rods in the clamping cylinders. A flat surface is provided at the top and bottom of the arc segment, with threaded holes for installing screws connecting the inner slip 240. A locking block is provided at each of the four corners of the flat surface. The four locking blocks, with their symmetrical stop surfaces, combine with the arc surface to form an installation space for connecting the inner slip 240. The inner slip 240 has symmetrical bosses on both its upper and lower sides. The side of each boss facing the center of the gripper has a countersunk hole for installing screws connecting to the outer slip 24. The outer diameter of the inner slip 240 matches the inner diameter of the outer slip 24 for easy installation. The inner surface of the inner slip 240 also has several protrusions or small sharp teeth for more stable clamping. The front projection of the inner slip 240 is a cross shape, which mates with the four stop surfaces on the outer slip 24 to achieve positioning along the front-rear axial direction of the gripper.

[0086] The inner diameter of the inner slip 240 matches the outer diameter of the smaller diameter drill pipe, while the inner diameter of the outer slip 24 matches the outer diameter of the larger diameter drill pipe. This allows for adjustment of the clamping mechanism by removing or adding the inner slip 240 when changing drill pipes of different sizes. The replacement operation is simply achieved by loosening the screws to remove or install the inner slip 240, further improving the ease of operation of this dual clamping device. The cylinder barrels of the front clamping cylinder 23 are symmetrically fixed to the front cylinder mounting plates 222 on both sides of the swing body 22. The piston rods of the front clamping cylinder 23 extend from both sides of the front clamping device towards the center, and clamp the drill pipe via the slips on the piston rod.

[0087] When replacing the inner slip 240, the piston rod of the clamping cylinder retracts, creating an open space for removing and installing the slip. Only a few screws need to be removed and installed for quick slip replacement, making the operation convenient and fast. Furthermore, the inner slip 240 uses a large flat surface for axial positioning along the gripper, while the screws achieve radial positioning along the arc. The flat surface absorbs the shear force for the screws, significantly reducing the possibility of screw deformation and improving positioning reliability, thus preventing slippage during unscrewing.

[0088] Furthermore, the nested structure of inner and outer slips 24 and inner and outer guide sleeves 21 enables rapid adaptation to drill string specifications and replacement of accessories, and also expands the applicability of the clamp, especially suitable for directional drilling rigs using special drill strings such as ordinary drill pipes, fishing drill pipes, and bottom hole motors. Moreover, the integrated design of the clamp and guide sleeves ensures the guiding function of the drill pipe entering and exiting the clamp while saving space on the drilling rig.

[0089] As shown in Figures 12 and 17, the front clamp also includes a guide sleeve assembly, which includes an outer guide sleeve 21 and an inner guide sleeve 210. The inner guide sleeve 210 and the outer guide sleeve 21 are detachably connected to the through hole, so as to integrate the guide sleeve into the clamp, thereby saving installation space and making the overall layout of the drilling rig more compact.

[0090] As shown in Figure 19, the outer diameter of the inner guide sleeve 210 is divided into two stages. The small diameter section of the inner guide sleeve 210 mates with the guide mounting hole on the swing body 22, and the large diameter section of the inner guide sleeve 210 mates with the through holes in the middle of the front support plate 203 and the rear support plate 205 of the base 2 to achieve axial positioning. At the same time, the inner diameter of the inner guide sleeve 210 is also divided into two stages. The small diameter section of the inner diameter is a through hole of equal diameter, which mates with the small diameter section of the outer guide sleeve 21. The large diameter section of the inner diameter is a countersunk stage, which mates with the outer guide sleeve 21. As shown in Figure 18, the outer guide sleeve 21 also has two-stage outer diameters. The large-diameter section of the outer guide sleeve 21 has a countersunk connecting hole for mounting screws to fix the outer guide sleeve 21 and inner guide sleeve 210 onto the swing body 22. The bottom surface of the countersunk stage of the large-diameter section of the inner guide sleeve 210 has a through hole corresponding to that of the outer guide sleeve 21. Screws are installed in the through hole to fix the outer guide sleeve 21 and inner guide sleeve 210 onto the swing body 22. Referring to Figure 17, the large-diameter section of the outer guide sleeve 21 mates with the countersunk stage of the inner guide sleeve 210 to achieve axial positioning of the outer guide sleeve 21. The inner diameter of the outer guide sleeve 21 matches the smaller outer diameter of the drill rod that can be used with the drilling rig, guiding the drill rod as it enters and exits the clamp. The inner guide sleeve 210 and outer guide sleeve 21 have significantly different structures, facilitating on-site parts management and identification.

[0091] Finally, referring to Figures 12 and 13, the rear clamp mounting part includes a symmetrically arranged front side plate 209 and a rear side plate 207. The front side plate 209 and the rear side plate 207 serve as support members for the rear clamp. A U-shaped hole is provided in the middle of both the front side plate 209 and the rear side plate 207, allowing the tops of the front side plate 209 and the rear side plate 207 to be completely open. Four rear liner plates 206 are symmetrically arranged between the front side plate 209 and the rear side plate 207. The four rear liner plates 206 form a guide space for the movement of the rear clamping cylinder 230 and the cylinder piston rod, and also serve as structural supports. Rear cylinder mounting plates 208 are connected to the outer end faces of both sides of the front side plate 209 and the rear side plate 207. The rear clamping cylinder 230 is fixedly connected to the rear cylinder mounting plate 208 by bolts. As shown in Figure 20, each U-shaped hole is connected to a semi-circular guide sleeve 25. The outer diameter of the semi-circular guide sleeve 25 is also divided into two stages. The smaller diameter section of the semi-circular guide sleeve 25 mates with the U-shaped hole, and the larger diameter section of the semi-circular guide sleeve 25 has a countersunk connecting hole on its end face. The countersunk connecting hole is used to install screws to fix the semi-circular guide sleeve 25 to the front side plate 209 or the rear side plate 207. The inner diameter of the semi-circular guide sleeve 25 that mates with the U-shaped hole can be matched with drill rods of different outer diameters on the drilling rig. The drill rod is inserted into the clamp through the top opening.

[0092] In traditional drilling rig structures, the clamp and guide sleeve are generally located as two independent components at the front end of the frame 3, occupying a significant amount of length space. To save space in the drilling direction, some drilling rigs have even eliminated the guide sleeve altogether. The traditional guide sleeve is a rotatable hollow cylinder, and one inner sleeve can only accommodate drill pipes of one outer diameter. When changing drill pipes, the guide sleeve must be replaced entirely or the inner sleeve must be replaced separately to accommodate the new drill pipe's outer diameter. Replacing the entire guide sleeve is simpler, but the spare parts cost is higher; replacing the inner sleeve separately is more complex, but the cost is lower, and this is the commonly used method in the field. Replacing the inner sleeve separately also presents a challenge in parts identification and management. Because the specifications of the drill pipes used on the same drilling rig are similar, the diameter difference is generally around 10mm, which translates to a difference of only a few millimeters in the inner sleeve thickness. Identifying such a small difference without measuring tools in the downhole field is extremely difficult, making on-site parts management challenging. The method of assembling a guide sleeve on the clamp in this embodiment solves this problem, further improving the ease of operation of the dual clamp, reducing the difficulty of changing drill rods during drilling, and improving work efficiency.

[0093] Finally, as shown in Figure 21, in response to the slippage phenomenon of the existing clamp during drill pipe uncoupling operations, this embodiment proposes an anti-slippage hydraulic system. By connecting the hydraulic motor 17 in the power head 1 to control the oil circuit and the clamping oil circuit 57 of the clamp, the pressure is increased during drill pipe uncoupling to achieve the purpose of preventing slippage.

[0094] The front clamping device is driven by the front clamping cylinder 23, and the rear clamping device is driven by the rear clamping cylinder 230. As shown in Figure 21, both the front clamping cylinder 23 and the rear clamping cylinder 230 are connected to clamping oil circuit 57 and releasing oil circuit 58, respectively, to provide hydraulic power for the movement of the cylinder piston rod. The two oil circuits on the front clamping cylinder 23 are connected to the front hydraulic lock 53, and the two oil circuits on the rear clamping cylinder 230 are connected to the rear hydraulic lock 56. The working principle of the hydraulic system is specifically explained using the front clamping cylinder 23 as an example: the clamping oil circuit 57 is connected to the rodless chamber of the front clamping cylinder 23, and the releasing oil circuit 58 is connected to the rod chamber of the front clamping cylinder 23. When oil is supplied to the clamping oil circuit 57, the internal pressure of the rodless chamber increases, thereby pushing the piston rod to move outward and clamping the drill pipe through the connected slips. Meanwhile, the hydraulic motor 17 serves as the driving active component of the power head 1. The hydraulic motor 17 is connected to a forward rotation oil circuit 51 and a reverse rotation oil circuit 52. When the forward rotation oil circuit 51 is filled with oil, it drives the hydraulic motor 17 to drive the power head 1 to rotate forward. When the reverse rotation oil circuit 52 is filled with oil, it drives the hydraulic motor 17 to drive the power head 1 to rotate in reverse.

[0095] A branch oil circuit is provided between the reversing oil circuit 52 and the clamping oil circuit 57 for connection. A front check valve 54 is installed on the branch oil circuit, allowing oil from the reversing oil circuit 52 to flow only into the clamping oil circuit 57. During drill pipe uncoupling, the hydraulic motor 17 drives the power head 1 to reverse. At this time, oil flows through the reversing oil circuit 52, and a portion of the hydraulic oil flows through the front check valve 54 to the two rodless chambers of the front clamping cylinder 23. This replenishes the leaking hydraulic oil in the front clamping cylinder 23, improving the clamping strength of the front clamp and preventing slippage. By directly utilizing the hydraulic oil in the reversing oil circuit 52, the hydraulic oil replenishment for the clamping cylinder during clamping operations can be achieved without adding a new oil supply inlet. This reduces the complexity of the hydraulic system structure, lowers modification costs, and further ensures the timeliness and synchronization of hydraulic oil replenishment to the rodless chambers of the clamping cylinder. When the unhooking is completed, the reverse operation of the power head 1 stops, and the oil supply to the reverse oil circuit 52 is suspended. The replenishment of hydraulic oil to the rodless chamber can also be suspended simultaneously. At this time, even if the pressure in the clamping oil circuit 57 is greater than the internal pressure of the reverse oil circuit 52, the hydraulic oil will not flow back to the reverse oil circuit 52 under the reverse shut-off protection of the check valve, thereby improving the safety of the hydraulic system operation.

[0096] The front hydraulic lock 53 provides hydraulic oil pressure protection for the front clamping cylinder 23 in the clamping or releasing state. When hydraulic oil enters the front clamping cylinder 23 through the clamping oil circuit 57 or the releasing oil circuit 58 and then through the front hydraulic lock 53, the oil supply stops, and the front hydraulic lock 53 immediately enters a pressure-holding state to prevent hydraulic oil from flowing out of the front clamping cylinder 23, ensuring the stability of the front counterweight clamp in the clamping or releasing state. In this embodiment, the outlet of the front one-way valve 54 is connected to the outlet of the rodless chamber of the front clamping cylinder 23 connected to the front hydraulic lock 53.

[0097] A rear check valve 55 connects the clamping oil circuit 57 of the rear clamping cylinder 230 to the reversing oil circuit 52, and the front check valve 54 and the rear check valve 55 are interconnected to simplify the hydraulic system circuit and ensure synchronization of the two clamps. Furthermore, considering that in practical applications, there may be situations where only one clamping clamp is used, such as the front clamp clamping and the rear clamp releasing. In this case, under the reverse cut-off action of the front check valve 54, the rodless chamber of the front clamping cylinder 23 and the rodless chamber of the rear clamping cylinder 230 are not interconnected. Therefore, although the oil circuits at the inlets of the front check valve 54 and the rear check valve 55 are connected, it will not affect the oil circuit control of the rear clamping cylinder 230 in the released state of the rear clamp. Moreover, under the cut-off action of the rear check valve 55, the normal operation of the reversing oil circuit 52 of the hydraulic motor 17 will not be affected, further ensuring the safety of the hydraulic system operation.

[0098] When the hydraulic motor 17 rotates forward, oil enters through the forward rotation oil circuit 51 and returns through the reverse rotation oil circuit 52. During the return flow of oil through the reverse rotation oil circuit 52, some hydraulic oil inevitably flows to the forward check valve 54 and the rear check valve 55, which may affect the gripper, which should be kept in a released state. Therefore, the opening pressures of the forward check valve 54 and the rear check valve 55 are set higher than the return pressure in the reverse rotation oil circuit 52. This ensures that the inlet valves of the check valves will not open under these conditions, preventing the branch oil circuit configuration from affecting the operational safety and stability of the original equipment. Furthermore, when both clamps are in the released state, the rod chamber in the clamping cylinder is under high pressure due to the pressure holding effect of the hydraulic lock, while the rodless chamber is in the low-pressure return chamber state. At this time, even in the extreme case of check valve failure, the pressure difference between the rod chamber and the rodless chamber can ensure that the released state of the two clamps is not affected. This forms a double insurance effect of releasing and maintaining the clamps, ensuring that the clamps in this hydraulic system will not affect the normal drilling work, and further ensuring the safety of construction.

[0099] By connecting the reverse oil circuit 52 of the hydraulic motor 17 and the clamping oil circuit 57 of the clamping cylinder in the clamp, and by setting a one-way valve and cooperating with a hydraulic lock, a hydraulic system for preventing slippage of the top clamp is formed, in which reverse linkage pressurization, forward rotation and individual clamping do not affect each other. This solves the problem of slippage caused by the decrease in clamping force due to leakage of the clamping cylinder and hydraulic lock in the existing hydraulic system of the top clamp, ensuring on-site construction safety and improving construction efficiency.

[0100] The specific implementation process is as follows:

[0101] When the system is performing directional drilling.

[0102] Initial state: The drive drill rod 10 and connecting shaft 11 are installed on the power head 1. No drill rod is connected to the drive drill rod 10. The brake assembly 18 is in the released state. The rear clamp is released, and the front clamp is clamped. The distance between the power head 1 and the clamp is sufficient to accommodate the drill rod to be received. The hydraulic system of the chuck 14 is always in a low-pressure clamping state. The drill rod to be received is placed into the rear clamp, and the rear clamp clamps.

[0103] The power head 1 drives the active drill rod 10 to rotate forward and move forward. The active drill rod 10 and the drill rod to be connected are engaged. The power head 1 then stops rotating and moving forward. The rear clamp is released. The power head 1 drives the active drill rod 10 to rotate forward and move forward. The drill rod to be connected is engaged with the drill rod clamped by the front clamp. The power head 1 then stops rotating and moving forward.

[0104] When the front clamp is released, the brake assembly 18 switches to braking mode, and normal directional drilling can be carried out. After the drilling of the current drill rod is completed, all components return to the initial state, and the cycle repeats.

[0105] When the system performs directional drilling withdrawal.

[0106] Initial state: The active drill rod 10 and connecting shaft 11 are installed on the power head 1. The active drill rod 10 is connected to the drill rod exposed in the hole (i.e., the drill rod to be disassembled). The brake assembly 18 is in braking condition. Both the front and rear clamps are released. The swing cylinder 226 on the front clamp is not swinging in the forward direction (the same as the forward rotation direction of the power head 1). The power head 1 is located at the front end of the frame 3 (i.e., just completed the drilling of one drill rod). The hydraulic system of the chuck 14 is always in a low-pressure clamping state.

[0107] The power head 1 retracts, positioning the threaded end of the drill rod to be disassembled between the front and rear clamps without being clamped. With both clamps engaged, the brake assembly 18 switches to the release position. The swing body 22 of the front clamp swings forward under the drive of the swing cylinder 226, pre-loosening the threaded end of the drill rod to be disassembled. The rear clamp releases, and the power head 1 drives the active drill rod 10 to reverse and retract until the threaded end is completely loosened, at which point the power head 1 stops rotating and retracting. The rear clamp engages again, and the power head 1 drives the active drill rod 10 to reverse and retract until the thread between the active drill rod 10 and the drill rod to be disassembled is completely loosened, at which point the power head 1 stops rotating and retracting.

[0108] Remove the drill rod to be disassembled, push the power head 1 to the front end and connect it with the next drill rod to be disassembled, and return all parts to their initial state. Repeat this process.

[0109] When the system is performing rotary drilling.

[0110] The process is the same as directional drilling, except that the brake assembly 18 is in a released state throughout the entire drilling process.

[0111] When the system is performing rotary drilling operation.

[0112] The process is the same as directional drill retraction, except that the brake assembly 18 is in a released state throughout the entire drill retraction process.

[0113] When the system is performing drilling operations to retrieve the drill rod.

[0114] The process is the same as directional drilling, except that the brake assembly 18 is in the released state throughout the drilling process. The active drill rod 10, connecting shaft 11, and front end cover 13 are removed, and the drill rod is clamped using the chuck 14. The chuck 14 is in a high-pressure clamping state when clamping the drill rod, and the chuck 14 is in the released state when removing the drill rod from the chuck 14.

[0115] When the system is performing drill rod retrieval and drilling operation.

[0116] The process is the same as directional drill retraction, except that the brake assembly 18 is in the released state throughout the entire drill retraction process. The active drill rod 10, connecting shaft 11, and front end cover 13 are removed. The drill rod is clamped with chuck 14. The chuck 14 is in a high-pressure clamping state when clamping the drill rod. The chuck 14 is in the released state when the drill rod is removed.

[0117] In summary, the drill pipe installation system in this solution improves and upgrades the structure of the power head 1, the clamping device, and the hydraulic control systems of the chuck 14 and the clamping device. Within the limited structure of the original drilling rig, it achieves convenience in drill pipe installation, disassembly, and replacement. At the same time, it provides different controls for different construction needs during the construction process. It is suitable for mining drilling rigs that need to change drill bit specifications during downhole construction, and is especially suitable for directional drilling rigs that use ordinary drill pipes, fishing drill pipes, and special drill bits such as bottom hole motors.

[0118] The above descriptions are merely embodiments of the present invention, and common knowledge such as specific technical solutions and / or characteristics are not described in detail here. It should be noted that those skilled in the art can make various modifications and improvements without departing from the technical solutions of the present invention, and these should also be considered within the scope of protection of the present invention. These modifications and improvements will not affect the effectiveness of the implementation of the present invention or the practicality of the patent. The scope of protection claimed in this application should be determined by the content of its claims, and the specific embodiments described in the specification can be used to interpret the content of the claims.

Claims

1. A drill pipe installation system comprising a frame and a power head and a double gripper respectively provided at both ends of the frame, characterized in that: The power head comprises a main shaft, a water braid and a driving drill rod, the main shaft is internally provided with a connecting shaft, the water braid and the driving drill rod are respectively connected to two ends of the connecting shaft, the driving drill rod comprises a limiting section and a rotation-stopping section, one end of the main shaft is provided with a chuck, one end of the chuck is provided with a front end cover, the chuck is clamped on the limiting section, the front end cover is slidingly connected to the rotation-stopping section, the front end cover can drive the driving drill rod to rotate, the chuck is connected with a staged hydraulic system, and the staged hydraulic system can control the clamping pressure of the chuck on the limiting section. The double clamping device comprises a front clamping device and a rear clamping device, the front clamping device comprises front and rear support plates which are arranged at intervals, and the front and rear support plates are both provided with through holes; two through holes are both provided with openings, and the width of the openings is greater than or equal to the diameter of the large drilling tool; the front and rear support plates are provided with swing bodies, and the swing bodies can swing out of the front and rear support plates; The front and rear clamping devices are both connected with clamping oil cylinders, and the power head further comprises a hydraulic motor, a slip-preventing hydraulic system is arranged between the hydraulic motor and the clamping oil cylinders, and the slip-preventing hydraulic system can pressurize the clamping oil cylinders through the reverse oil circuit of the hydraulic motor during clamping operation.

2. The drill rod mounting system of claim 1, wherein: The driving drill rod comprises a rod body and a double-end joint arranged at one end of the rod body, the limiting section and the rotation-stopping section are both arranged on the rod body, the outer periphery of the rotation-stopping section is provided with a hexagonal shape, the inner part of the front end cover is provided with a hexagonal through hole, the diagonal distance of the hexagonal shape of the outer periphery of the rotation-stopping section is less than the diameter of the chuck after loosening, the outer diameters of the shaft sections on the two sides of the limiting section are both greater than the minimum diameter of the chuck after clamping, and the width of the limiting section is slightly greater than the clamping width of the chuck.

3. The drill rod mounting system of claim 2, wherein: The hydraulic motor is connected with a gearbox, the gearbox comprises a gear shaft and multiple gear stages, the power of the hydraulic motor is transmitted to the driving drill rod after speed change and torque increase, and the main shaft is arranged in the inner part of the gearbox.

4. The drill rod mounting system of claim 3, wherein: The water braid comprises a mandrel and a water inlet assembly, the mandrel is fixedly connected and communicated with the connecting shaft, and the mandrel is rotationally connected with the water inlet assembly; the water inlet assembly comprises a shell and a water inlet hole, the inner part of the shell is provided with a water supply cavity which is communicated with the water inlet hole; further comprising a bearing seat, the bearing seat supports the mandrel, and the bearing seat is provided with a grease nipple which is communicated with the inner part of the bearing seat.

5. The drill rod mounting system of claim 4, wherein: Further comprising a connecting sleeve, the connecting sleeve connects the water braid to one end of the gearbox which is away from the hydraulic motor; the connecting sleeve comprises a connecting flange, the connecting flange is provided with a waist-shaped hole for bolt penetration, and the end face of the connecting sleeve which faces the driving drill rod leaves a gap with the end face of the connecting shaft.

6. The drill rod mounting system of claim 5, wherein: The brake assembly comprises a brake cover, a clamping piston and a loosening piston, the brake cover is internally provided with a sliding shaft, one end of the transmission shaft extends into the center of the clamping piston, the transmission shaft is circumferentially provided with multiple brake slips, the clamping piston is sleeved on the brake slips and can move in the axial direction, the surface of the brake slip which is away from the transmission shaft is a slope, the surface of the clamping piston which is opposite to the brake slip is a slope surface which is matched with the slope of the brake slip, the clamping piston can slide through the brake slip to clamp the transmission shaft, and the loosening piston is slidingly sleeved on the sliding shaft and can push the clamping piston to release the clamping.

7. The drill rod mounting system of claim 1, wherein: The hierarchical hydraulic control system comprises a pressure reducing valve, an electromagnetic reversing valve, a hydraulic control reversing valve, a main pump and a secondary pump; the electromagnetic reversing valve is a three-position four-way electromagnetic reversing valve with A port, B port, P port and T port, and the electromagnetic reversing valve has Y1 position and Y2 position; the hydraulic control reversing valve is a hydraulic control reversing valve with P port, T port, A port and hydraulic control port, and the chuck has a control oil port, the A port of the hydraulic control reversing valve is connected with the control oil port of the chuck, and the main pump is connected with the P port of the hydraulic control reversing valve; the oil path of the secondary pump is divided into two, one is connected with the P port of the hydraulic control reversing valve, and the other is connected with the P port of the electromagnetic reversing valve through the pressure reducing valve; the oil discharge port of the pressure reducing valve is connected with the T port of the electromagnetic reversing valve and discharges oil; the oil outlet of the A port of the electromagnetic reversing valve is divided into two, one is connected with the P port of the hydraulic control reversing valve, and the other is connected with the hydraulic control port of the hydraulic control reversing valve, and the B port of the electromagnetic reversing valve is connected with the T port of the hydraulic control reversing valve.

8. The drill rod mounting system of claim 7, wherein: When the chuck is loosened, Y1 and Y2 positions are de-energized, the pressure oil from the main pump reaches the P port of the hydraulic control reversing valve and is cut off, and the pressure oil from the secondary pump flows through the pressure reducing valve and reaches the P port of the electromagnetic reversing valve and is cut off.

9. The drill rod mounting system of claim 8, wherein: When the chuck is clamped at low pressure, Y2 is energized, the pressure oil from the main pump reaches the P port of the hydraulic control reversing valve and is cut off, and the pressure oil from the secondary pump reaches the P port of the hydraulic control reversing valve and is cut off, and the other part of the pressure oil flows through the electromagnetic reversing valve, the hydraulic control valve and reaches the control port of the chuck.

10. The drill rod mounting system of claim 9, wherein: When the chuck is clamped at high pressure, Y1 is energized, the pressure oil from the main pump flows into the control port of the chuck through the hydraulic control reversing valve, and the pressure oil from the secondary pump reaches the control port of the hydraulic control reversing valve through the electromagnetic reversing valve, switches the working state of the hydraulic control reversing valve, reaches the control port of the chuck through the hydraulic control reversing valve, and the hydraulic oil from the main pump and the secondary pump flows together.

11. The drill rod mounting system of claim 1, wherein: The swing body comprises two support plates symmetrically arranged front and back, and guiding installation holes are arranged on the two support plates; a turnover shaft seat is arranged below one side of the support plate, and one front oil cylinder mounting plate is connected to the outer end face of each side of the two support plates, a front clamping oil cylinder is arranged on the front oil cylinder mounting plate, a swing ear seat is arranged below the front oil cylinder mounting plate close to the turnover shaft seat, and a swing oil cylinder is rotatably connected in the swing ear seat; a turnover plate is connected to one side of the front support plate and the rear support plate close to the turnover shaft seat, a turnover hole is arranged on the turnover plate, and a turnover pin shaft is arranged in the turnover hole.

12. The drill rod mounting system of claim 11, wherein: A reinforcing plate is detachably connected to each opening, and a plurality of recesses and protrusions matched with each other are arranged between the top of the front support plate and the rear support plate and the bottom of the reinforcing plate.

13. The drill rod mounting system of claim 12, wherein: A guiding sleeve group is arranged in each through hole, and the guiding sleeve group comprises an outer guiding sleeve and an inner guiding sleeve; the outer diameter of the inner guiding sleeve is divided into two levels, the small-diameter section of the inner guiding sleeve is matched with the guiding installation hole on the swing body, and the large-diameter section of the inner guiding sleeve is matched with the through hole on the front support plate and the rear support plate.

14. The drill rod mounting system of claim 13, wherein: The outer diameter of the outer guiding sleeve is divided into two levels, wherein a countersunk hole is arranged on the large-diameter section of the outer guiding sleeve, and the countersunk hole is used for connecting the outer guiding sleeve and the inner guiding sleeve on the swing body; the inner diameter of the inner guiding sleeve is also divided into two levels, the small-diameter section of the inner diameter is an equal-diameter through hole matched with the small-diameter section of the outer diameter of the outer guiding sleeve, and the large-diameter section of the inner diameter is a countersunk stage matched with the large-diameter section of the outer guiding sleeve.

15. The drill rod mounting system of claim 14, wherein: The clamp holder mounting part comprises a rear clamp holder mounting part, which comprises symmetrically arranged front and rear side plates, the middle part of each of the front and rear side plates is provided with a U-shaped hole, and the top part of each of the front and rear side plates is completely open; the outer end face of each of the front and rear side plates is connected with a rear oil cylinder mounting plate.

16. The drill rod mounting system of claim 15, wherein: A half-ring guide sleeve is connected to each of the U-shaped holes, the outer diameter of the half-ring guide sleeve is divided into two levels, the small-diameter section of the half-ring guide sleeve is matched with the U-shaped hole, and the large-diameter section of the half-ring guide sleeve is used for fixing the half-ring guide sleeve on the front or rear side plate.

17. The drill rod mounting system of claim 16, wherein: The piston rod of each of the clamp oil cylinders is detachably connected with an outer slip, the inner side of the outer slip is detachably connected with an inner slip, the inner surface arc section of the outer slip is matched with the outer diameter of the inner slip, the outer slip is provided with a countersunk hole, the piston rod of the clamp oil cylinder is detachably connected in the countersunk hole, the upper end and the lower end of the inner slip are provided with bosses, and the upper end and the lower end of the outer slip are provided with clamping grooves, the bosses are detachably connected in the clamping grooves.

18. The drill rod mounting system of claim 17, wherein: The anti-slip hydraulic system comprises a branch oil path arranged between the reverse oil path connected with the hydraulic motor and the clamp oil path connected with the clamp oil cylinder, a one-way valve is arranged on the branch oil path, and the one-way valve is only used for one-way flow of oil in the reverse oil path into the clamp oil path; the clamp oil path and the loosening oil path are commonly connected with a hydraulic lock.

19. The drill rod mounting system of claim 18, wherein: The opening pressure of the oil inlet valve of the one-way valve is higher than the oil return pressure in the reverse oil path.

20. The drill rod mounting system of claim 19, wherein: A front one-way valve is arranged between the clamp oil path and the reverse oil path of the front clamp oil cylinder, a rear one-way valve is arranged between the clamp oil path and the reverse oil path of the rear clamp oil cylinder, and the front one-way valve and the rear one-way valve are in communication with each other.

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