Integrated linkage multi-way valve of hydraulic drilling rig

Abstract

The invention discloses an integrated linkage multi-way valve of a hydraulic drilling rig, and belongs to the field of drilling machinery. The multi-way valve comprises a front end valve plate, a rotary valve plate, a pressure control valve plate, a propelling valve plate and a hydraulic control valve plate which are sequentially connected in parallel. The front end valve plate is provided with a main oil pump connector P1 and an oil tank connector T1. A three-position six-way first reversing valve is arranged in the rotary valve plate to drive a hydraulic motor; the pressure control valve plate integrates a sequence valve, an overflow valve and a throttle valve and is connected with a P2 port of the auxiliary oil pump; a three-position six-way second reversing valve is arranged in the propelling valve plate to control the feeding oil cylinder; the hydraulic control valve plate integrates a pressure reducing valve, a three-position four-way third reversing valve, a two-position three-way fourth / fifth reversing valve, a two-position four-way / three-way hydraulic control valve, a driving chuck and a clamp holder. Through the integrated design, external pipelines are remarkably simplified, the size is reduced, the weight is reduced, linkage control over the hydraulic motor, the oil cylinder, the chuck and the clamp holder is achieved, operation is easy and convenient, and the device is suitable for crawler-type and split-type full-hydraulic drilling machines.

Description

Technical Field

[0001] The present invention relates to the field of drilling machinery, and particularly to an integrated linkage multi-way valve for a hydraulic drill rig. Background Art

[0002] China is extremely rich in mineral resources. In order to clarify their types and reserves, a fully hydraulic drill rig is mostly used to drill holes underground or on the surface to complete exploration tasks. In addition, water hazard is the main disaster source in underground operations or tunnel construction. Conducting underground drilling and water exploration operations is an effective means to prevent and control water hazards.

[0003] Traditional fully hydraulic drill rigs mostly use standard three-position six-way multi-way directional control valves, supplemented by some external pipelines to achieve interconnection and intercommunication between each directional control valve. And it is also necessary for the operator to operate two directional control handles simultaneously to achieve the sequential actions of the hydraulic motor, feed cylinder, chuck, and gripper, resulting in a large volume and complex operation of the hydraulic control system, which is extremely inconvenient for handling and use in narrow underground roadways. Summary of the Invention

[0004] The purpose of the present invention is to provide an integrated linkage multi-way valve for a hydraulic drill rig, making the multi-way valve simple to operate, small in size, light in weight, and capable of being used in both crawler drill rigs and split fully hydraulic drill rigs.

[0005] To achieve the above purpose, the technical solution adopted by the present invention is: an integrated linkage multi-way valve for a hydraulic drill rig, including a valve body composed of a front valve plate, a rotary valve plate, a pressure control valve plate, a propulsion valve plate, and a hydraulic control valve plate connected in parallel in sequence; the front valve plate is provided with a P1 port connected to the main oil pump and a T1 port connected to the oil tank; the rotary valve plate is internally provided with a first directional control valve, and the rotary valve plate is provided with an A1 port and a B1 port for driving the hydraulic motor to rotate; the pressure control valve plate is internally provided with a sequence valve, a relief valve, and a throttle valve, and the pressure control valve plate is provided with a P2 port connected to the auxiliary oil pump; the propulsion valve plate is internally provided with a second directional control valve, and the propulsion valve plate is provided with an A3 port and a B3 port for driving the feed cylinder to move forward and backward; the hydraulic control valve plate is internally provided with a pressure reducing valve, a third directional control valve, a fourth directional control valve, a fifth directional control valve, a first hydraulic control valve, and a second hydraulic control valve, and the hydraulic control valve plate is provided with an A5 port and a B5 port for driving the chuck to clamp and release, an A6 port for driving the gripper to release, and a T2 port connected to the oil tank.

[0006] Further, the first directional control valve is a three-position six-way directional control valve, the second directional control valve is a three-position six-way directional control valve, the third directional control valve is a three-position four-way directional control valve, the fourth directional control valve is a two-position three-way directional control valve, the fifth directional control valve is a two-position three-way directional control valve, the first hydraulic control valve is a two-position four-way hydraulic control valve, and the second hydraulic control valve is a two-position three-way hydraulic control valve.

[0007] Further, the first reversing valve has an oil return port 1a, an oil inlet port 2a, an oil inlet port 3a, a working oil port 4a, a working oil port 5a, and an intermediate oil outlet port 6a. The port 1a is connected to the port T1, the port P1 is connected to the combined ports 2a and 3a, the port 4a is connected to the port A1, and the port 5a is connected to the port B1. The second reversing valve has an oil return port 1c, an oil inlet port 2c, an oil inlet port 3c, a working oil port 4c, a working oil port 5c, and an intermediate oil outlet port 6c. The port 1c is connected to the port T1, the combined ports 2c and 3c are connected to the port 6a through an intermediate oil passage, the port 4c is connected to the port A3, the port 5c is connected to the port B3, and the port 6c is connected to the port T1.

[0008] Further, the sequence valve has an oil inlet port 1b, an oil outlet port 2b, and a drain port 3b. The port P2 is connected to the port 1b, the port 2b is connected to the intermediate oil passage, and the port 3b is connected to the port T1. An overflow valve and a throttle valve are connected in parallel between the intermediate oil passage and the port T1.

[0009] Further, the pressure reducing valve has an oil inlet port 1d, an oil outlet port 2d, and a drain port 3d. The port P2 is connected to the port 1d, and the port 3d is connected to the port T1. The third reversing valve has a reversing oil port 1e, a reversing oil port 2e, a working oil port 3e, and a working oil port 4e. The port 1e is connected to the port 5c, and the port 2e is connected to the port 4c.

[0010] Further, the fourth reversing valve has a reversing oil port 1f, a reversing oil port 2f, and a working oil port 3f. The port 1f is connected to the port 3e, and the port 2f is connected to the port 2d. The first hydraulic control valve has a hydraulic control port xg, an oil inlet port 1g, an oil return port 2g. The port xg is connected to the port 3f, the port 1g is connected to the port 2a, the port 2g is connected to the port T2, the port 3g is connected to the port A5, and the port 4g is connected to the port B5. The fifth reversing valve has a reversing oil port 1m, a reversing oil port 2m, and a working oil port 3m. The port 1m is connected to the port 4e, and the port m is connected to the port 2d. The second hydraulic control valve has a hydraulic control port xn, an oil inlet port 1n, an oil return port 2n, and a working oil port 3n. The port xn is connected to the port 3m, the port 1n is connected to the port 2a, the port 2n is connected to the port T2, and the port 3n is connected to the port A6.

[0011] The beneficial effects of the integrated linkage multi-way valve of the hydraulic drill of the present invention: Through the integrated design of valve plates and the coordinated control of multiple valve components, the present invention realizes the efficient linkage of the actuators of the hydraulic drill and the optimization of the system performance. The specific beneficial effects are as follows: 1. Compact integrated design, significantly improving spatial adaptability: By integrating the front-end valve plate, rotary valve plate, pressure control valve plate, propulsion valve plate, and hydraulic control valve plate into one, the complex structure of the traditional multi-way valve relying on external pipelines is abandoned, and the oil flow is only realized through the internal oil passage for penetration and distribution.

[0012] Substantial reduction in volume and weight: Compared with traditional combined valve groups, the overall volume is reduced by more than 40%, and the weight is reduced by 30%, significantly improving the handling convenience and installation flexibility in confined spaces such as narrow underground roadways and tunnels.

[0013] Simplification of pipelines and improvement in reliability: Eliminate the leakage risks, pressure drop losses, and pipeline interference problems caused by external pipeline connections. The system has a high degree of integration, fewer maintenance nodes, and an extended service life.

[0014] 2. Integration of linkage control, double improvement in operation efficiency and safety: Through the coordinated cooperation of built-in reversing valves, hydraulic control valves, and pressure control valves in each valve plate, automatic linkage of the rotation of the hydraulic motor, the advancement of the oil cylinder, and the actions of the chuck and gripper is achieved, eliminating the need for operators to synchronously operate multiple handles.

[0015] Single-handle / few-handle operation: Only need to operate the main reversing handles of the rotary valve plate and the advancement valve plate, and through the logical linkage of the hydraulic control valve plates, the clamping / loosening actions of the chuck / gripper can be automatically triggered (for example, when the feed oil cylinder advances, the gripper automatically loosens, and when it retreats, the chuck automatically loosens), reducing the operation complexity and the risk of human error.

[0016] Guarantee for safe clamping of drill pipes: The system design ensures that at least one clamping mechanism (chuck or gripper) remains clamped during the processes of drilling, adding pipes, and pulling pipes, effectively preventing the slipping accidents of drill pipes caused by sudden pressure changes or misoperations, and enhancing the operation safety.

[0017] 3. Precise pressure and flow control, strong system stability and working condition adaptability: Multiple pressure control components are built into the pressure control valve plate and the hydraulic control valve plate to construct a multi-stage pressure regulation system to meet the load requirements of different drilling working conditions.

[0018] Intelligent pressure distribution of the auxiliary oil pump: The sequence valve (31) automatically switches the oil flow path according to the system pressure. When the pressure of the auxiliary oil pump exceeds the preset value, the oil is supplemented to the advancement valve plate through the middle oil passage to increase the movement speed of the feed oil cylinder; the overflow valve (32) and the throttle valve (33) are arranged in parallel to achieve stepless adjustment of the feed speed and maximum pressure overload protection, avoiding damage to components caused by impact loads.

[0019] Constant pressure control of the chuck / gripper: The pressure reducing valve (51) provides a stable low-pressure oil source for the hydraulic control valve plate to ensure that the chuck (5) and the gripper (6) maintain a constant clamping force under different working conditions, avoiding clamping failure caused by system pressure fluctuations, especially suitable for high-pressure scenarios such as hard rock drilling.

[0020] 4. Universal adaptation to multiple models, strong equipment compatibility: The modular valve design supports flexible configuration, taking into account the compact layout requirements of crawler drilling rigs and the distributed control requirements of split drilling rigs.

[0021] Power source compatibility: The front valve plate (0) is connected to the main oil pump (P1 port), and the pressure control valve plate (3) is connected to the auxiliary oil pump (P2 port). The dual-pump independent oil supply architecture can adapt to hydraulic systems of different power levels to meet the power requirements of light exploration drilling rigs and heavy engineering drilling rigs.

[0022] Full coverage of actuators: The first reversing valve (21) drives the hydraulic motor (9), the second reversing valve (41) controls the feed cylinder (7), and the hydraulic control valve plate (4) links the chuck (5) and the clamp (6). A set of valve groups can realize the full process control of drilling operations without the need for additional modification, thereby reducing the equipment development and maintenance costs.

[0023] 5. Energy saving and temperature rise control optimization: Unloading and return design: The oil return path between the rotary valve plate (1) and the thrust valve plate (3) in the middle position (e.g., ports 6a and 6c are directly connected to port T1) ensures low-pressure unloading of the hydraulic oil in the non-working state, thereby reducing no-load loss; the throttle valve (33) accurately adjusts the flow rate, avoids overflow energy waste, reduces system temperature rise, and prolongs the service life of the hydraulic oil.

[0024] In summary, the present invention breaks through the bottleneck of complex operation and bulky size of traditional hydraulic drilling rig multi-way valves through structural integration, control linkage, and functional modular design, and has significant engineering application value in the fields of coal mine water exploration and drainage, mineral exploration, tunnel construction, etc. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 It is a structural schematic diagram of a hydraulic drilling rig; Figure 2 It is the structural appearance diagram of the multi-way valve of the present invention; Figure 3 It is a schematic diagram of the oil circuit structure of the multi-way valve of the present invention; Figure 4 for Figure 3 The left figure of ; Figure 5 for Figure 3 The right figure of ; Figure 6 This is a schematic diagram of the oil circuit structure of a working position in the first reversing valve of the present invention; Figure 7 This is a schematic diagram of the oil circuit structure of the upper position of the first reversing valve of the present invention; Figure 8 This is a schematic diagram of the oil circuit structure of the lower working position of the first reversing valve of the present invention; Figure 9 This is a schematic diagram of the internal oil circuit structure of the pressure control valve plate of the present invention; Figure 10 Schematic diagram of the working position oil circuit structure in the second reversing valve of the present invention; Figure 11 Schematic diagram of the upper working position oil circuit structure in the second reversing valve of the present invention; Figure 12 Schematic diagram of the lower working position oil circuit structure in the second reversing valve of the present invention; Figure 13 Schematic diagram of the internal oil circuit structure of the upper working position hydraulic control valve plate in the third reversing valve of the present invention; Figure 14 Schematic diagram of the internal oil circuit structure of the lower working position hydraulic control valve plate in the third reversing valve of the present invention; Figure 15 Schematic diagram of the internal oil circuit structure of the lower working position hydraulic control valve plates in both the fourth reversing valve and the fifth reversing valve of the present invention; Explanation of reference numerals: 0. Front valve plate, 1. Rotary valve plate, 2. Pressure control valve plate, 3. Thrust valve plate, 4. Hydraulic control valve plate, 5. Chuck, 6. Holder, 7. Feed oil cylinder, 8. Drill pipe, 9. Hydraulic motor, 10. Intermediate oil passage, 11. First reversing valve, 21. Sequence valve, 22. Relief valve, 23. Throttle valve, 31. Second reversing valve, 41. Pressure reducing valve, 42. Third reversing valve, 43. Fourth reversing valve, 44. First hydraulic control valve, 45. Fifth reversing valve, 46. Second hydraulic control valve. Detailed implementation manners

[0026] The embodiments of the technical solution of the present invention will be described in detail below with reference to the drawings. The following embodiments are only used to illustrate the technical solution of the present invention more clearly, and therefore are only examples and cannot be used to limit the protection scope of the present invention.

[0027] In the description of the present application, it should be understood that the orientation or positional relationships indicated by the terms "middle", "upper", "lower", "clockwise", "counterclockwise", etc. are based on the orientation or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present invention.

[0028] Refer to Figures 1 to 5 , a hydraulic drill integrated linkage multi-way valve, including a front valve plate 0, a rotary valve plate 1, a pressure control valve plate 2, a thrust valve plate 3, and a hydraulic control valve plate 4 that are connected in parallel in sequence, and each valve plate forms a valve body. The specific structures and connection relationships of each valve plate are as follows: Front valve plate 0: An oil port P1 connected to the main oil pump and an oil port T1 connected to the oil tank are provided, serving as the oil inlet and oil return interfaces of the main oil circuit.

[0029] Rotary valve plate 1: The first reversing valve 11 is integrated inside. Oil ports A1 and B1 for driving the hydraulic motor 9 are arranged outside the valve body. The oil return port 1a of the first reversing valve 11 is connected to the T1 port of the front valve plate 0. The oil inlet ports 2a and 3a are merged and then connected to the P1 port of the front valve plate 0. The working oil ports 4a and 5a are respectively connected to the A1 port and the B1 port. The middle oil outlet port 6a is connected to the second reversing valve 31 of the advancing valve plate 3 through an internal oil passage.

[0030] Pressure control valve plate 2: The sequence valve 21, the overflow valve 22 and the throttle valve 23 are integrated inside. The oil port P2 for connecting the auxiliary oil pump is arranged outside the valve body. The oil inlet port 1b of the sequence valve 21 is connected to the P2 port. The oil outlet port 2b is communicated with the advancing valve plate 3 through the middle oil passage 10. The oil drain port 3b is connected to the T1 port. The overflow valve 22 and the throttle valve 23 are arranged in parallel between the middle oil passage 10 and the T1 port to control the pressure and flow rate of the auxiliary oil pump.

[0031] Advancing valve plate 3: The second reversing valve 31 is integrated inside. Oil ports A3 and B3 for driving the feed cylinder 7 are arranged outside the valve body. The oil return port 1c of the second reversing valve 31 is connected to the T1 port. The oil inlet ports 2c and 3c are merged and then communicated with the middle oil outlet port 6a of the rotary valve plate 1 through the middle oil passage 10. The working oil ports 4c and 5c are respectively connected to the A3 port and the B3 port. The middle oil outlet port 6c is connected to the T1 port.

[0032] Hydraulic control valve plate 4: The pressure reducing valve 41, the third reversing valve 42, the fourth reversing valve 43, the first hydraulic control valve 44, the fifth reversing valve 45 and the second hydraulic control valve 46 are integrated inside. Oil ports A5 and B5 for driving the chuck 5, the oil port A6 for driving the gripper 6, and the oil tank connection port T2 are arranged outside the valve body.

[0033] The oil inlet port 1d of the pressure reducing valve 41 is connected to the P2 port of the auxiliary oil pump. The oil outlet port 2d provides pressure-reduced oil for the chuck and the gripper. The oil drain port 3d is connected to the T1 port. The reversing oil ports 1e and 2e of the third reversing valve 42 are respectively connected to the 5c port and the 4c port of the advancing valve plate 3. The working oil ports 3e and 4e are respectively connected to the fourth reversing valve 43 and the fifth reversing valve 45. The working oil port 3f of the fourth reversing valve 43 is connected to the hydraulic control port xg of the first hydraulic control valve 44. The working oil port 3m of the fifth reversing valve 45 is connected to the hydraulic control port xn of the second hydraulic control valve 46. The oil inlet port 1g of the first hydraulic control valve 44 is connected to the 2d port. The oil return port 2g is connected to the T2. The working oil ports 3g and 4g are respectively connected to the A5 port and the B5 port. The oil inlet port 1n of the second hydraulic control valve 46 is connected to the 2d port. The oil return port 2n is connected to the T2. The working oil port 3n is connected to the A6 port.

[0034] The working principle of the present invention is as follows:

[0035] When it is necessary to drive the hydraulic motor 9 to rotate, operate the first reversing valve 11 of the rotary valve plate 1: Stop rotation: Refer to Figure 6 , the first reversing valve 11 is in the middle position, and the hydraulic motor 9 stops rotating. The pressure oil from the main oil pump flows in from port P1 through the combined ports 2a and 3a, and part of the oil enters the intermediate oil passage 10 through port 6a.

[0036] Clockwise rotation: Refer to Figure 7 , the first reversing valve 11 is switched to the upper position. The pressure oil from the main oil pump enters the valve from port P1 through port 2a, flows to port A1 through port 4a, drives the hydraulic motor 9 to rotate clockwise, and the return oil returns to the fuel tank from port B1 through port 5a, port 1a and port T1.

[0037] Counterclockwise rotation: Refer to Figure 8 , the first reversing valve 11 is switched to the lower position. The pressure oil from the main oil pump flows from port P1 through port 2a and port 5a to port B1, drives the hydraulic motor 9 to rotate counterclockwise, and the return oil returns to the fuel tank from port A1 through port 4a, port 1a and port T1.

[0038] Refer to Figure 9 , under the action of the sequence valve 21 on the pressure control valve plate 2, the oil fluid input from port P2 first enters the pilot valve plate 4 to provide a pressure oil source.

[0039] When the pressure input from port P2 exceeds the preset pressure of port 1b of the sequence valve 21, a part of the oil fluid will be diverted to port 2b of the sequence valve 21 to the intermediate oil passage 10, adding a pressure oil source to the second reversing valve 31 and increasing the reciprocating movement speed of the feed cylinder 7.

[0040] Adjust the throttle valve 23 to achieve the fast and slow movement of the feed cylinder 7, and the relief valve 22 can limit the maximum working pressure of the feed cylinder 7.

[0041] The second reversing valve 31 of the push valve plate 3 controls the forward / backward movement of the feed cylinder 7: Stop: Refer to Figure 10 , the second reversing valve 31 is in the middle position, the feed cylinder 7 is in a floating state, and the pressure oil in the intermediate oil passage 10 returns to the fuel tank through ports 3c, 6c and T1 for unloading; Forward: Refer to Figure 11 , the second reversing valve 31 is switched to the upper position. The pressure oil in the intermediate oil passage 10 flows from ports 2c and 4c to port A3, pushing the piston rod of the feed cylinder 7 to extend; the oil fluid is also input to port 2e of the third reversing valve 42 as pressure oil; the return oil returns to the fuel tank from port B3 through ports 5c, 1c and T1.

[0042] Backward: Refer to Figure 12, the second reversing valve 31 switches to the lower working position. The pressure oil in the intermediate oil passage 10 flows from port 2c and port 5c to port B3, the piston rod retracts, and the oil is simultaneously input to port 1e of the third reversing valve 42 as pressure oil; the return oil returns to the fuel tank from port A3 through port 4c, port 1c, and port T1.

[0043] See Figure 5 , when the third reversing valve 42 is in the middle working position, the four oil ports 1e, 2e, 3e, and 4e are not interconnected, and both the first hydraulic control valve 44 and the second hydraulic control valve 46 are in the right working position. The pressure oil at port 2d of the pressure reducing valve 41 will be simultaneously delivered to port 1n of the second hydraulic control valve 46, the gripper 6 has no action, and from ports 1g and 3g of the first hydraulic control valve 44 to port A5, causing the chuck 5 to clamp.

[0044] See Figure 13 , when the third reversing valve 42 is in the upper working position, the hydraulic control pressure oil output from the second reversing valve 31 passes through ports 1e, 4e, 1f, and 3f to xg, causing the spring inside the first hydraulic control valve 44 to be compressed and change to the left working position. The pressure oil from port 2d passes through ports 1g and 4g to port B5, and the chuck 5 will be opened; the hydraulic control pressure oil output from the second reversing valve 31 passes through ports 2e, 3e, 1m, and 3m to xn, causing the spring inside the second hydraulic control valve 46 to be compressed and change to the left working position. The pressure oil from port 2d passes through ports 1n and 3n to port A6, and the gripper 6 will be opened.

[0045] See Figure 14 , when the third reversing valve 42 is in the lower working position, the hydraulic control pressure oil output from the second reversing valve 31 passes through ports 1e, 3e, 1m, and 3m to xn, causing the spring inside the second hydraulic control valve 46 to be compressed and change to the left working position. The pressure oil from port 2d passes through ports 1n and 3n to port A6, and the gripper 6 will be opened. The hydraulic control pressure oil output from the second reversing valve 31 passes through ports 2e, 4e, 1f, and 3f to xg, causing the spring inside the first hydraulic control valve 44 to be compressed and change to the left working position. The pressure oil from port 2d passes through ports 1g and 4g to port B5, and the chuck 5 will be opened.

[0046] See Figure 15 , when operating the fourth reversing valve 43 to the lower working position, the pressure oil at port 2d of the pressure reducing valve 41 passes through ports 2f and 3f to xg, causing the spring inside the first hydraulic control valve 44 to be compressed and change to the left working position. The pressure oil at port 2d of the pressure reducing valve 41 passes through ports 1g and 4g to port B5, causing the chuck 5 to be opened.

[0047] See Figure 15 , when operating the fifth reversing valve 45 to the lower working position, the pressure oil at port 2d of the pressure reducing valve 41 passes through ports 2m and 3m to xn, causing the spring inside the second hydraulic control valve 46 to be compressed and change to the left working position. The pressure oil at port 2d of the pressure reducing valve 41 passes through ports 1n and 3n to port A6, causing the gripper 6 to be opened.

[0048] The working process of the present invention will be further described below in conjunction with the drawings and embodiments;

[0049] See Figure 3 , the pressure oil input from the main oil pump of the P1 port flows back to the fuel tank through the 3a and 6a ports of the first reversing valve 11, the intermediate oil passage 10, the 3c and 6c ports of the second reversing valve 31, and the T1 port.

[0050] The pressure oil input from the auxiliary oil pump of the P2 port is divided into two paths. One path is connected to the sequence valve 21. After the oil pressure reaches the preset pressure, the oil fluid converges into the intermediate oil passage 10 from the 2b port and flows back to the fuel tank through the 3c and 6c ports of the second reversing valve 31 and the T1 port. The other path is connected to the pressure reducing valve 41 inside the hydraulic control valve plate 4. After decompression, it supplies pressure oil to the fourth reversing valve 43, the first hydraulic control valve 44, the fifth reversing valve 45, and the second hydraulic control valve 46 at the same time. The oil fluid at the 1g port of the first hydraulic control valve 44 flows to the A5 port through 3g, causing the chuck 5 to automatically clamp and maintaining this clamping oil pressure. Method 1:

[0051] See Figure 15 , operate the fourth reversing valve 43 to switch to the lower working position, so that the chuck 5 is opened. Then operate the fifth reversing valve 45 to the lower working position, so that the gripper 6 is opened. Load the drill pipe 8 into the chuck 5 and the gripper 6. Then reset the operating handles of the fourth reversing valve 43 and the fifth reversing valve 45. The chuck 5 and the gripper 6 clamp the drill pipe 8 at the same time, and the first drill pipe is loaded. Method 2:

[0052] (1) Place the third reversing valve 42 in the lower working position; (2) See Figure 12 , operate the second reversing valve 31 to the lower working position. The pressure oil flows to the B3 port through the 2c and 5c ports, driving the piston rod of the feed cylinder 7 to retract. At this time, the oil fluid at the B3 port is synchronously input into the 2e port of the third reversing valve 42 and flows to the hydraulic control port xg through the 4e, 1f, and 3f ports, pushing the first hydraulic control valve 44 to switch to the left working position, so that the pressure oil output by the pressure reducing valve 41 flows from the 1g port through the 4g port to the B5 port, realizing the loosening of the chuck 5.

[0053] (3) See Figure 10 , operate the second reversing valve 31 to the middle working position. At this time, the B3 port, 5c, 1c, and T1 port are connected to the fuel tank and there is no pressure. The first hydraulic control valve 44 returns to the normal working position under the action of the built-in spring, and the chuck 5 clamps the drill pipe 8.

[0054] (4) See Figure 11, Operate the second reversing valve 31 to the upper working position. The hydraulic oil flows through 2c, 4c, and port A3 to the feed cylinder 7, and the piston rod extends. The hydraulic oil at port A3 enters port 1e of the third reversing valve 42, and then through 3e, 1m, 3m to xn, causing the spring inside the second hydraulic control valve 46 to be compressed and changing it to the left working position. The pressure oil at 1n will be delivered to 3n to port A6, opening the gripper 6. The extension of the feed cylinder 7 drives the chuck 5 and the clamped drill pipe 8 towards the opened gripper 6.

[0055] (5) When the drill pipe 8 passes through the gripper 6, operate the second reversing valve 31 to the middle working position. At this time, port A3 communicates with port T1 and there is no pressure oil. The second hydraulic control valve 46 returns to its normal working position under the action of the built-in spring, and the gripper 6 clamps the drill pipe 8, completing the loading of the first drill pipe.

[0056] (1) Rotate the throttle valve 23 counterclockwise to drain all the hydraulic oil flowing to the second reversing valve 31 back to the oil tank.

[0057] (2) Operate the fifth reversing valve 45 to the lower working position. The spring inside the second hydraulic control valve 46 is compressed and it changes to the left working position. The pressure oil at 1n flows through 3n to A6, opening the gripper 6.

[0058] (3) Operate the first reversing valve 11 to the upper working position. The hydraulic oil at port P1 flows through 2a, 4a to A1, causing the hydraulic motor 9 to rotate clockwise, and the chuck 5 clamps the drill pipe 8 and rotates clockwise.

[0059] (4) Operate the second reversing valve 31 to the upper working position, and then rotate the throttle valve 23 clockwise to allow the hydraulic oil to flow through 2c, 4c, and port A3 to the feed cylinder 7. The piston rod extends. While the chuck 5 clamps the drill pipe 8 and rotates clockwise, it is pressed into the rock. Continue to rotate the throttle valve 23 clockwise to allow more hydraulic oil to flow through 2c, 4c, and port A3 to the feed cylinder 7, enabling the drill pipe 8 to be pressed into the rock with greater force.

[0060] (5) After completing the drilling for one cylinder stroke, rotate the throttle valve 23 counterclockwise to drain all the hydraulic oil flowing to the second reversing valve 31 back to the oil tank.

[0061] Operate the second reversing valve 31 to the middle working position, and the feed cylinder 7 stops moving. Operate the first reversing valve 11 to the middle working position, and the hydraulic motor 9 stops rotating.

[0062] Operate the fifth reversing valve 45 to the upper working position, and the gripper 6 clamps the drill pipe 9.

[0063] (1) Operate the third reversing valve 42 to the lower working position, and the working condition of the linkage system changes to the drill feed (lowering the drill) state.

[0064] (2) Tighten the throttle valve 23 clockwise to allow the oil to flow to the second reversing valve 31; operate the second reversing valve 31 to the lower working position, the piston rod of the feed cylinder 7 retracts, and at the same time the chuck 5 releases the drill pipe 8.

[0065] (3) When the chuck 5 reaches the end point, pass the new drill pipe through the chuck and press it against the existing drill pipe; operate the second reversing valve 31 to the lower working position, and then to the middle working position. There is no oil in ports A3 and B3, and the chuck 5 automatically clamps the drill pipe 8; operate the first reversing valve 11 to the upper working position, and the hydraulic motor 9 drives the chuck 5 that clamps the drill pipe 8 to rotate clockwise to tighten the thread of the original drill pipe; operate the first reversing valve 11 to the middle working position, and the hydraulic motor 9, chuck 5, and drill pipe 8 stop rotating.

[0066] (4) Operate the second reversing valve 31 to the upper working position, the piston rod of the feed cylinder 7 extends, and at the same time the gripper 6 is opened, and the originally clamped drill pipe 8 will be fed into the drill hole.

[0067] (5) After the chuck reaches the end point, repeat the actions in (2), (3), and (4) above to load multiple drill pipes into the drill hole.

[0068] (1) Operate the third reversing valve 42 to the upper working position, and the working condition of the linkage system changes to the drill lifting (drill raising) state.

[0069] (2) Operate the second reversing valve 31 to the upper working position, and the pressure oil flows through ports 2c and 4c to port A3. The piston rod of the feed cylinder 7 extends. At the same time, the oil in port A3 passes through ports 2e, 23, 1f, and 3f of the third reversing valve 42 to xg, causing the spring in the first hydraulic control valve 44 to be compressed and changing to the left working position. The pressure oil at 1g is transported to ports 4g and B5, causing the chuck 5 to be opened, the chuck 5 releases the drill pipe 8, and it moves to near the gripper 6.

[0070] (3) After completing one cylinder stroke, operate the second reversing valve 31 to the middle working position. There is no oil in ports A3 and B3, and the chuck 5 will automatically clamp the drill pipe 8.

[0071] (4) Operate the second reversing valve 31 to the b1 lower working position. The oil passes through ports 2c, 5c, and B3 to the feed cylinder 7, and the piston rod retracts. The oil is also input to port 2e of the third reversing valve 42, and passes through ports 4e, 1m, and 3m to xn, causing the spring in the second hydraulic control valve 46 to be compressed and changing to the left working position. The pressure oil at 1n will be transported to port 3n to A6, causing the gripper 6 to be opened, and the feed cylinder 7 drives the chuck 5 that clamps the drill pipe 8 to move backward to pull out the drill pipe.

[0072] (5) After completing one cylinder stroke, operate the second reversing valve 31 to the middle working position. There is no oil in ports A3 and B3, and the chuck 5 and gripper 6 will automatically clamp the drill pipe 8.

[0073] (6) Operate the first reversing valve 11 to the lower working position. The oil fluid at port P1 flows through 2a to 5a and B1, causing the hydraulic motor 9 to drive the chuck 5 that clamps the drill pipe 8 to rotate counterclockwise, disengaging the thread from the original drill pipe. Operate the first reversing valve 11 to the middle working position, and the hydraulic motor 9, the chuck 5, and the drill pipe 8 stop rotating.

[0074] (7) The chuck 5 operated according to step (2) will clamp another drill pipe, and at this time, the uncoupled drill pipe is removed. Repeat the actions of steps (3), (4), (5), and (6) to pull out the drill pipes one by one from the borehole.

[0075] From the entire drilling operation process, it can be seen that by repeatedly operating the two control levers of the first reversing valve 11 and the second reversing valve 31, and only operating the handle of the third reversing valve 42 when switching between the drilling or pulling-out mode, the drilling operation can be completed. The operation is simple and convenient. Throughout the process, there is always at least the gripper 6 or the chuck 5 clamping the drill pipe 8, which can effectively prevent accidental slipping accidents of the drill pipe.

[0076] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit them; although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that it is still possible to modify the specific implementation manners of the present invention or perform equivalent replacements for some technical features; without departing from the spirit of the technical solutions of the present invention, they should all be covered within the scope of the technical solutions claimed by the present invention.

Claims

1. An integrated linkage multi-way valve for a hydraulic drill, characterized in that: It includes a valve body composed of a front valve plate (0), a rotary valve plate (1), a pressure control valve plate (2), a propulsion valve plate (3) and a hydraulic control valve plate (4) connected in parallel in sequence; a P1 port connecting to the main oil pump and a T1 port connecting to the oil tank are arranged on the front valve plate (0); a first reversing valve (11) is arranged inside the rotary valve plate (1), and an A1 port and a B1 port for driving the hydraulic motor to rotate are arranged on the rotary valve plate (1); a sequence valve (21), a relief valve (22) and a throttle valve (23) are arranged inside the pressure control valve plate (2), and a P2 port connecting to the auxiliary oil pump is arranged on the pressure control valve plate (2); a second reversing valve (31) is arranged inside the propulsion valve plate (3), and an A3 port and a B3 port for driving the feed cylinder to move forward and backward are arranged on the propulsion valve plate (3); a pressure reducing valve (41), a third reversing valve (42), a fourth reversing valve (43), a fifth reversing valve (45), a first hydraulic control valve (44) and a second hydraulic control valve (46) are arranged inside the hydraulic control valve plate (4), and an A5 port and a B5 port for driving the chuck (5) to clamp and loosen, an A6 port for driving the gripper to loosen, and a T2 port connecting to the oil tank are arranged on the hydraulic control valve plate (4); each valve plate is connected through an internal oil passage without external pipeline connection.

2. The integrated linkage multi-way valve of the hydraulic drill according to claim 1, characterized in that: The first and second reversing valves (11, 31) are both three-position six-way reversing valves, the third reversing valve (42) is a three-position four-way reversing valve, the fourth and fifth reversing valves (43, 45) are both two-position three-way reversing valves, the first hydraulic control valve (44) is a two-position four-way hydraulic control valve, and the second hydraulic control valve (46) is a two-position three-way hydraulic control valve.

3. The integrated linkage multi-way valve of the hydraulic drill according to any one of claims 1 to 2, characterized in that: The first reversing valve (11) is provided with an oil return port 1a, an oil inlet port 2a, 3a (merged and connected to the P1 port), a working oil port 4a (connected to the A1 port), 5a (connected to the B1 port) and an intermediate oil outlet port 6a, wherein the 1a port is connected to the T1 port; the second reversing valve (31) is provided with an oil return port 1c, an oil inlet port 2c, an oil inlet port 3c, a working oil port 4c, a working oil port 5c, and an intermediate oil outlet port 6c. The 1c port is connected to the T1 port, the merged 2c port and 3c port are connected to the 6a port through an intermediate oil passage, the 4c port is connected to the A3 port, the 5c port is connected to the B3 port, and the 6c port is connected to the T1 port.

4. The integrated linkage multi-way valve of the hydraulic drill according to any one of claims 1 to 2, characterized in that: The sequence valve (21) is provided with an oil inlet port 1b, an oil outlet port 2b, and a drain port 3b. The P2 port is connected to the 1b port, the 2b port is connected to the intermediate oil passage, and the 3b port is connected to the T1 port; a relief valve (22) and a throttle valve (23) are connected in parallel between the intermediate oil passage and the T1 port.

5. The integrated linkage multi-way valve of a hydraulic drill according to any one of claims 1 to 2, characterized in that: The pressure reducing valve (41) is provided with an oil inlet port 1d, an oil outlet port 2d, and a drain port 3d. The P2 port is connected to the 1d port, and the 3d port is connected to the T1 port; the third reversing valve (42) is provided with a reversing oil port 1e, a reversing oil port 2e, a working oil port 3e, and a working oil port 4e. The 1e port is connected to the 5c port, and the 2e port is connected to the 4c port.

6. The integrated linkage multi-way valve of the hydraulic drill according to claim 5, characterized in that: The fourth reversing valve (43) is provided with a reversing oil port 1f, a reversing oil port 2f, and a working oil port 3f. The 1f port is connected to the 3e port, and the 2f port is connected to the 2d port. The first hydraulic control valve (44) is provided with a hydraulic control port xg, an oil inlet port 1g, an oil return port 2g, a working oil port 3g, and a working oil port 4g. The xg port is connected to the 3f port, the 1g port is connected to the 2d port, the 2g port is connected to T2, the 3g port is connected to the A5 port, and the 4g port is connected to the B5 port. The fifth reversing valve (45) is provided with a reversing oil port 1m, a reversing oil port 2m, and a working oil port 3m. The 1m port is connected to the 3e port, and the 2m port is connected to the 2d port. The second hydraulic control valve (46) is provided with a hydraulic control port xn, an oil inlet port 1n, an oil return port 2n, and a working oil port 3n. The xn port is connected to the 3m port, the 1n port is connected to the 2d port, the 2n port is connected to T2, and the 3n port is connected to the A6 port.

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