A pressurized rotary hydraulic control system with multiple operating modes

Abstract

The application provides a pressurized rotary hydraulic control system with multiple working modes, comprising a load-sensitive pump, a pilot oil pump, a multi-way valve assembly, a hydraulic cylinder, a hydraulic motor, a proportional pressure reducing valve, an electromagnetic reversing valve, a hydraulic control reversing valve and a manual overflow valve, etc. The application has three working modes of pressurized feeding, single-pump driving rotary rock breaking and double-pump driving rotary rock breaking; wherein the pressurized feeding working mode is the extension and retraction work of the hydraulic cylinder driven by the hydraulic pump, having the advantages of fast feeding and pressurized propulsion of the drilling tool for active rock breaking; the single-pump driving rotary rock breaking working mode is the forward and reverse rotation work of the double motor driven by the single hydraulic pump, having the advantages of stepless speed regulation and multiple torque output; the double-pump driving rotary rock breaking working mode is the forward and reverse rotation work of the double motor driven by the double hydraulic pump, having the advantages of high power output and fast cutting of the rock layer. The application can meet the needs of high and low speed rotary rock breaking of the drilling tool, pressurized drilling in super deep ground and load-sensitive regulation and control in the well forming process.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of hydraulic transmission and control, and particularly relates to a pressurized rotary hydraulic control system with multiple working modes. BACKGROUND

[0002] The existing well completion drilling equipment in China has the problems of limited drilling depth, inaccurate drilling precision, poor reliability and adaptability in complex geological environments such as mountainous areas, remote disaster areas and mining areas. On the other hand, under the premise that the land surface resources in the territory of each country are decreasing, in order to meet the needs of the rapid development of industry, deep land and deep sea resources are considered the most important alternative resources in the 21st century, but most of the high-performance drilling rigs needed for the exploitation of deep land and deep sea resources in China depend on imports.

[0003] At present, the commonly used well completion drilling equipment is a hydraulic drilling rig. In order to improve the drilling capacity of the hydraulic drilling rig, the hydraulic transmission and control system, which is the'skeleton and muscle' of the drilling rig, still needs to be broken through. Based on this, domestic and foreign technical personnel have carried out a lot of optimization and innovation. In the drilling rig hydraulic transmission and control systems disclosed in patents CN202221530671.5, CN202220177506.X, CN202111459216.0, CN202110294858.3, CN200710018441.4, although the load-sensitive control technology is used to improve the energy utilization rate of the drilling rig hydraulic system, the single-pump-driven motor rotary structure and the hydraulic motor cooperating with the pulley block to pull out the drilling tool have relatively weak rock breaking capacity, drilling speed and drilling depth, which cannot meet the needs of emergency rescue and ultra-deep well drilling, thereby restricting the rapid response capability of China's deep land and deep sea resource drilling and exploitation and emergency drilling rescue. Therefore, it is necessary to invent a new type of deep well drilling rig hydraulic control system to improve the drilling speed and drilling capacity of the drilling rig and help China's emergency rescue guarantee and deep land resource exploitation. SUMMARY

[0004] In view of the deficiencies in the prior art, the present application provides a pressurized rotary hydraulic control system with multiple working modes, which can meet the multifunctional requirements of high and low speed rotation of the drilling tool for breaking rock, pressurized drilling in ultra-deep wells, load-sensitive regulation and control and remote proportional regulation during drilling, and effectively improve the ability of the drilling rig in ultra-deep well drilling and hard rock drilling.

[0005] The present application achieves the above technical purposes through the following technical means:

[0006] A pressurized rotary hydraulic control system with multiple working modes comprises an oil tank, the oil tank is connected with a load-sensitive pump A through an oil suction filter A, the oil tank is connected with a load-sensitive pump B through an oil suction filter B, and the oil tank is connected with a pilot oil pump through an oil suction filter C;

[0007] The outlet of the load sensitive pump A is connected with the inlet of the manual overflow valve A, the inlet of the hydraulic control overflow valve A, the throttle valve A, the P port of the multi-way valve assembly A and the P port of the multi-way valve assembly B respectively; the load sensitive pump B is connected with the inlet of the manual overflow valve B, the inlet of the hydraulic control overflow valve B, the throttle valve C and the P port of the multi-way valve assembly C respectively; the pilot oil pump is connected with the one-way valve, and the proportional overflow valve is installed on the branch oil line between the pilot oil pump and the one-way valve;

[0008] The A port of the multi-way valve assembly A is connected with the inlet of the balance valve, the B port of the multi-way valve assembly A is connected with the upper oil port of the hydraulic cylinder, the outlet of the balance valve is connected with the lower oil port of the hydraulic cylinder, the pilot oil discharge port of the multi-way valve assembly A is connected with the P port of the hydraulic control reversing valve A, the load feedback outlet of the multi-way valve assembly A is connected with the throttle valve B, and the T port of the multi-way valve assembly A is connected with the oil tank;

[0009] The A port of the multi-way valve assembly B is connected with the P port of the electromagnetic reversing valve and the lower oil port of the hydraulic motor A, the B port of the multi-way valve assembly B is connected with the lower oil port of the hydraulic motor B and the electromagnetic reversing valve, the pilot oil discharge port of the multi-way valve assembly B is connected with the P port of the hydraulic control reversing valve A, the load feedback outlet of the multi-way valve assembly B is connected with the load feedback inlet of the multi-way valve assembly A, and the T port of the multi-way valve assembly B is connected with the oil tank;

[0010] The A port of the multi-way valve assembly C is connected with the P port of the electromagnetic reversing valve and the lower oil port of the hydraulic motor A, the B port of the multi-way valve assembly C is connected with the lower oil port of the hydraulic motor B and the T port of the electromagnetic reversing valve, the pilot oil discharge port of the multi-way valve assembly C is connected with the hydraulic control reversing valve B, the load feedback outlet of the multi-way valve assembly C is connected with the throttle valve D, and the T port of the multi-way valve assembly C is connected with the oil tank.

[0011] Further, three working modes are provided: the pressurized feeding working mode, the single-pump driving rotary rock breaking working mode and the double-pump driving rotary rock breaking working mode.

[0012] Further, in the pressurized feeding working mode, the inlet of the load sensing pump A is connected with the oil tank through the oil suction filter A; the outlet of the load sensing pump A is connected with the inlet of the manual overflow valve A, the inlet of the hydraulic control overflow valve A, the lower control port of the hydraulic control overflow valve A, the inlet of the throttle valve A and the P port of the multi-way valve assembly A respectively; the A port of the multi-way valve assembly A is communicated with the inlet of the balance valve; the outlet of the balance valve is connected with the upper oil port of the hydraulic cylinder; the lower oil port of the hydraulic cylinder is connected with the B port of the multi-way valve assembly A; the pilot oil discharge port of the multi-way valve assembly A is connected with the P port of the hydraulic control reversing valve A; the load feedback outlet of the multi-way valve assembly A is connected with the inlet of the throttle valve B; the control port a and the control port b of the hydraulic control reversing valve A are connected with the outlet of the throttle valve A and the outlet of the throttle valve B respectively; the outlet of the manual overflow valve A, the outlet of the hydraulic control overflow valve A, the T port of the hydraulic control reversing valve A and the T port of the multi-way valve assembly A are all communicated with the oil tank.

[0013] Further, in the single pump driving rotary rock breaking working mode, the inlet of the load sensing pump B is connected with the oil tank through the oil suction filter B; the outlet of the load sensing pump B is connected with the inlet of the manual overflow valve B, the inlet of the hydraulic control overflow valve B, the lower control port of the hydraulic control overflow valve B, the inlet of the throttle valve C and the P port of the multi-way valve assembly C respectively; the A port of the multi-way valve assembly C is connected with the P port of the electromagnetic reversing valve and the lower oil port of the hydraulic motor A; the upper oil port of the hydraulic motor A is communicated with the A port of the electromagnetic reversing valve; the B port of the electromagnetic reversing valve is connected with the upper oil port of the hydraulic motor B (32); the lower oil port of the hydraulic motor B (32) is connected with the T port of the electromagnetic reversing valve and further connected with the B port of the multi-way valve assembly C; the pilot oil discharge port of the multi-way valve assembly C is connected with the P port of the hydraulic control reversing valve B; the load feedback outlet of the multi-way valve assembly C is connected with the inlet of the throttle valve D; the control port a and the control port b of the hydraulic control reversing valve B are connected with the outlet of the throttle valve C and the outlet of the throttle valve D respectively; the outlet of the manual overflow valve B, the outlet of the hydraulic control overflow valve B, the T port of the hydraulic control reversing valve B and the T port of the multi-way valve assembly C are all communicated with the oil tank.

[0014] Further, in the double pump driving rotary rock breaking mode, the inlet of the load sensitive pump A is connected with the oil tank through the oil suction filter A; the outlet of the load sensitive pump A is connected with the inlet of the manual overflow valve A, the inlet of the hydraulic control overflow valve A, the lower control port of the hydraulic control overflow valve A, the inlet of the throttle valve A, the P port of the multi-way valve assembly A, and the P port of the multi-way valve assembly B respectively; the A port of the multi-way valve assembly A is communicated with the inlet of the balance valve; the outlet of the balance valve is connected with the upper oil port of the hydraulic cylinder; the lower oil port of the hydraulic cylinder is connected with the B port of the multi-way valve assembly A; the A port of the multi-way valve assembly B is connected with the P port of the electromagnetic reversing valve and the lower oil port of the hydraulic motor A; the upper oil port of the hydraulic motor A is communicated with the A port of the electromagnetic reversing valve; the B port of the electromagnetic reversing valve is connected with the upper oil port of the hydraulic motor B (32); the lower oil port of the hydraulic motor B (32) is connected with the T port of the electromagnetic reversing valve, and is further communicated with the B port of the multi-way valve assembly B; the pilot oil discharge port of the multi-way valve assembly B and the pilot oil discharge port of the multi-way valve assembly A are connected with the P port of the hydraulic control reversing valve A; the load feedback outlet of the multi-way valve assembly B is communicated with the load feedback inlet of the multi-way valve assembly A, and is further connected with the inlet of the throttle valve B; the control ports a and b of the hydraulic control reversing valve A are connected with the outlet of the throttle valve A and the outlet of the throttle valve B respectively; the outlet of the manual overflow valve A, the outlet of the hydraulic control overflow valve A, the T port of the hydraulic control reversing valve A, the T port of the multi-way valve assembly A, and the T port of the multi-way valve assembly B are communicated with the oil tank.

[0015] Further, the pilot oil discharge port of the multi-way valve assembly B is connected with the P port of the hydraulic control reversing valve A through the pilot oil discharge port in the multi-way valve assembly A; and the load feedback outlet of the multi-way valve assembly B is connected with the inlet of the throttle valve B through the shuttle valve in the multi-way valve assembly A.

[0016] Further, the outlet of the one-way valve is connected with the inlet of the proportional pressure reducing valve A, the proportional pressure reducing valve B and the proportional pressure reducing valve C respectively; the outlet of the proportional pressure reducing valve A is connected with the pilot oil supply port of the multi-way valve assembly A; the outlet of the proportional pressure reducing valve B is connected with the pilot oil supply port of the multi-way valve assembly B; and the outlet of the proportional pressure reducing valve C is connected with the pilot oil supply port of the multi-way valve assembly C.

[0017] Further, the load sensitive pump A, the load sensitive pump B and the pilot oil pump are connected with the motor through the shaft couplings.

[0018] By means of the above technical scheme, the application has the following beneficial effects:

[0019] (1) the present application adopts the liquid control reversing valve to perceive the change of pump outlet pressure and load pressure, to dynamically regulate the main valve opening degree in the multi-way valve assembly, and to realize the proportional distribution of the outlet flow of the multi-way valve assembly under the flow saturation working condition, thereby solving the problem of the outlet flow of the multi-way valve preferentially running under light load caused by the valve pre-compensation structure;

[0020] (2) the present application adopts the structure scheme of double-pump driving double-motor, and the double-motor can realize series-parallel switching, thereby realizing the four-gear speed changing capability of the drilling machine in the rotary rock breaking, and significantly improving the application range and drilling speed of the drilling machine;

[0021] (3) the present application adopts the drilling mode of the hydraulic cylinder driving the drilling tool pressurization feeding, avoids the problem of the difficulty of the drilling machine in the hard rock stratum, and significantly improves the rapid feeding capability of the drilling machine in the complex geological stratum;

[0022] (4) the pressurization feeding and the rotary rock breaking working mode in the present application exist independent and linkage two states, improve the drilling depth and drilling rate of the drilling machine, and can meet the needs of deep land deep sea drilling and emergency drilling rescue. BRIEF DESCRIPTION OF DRAWINGS

[0023] In order to more clearly illustrate the technical scheme in the embodiments of the present application or the prior art, the drawings needed to be used in the embodiment or prior art description will be briefly introduced below, and obviously, the drawings in the following description are only some embodiments of the present application, and those skilled in the art can obtain other drawings according to these drawings without creating any creative labor.

[0024] Figure 1 is the principle diagram of the pressurization rotary hydraulic control system with multiple working modes described in the present application;

[0025] Figure 2 is the structure diagram of the multi-way valve assembly described in the present application;

[0026] Figure 3 is the principle diagram of the pressurization feeding working mode in the embodiment described in the present application;

[0027] Figure 4 is the principle diagram of the rotary rock breaking working mode in the embodiment described in the present application;

[0028] Figure 5 is the principle diagram of the rotary rock breaking working mode in the embodiment described in the present application.

[0029] ATTACHMENT Figure 1In the middle section: 1. Oil tank; 2. Motor; 3. Coupling; 4. Suction filter A; 5. Load-sensitive pump A; 6. Suction filter B; 7. Load-sensitive pump B; 8. Suction filter C; 9. Pilot pump; 10. Check valve; 11. Proportional relief valve; 12. Manual relief valve A; 13. Hydraulic relief valve A; 14. Throttle valve A; 15. Hydraulic directional valve A; 16. Throttle valve B; 17. Multi-way valve assembly Component A; 18. Proportional pressure reducing valve A; 19. Multi-way valve assembly B; 20. Proportional pressure reducing valve B; 21. Manual relief valve B; 22. Hydraulic relief valve B; 23. Throttle valve C; 24. Hydraulic directional valve B; 25. Throttle valve D; 26. Multi-way valve assembly C; 27. Proportional pressure reducing valve C; 28. Balance valve; 29. ​​Hydraulic cylinder; 30. Solenoid directional valve; 31. Hydraulic motor A; 32. Hydraulic motor B.

[0030] Among them, the appendix Figure 1 Appendix Figure 2 Appendix Figure 3 Appendix Figure 4 and attached Figure 5 P, T, A, and B represent the inlet and outlet ports of the hydraulic valve, respectively; a and b represent the pilot ports of the hydraulic control valve. Detailed Implementation

[0031] The following is in conjunction with the appendix Figure 1 The present invention will be further described below, but the scope of protection of the present invention is not limited thereto.

[0032] Example: Combining Figures 1-5 As shown, the pressurized rotary hydraulic control system with multiple working modes of the present invention comprises: a hydraulic power unit, a valve control unit, a pressurized feed execution unit, and a rotary rock-breaking execution unit.

[0033] The hydraulic power unit includes an oil tank 1, a motor 2, a coupling 3, a suction filter A4, a load-sensitive pump A5, a suction filter B6, a load-sensitive pump B7, a suction filter C8, a pilot pump 9, a check valve 10, and a proportional relief valve 11; the valve control unit includes a manual relief valve A12, a hydraulically controlled relief valve A13, a throttle valve A14, a hydraulically controlled directional valve A15, a throttle valve B16, a multi-way valve assembly A17, a proportional pressure reducing valve A18, a multi-way valve assembly B19, a proportional pressure reducing valve B20, a manual relief valve B21, a hydraulically controlled relief valve B22, a throttle valve C23, a hydraulically controlled directional valve B24, a throttle valve D25, a multi-way valve assembly C26, and a proportional pressure reducing valve C27; the pressurized feed actuator includes a balance valve 28 and a hydraulic cylinder 29; the rotary rock-breaking actuator includes a solenoid directional valve 30, a hydraulic motor A31, and a hydraulic motor B32.

[0034] As attached Figure 2As shown, the multi-way valve assembly A17, the multi-way valve assembly B19 and the multi-way valve assembly C26 have the same structure, which are composed of a main valve, a pressure compensation valve, a throttle valve a, a throttle valve b, a shuttle valve a, a shuttle valve b, an overflow valve a and an overflow valve b. The P port of the pressure compensation valve is connected with the hydraulic pump source, and is further connected with the oil port of the main valve; the A and B working oil ports of the main valve are connected with the actuator; the load oil pressure outlets of the main valve are connected with the left and right load feedback inlets of the shuttle valve a respectively; the load oil pressure outlets of the main valve are further connected with the overflow valve a and the overflow valve b respectively; the load feedback outlet of the shuttle valve a is connected with the upper load feedback inlet of the shuttle valve b; and the load feedback outlet of the shuttle valve b is connected with the external valve pump; the overflow valve a, the overflow valve b and the oil return T port of the main valve are all connected with the oil tank 1.

[0035] As shown in the accompanying drawings, Figure 1 As shown in the accompanying drawings,

[0036] As shown in the accompanying drawings, Figure 1As shown, the inlet of the load-sensitive pump B7 is connected to the oil tank 1 through the suction filter B6; the outlet of the load-sensitive pump B7 is connected to the inlet of the manual relief valve B21, the inlet of the hydraulic relief valve B22, the lower control port of the hydraulic relief valve B22, the inlet of the throttle valve C23, and the P port of the multi-way valve assembly C26; the A port of the multi-way valve assembly C26 is connected to the P port of the solenoid directional valve 30 and the lower oil port of the hydraulic motor A31; the upper oil port of the hydraulic motor A31 is connected to the A port of the solenoid directional valve 30; and the B port of the solenoid directional valve 30 is connected to the upper oil port of the hydraulic motor B32. The lower oil port of hydraulic motor B32 is connected to the T port of solenoid directional valve 30 and the B port of multi-way valve assembly C26; the pilot unloading port of multi-way valve assembly C26 is connected to the P port of hydraulic directional valve B24; the load feedback outlet of multi-way valve assembly C26 is connected to the inlet of throttle valve D25; the control port a and control port b of hydraulic directional valve B24 are connected to the outlet of throttle valve C23 and the outlet of throttle valve D25, respectively; the outlet of manual relief valve B21, the outlet of hydraulic relief valve B22, the T port of hydraulic directional valve B24, and the T port of multi-way valve assembly C26 are connected to oil tank 1, respectively.

[0037] As attached Figure 1 As shown, the inlet of the pilot oil pump 9 is connected to the oil tank 1 through the suction filter C8; the outlet of the pilot oil pump 9 is connected to the inlet of the check valve 10; a proportional relief valve 11 is installed on the branch oil lines of the pilot oil pump 9 and the check valve 10; the outlet of the check valve 10 is connected to the inlets of the proportional pressure reducing valves A18, B20, and C27 respectively; the outlet of the proportional pressure reducing valve A18 is connected to the pilot oil supply port of the multi-way valve assembly A17; the outlet of the proportional pressure reducing valve B20 is connected to the pilot oil supply port of the multi-way valve assembly B19; and the outlet of the proportional pressure reducing valve C27 is connected to the pilot oil supply port of the multi-way valve assembly C26.

[0038] As attached Figure 1 As shown, load-sensitive pump A5, load-sensitive pump B7 and pilot oil pump 9 are connected to motor 2 via coupling 3.

[0039] The pressurized rotary hydraulic control system with multiple working modes described in this invention has the following three working modes: pressurized feed working mode, single pump driven rotary rock breaking working mode, and dual pump driven rotary rock breaking working mode.

[0040] As attached Figure 3As shown, the pressurized feed working mode is as follows: Motor 2 drives the load-sensitive pump A5 and the pilot oil pump 9 to operate. The control oil output by the pilot oil pump 9 is regulated by the proportional pressure reducing valve A18 and then controls the opening of the main valve in the multi-way valve assembly A17. When the main valve in the multi-way valve assembly A17 is closed, the high-pressure oil discharged by the load-sensitive pump A5 is unloaded by the manual relief valve A12 and the hydraulic relief valve A13 and returns to the oil tank. When the main valve in the multi-way valve assembly A17 is open, the high-pressure oil discharged by the load-sensitive pump A5 flows into the P port of the pressure compensation valve in the multi-way valve assembly A17 and further flows into the oil inlet of the main valve in the multi-way valve assembly A17. When the main valve in multi-way valve assembly A17 is in the upper position, oil flows from port A of the main valve into the rodless chamber of the hydraulic cylinder, driving the piston of hydraulic cylinder 29 to extend and complete the pressurized feed operation. When the main valve in multi-way valve assembly A17 is in the lower position, oil flows from port B of the main valve into the rod chamber of the hydraulic cylinder, driving the piston of hydraulic cylinder 29 to retract and complete the drilling tool lifting operation. Simultaneously, the shuttle valve in multi-way valve assembly A17 feeds back the load pressure to the receiving end of the load-sensitive pump A5 to adjust the output pressure and flow rate of the load-sensitive pump A5 to match the load demand, thereby reducing overflow losses and achieving higher energy efficiency. This operating mode combines the advantages of rapid feed and pressurized propulsion for active rock breaking, making it particularly suitable for drilling in deep hard rock formations.

[0041] As attached Figure 4As shown, the single pump driving rotary rock breaking working mode is as follows: the motor 2 drives the load sensitive pump B7 and the pilot pump 9 to operate, the control oil output by the pilot pump 9 is adjusted by the proportional pressure reducing valve C27, and then controls the opening degree of the main valve in the multi-way valve assembly C26. When the main valve in the multi-way valve assembly C26 is closed, the high-pressure oil discharged by the load sensitive pump B7 returns to the oil tank after unloading by the manual overflow valve B21 and the hydraulic control overflow valve B22; when the main valve in the multi-way valve assembly C26 is opened, the high-pressure oil discharged by the load sensitive pump B7 flows into the P port of the pressure compensation valve in the multi-way valve assembly C26, and further flows into the oil inlet of the main valve in the multi-way valve assembly C26. When the main valve in the multi-way valve assembly C26 works at the upper position, the oil flows from the A port of the main valve in the multi-way valve assembly C26 into the lower oil port of the hydraulic motor A31, and then flows back from the lower oil port of the hydraulic motor B32 to the B port of the main valve in the multi-way valve assembly C26 through the hydraulic motor A31 and the hydraulic motor B32, at this time, the double motors are in the clockwise rotation state; when the main valve in the multi-way valve assembly C26 works at the lower position, the oil flows from the B port of the main valve in the multi-way valve assembly C26 into the lower oil port of the hydraulic motor B32, and then flows back from the lower oil port of the hydraulic motor A31 to the A port of the main valve in the multi-way valve assembly C26 through the hydraulic motor B32 and the hydraulic motor A31, at this time, the double motors are in the counterclockwise rotation state. At the same time, the electromagnetic reversing valve 30 controls the series-parallel switching of the motors, and when the double motors are in parallel, it is low-speed and large-torque output, which is suitable for hard rock stratum drilling working conditions; when the double motors are in series, it is high-speed and small-torque output, which is suitable for soft stratum drilling working conditions. At the same time, the shuttle valve in the multi-way valve assembly C26 feeds back the load pressure to the receiving end of the load sensitive pump B7, so as to adjust the pressure and flow of the load sensitive pump B7 output, so as to match the load demand, thereby reducing the overflow loss and having higher energy saving efficiency. This working mode has the advantages of stepless speed regulation and multi-torque output in hole forming drilling. At the same time, with the help of the ability of load sensing technology to perceive the change of load pressure, the drill string sticking accident is effectively avoided, and overload protection can be realized.

[0042] As shown in the accompanying drawings Figure 5As shown, the double-pump driving rotary rock breaking working mode is as follows: in order to enhance the rock breaking efficiency of the system and increase the motor rotating speed, on the basis of the single-pump driving hydraulic rotary rock breaking function circuit, i.e. under the premise of keeping the load-sensitive pump B7 normally driving the motor, the load-sensitive pump A5 is operated by the motor 2, and the control oil output by the pilot oil pump 9 is adjusted by the proportional pressure reducing valve B20 to open the main valve in the multi-way valve assembly B19. At this time, the high-pressure oil output by the load-sensitive pump A5 is adjusted by the multi-way valve assembly B19, and then flows together with the high-pressure oil output by the load-sensitive pump B7 to drive the double-motor rotary. When the main valve in the multi-way valve assembly B19 and the main valve in the multi-way valve C26 are both working in the upper position, at this time, the double-motor is in the clockwise rotary state under the high-power driving; when the main valve in the multi-way valve assembly B19 and the main valve in the multi-way valve C26 are both working in the lower position, at this time, the double-motor is in the counterclockwise rotary state under the high-power driving, and the pipeline connection between the double-motors and the working principle are the same as those under the single-pump driving mode. At the same time, the electromagnetic reversing valve 30 controls the series-parallel switching of the motor. At the same time, the shuttle valve in the multi-way valve assembly B19 feeds back the load pressure to the receiving end of the load-sensitive pump A5 to adjust the pressure and flow rate of the load-sensitive pump A5 output to match the load demand, thereby reducing the overflow loss and having higher energy-saving efficiency. On the other hand, when the main valve in the multi-way valve assembly B19 is closed, the high-pressure oil discharged by the load-sensitive pump A5 is returned to the oil tank after being unloading by the manual overflow valve A12 and the hydraulic control overflow valve A13. This working mode has the advantages of high-power output and fast cutting rock, and is suitable for drilling work conditions of super deep well and hard rock. At the same time, by means of the load-sensitive technology, the system pressure and flow rate are adjusted, the double-pump outlet pressure is adjusted in real time, and the impact and fluctuation problems after the double-pump flow together are effectively avoided.

[0043] The hydraulic circuits of the pressurized feeding working mode, the single-pump driving rotary rock breaking working mode and the double-pump driving rotary rock breaking working mode all contain a pilot oil unloading assembly, which is composed of the throttle valve A14, the hydraulic control reversing valve A15, the throttle valve B16, the throttle valve C23, the hydraulic control reversing valve B24 and the throttle valve D25. Among them, the hydraulic control reversing valve A15 and the hydraulic control reversing valve B24 dynamically adjust the pilot pressure of the main valve in the multi-way valve assembly by sensing the change of the pump outlet pressure and the load pressure, thereby adjusting the opening degree of the main valve in the multi-way valve assembly, and further realizing that the outlet flow rate of the multi-way valve assembly can still be proportionally distributed under the flow rate saturation working condition, thereby solving the problem that the outlet flow rate of the multi-way valve is preferentially running under light load caused by the valve front compensation form under different load working conditions.

[0044] During the system operation, the pressurized feeding working mode and the rotary rock breaking working mode can realize independent and linked two working states, thereby achieving the multifunctional requirements of high and low speed rotary rock breaking of the drilling tool, pressurized drilling of super deep well, load-sensitive regulation and remote proportional regulation during drilling.

[0045] It should be understood that although the present specification is described in terms of various working modes, not every working mode contains only one independent technical solution, and the description of the specification is only for the sake of clarity. The skilled person should consider the specification as a whole, and the technical solutions in each working mode can also be appropriately combined to form other working modes that can be understood by the skilled person.

[0046] The above series of detailed descriptions are only specific descriptions of the feasible working modes of the present application, and are not used to limit the protection scope of the present application. Equivalent embodiments or changes made without departing from the spirit of the present application should be included in the protection scope of the present application.

Claims

1. A pressurized swash plate hydraulic control system having multiple operating modes, characterized by, It comprises: a tank (1) connected with a load sensing pump A (5) through an oil suction filter A (4); the tank (1) is connected with a load sensing pump B (7) through an oil suction filter B (6); the tank (1) is connected with a pilot pump (9) through an oil suction filter C (8); the load sensing pump A (5) is connected with the inlet of a manual overflow valve A (12), the inlet of a hydraulic control overflow valve A (13), a throttle valve A (14), the P port of a multi-way valve assembly A (17) and the P port of a multi-way valve assembly B (19) respectively; the load sensing pump B (7) is connected with the inlet of a manual overflow valve B (21), the inlet of a hydraulic control overflow valve B (22), a throttle valve C (23) and the P port of a multi-way valve assembly C (26) respectively; the pilot pump (9) is connected with a one-way valve (10), and a proportional overflow valve (11) is installed on the branch oil circuit of the pilot pump (9) and the one-way valve (10); the A port of the multi-way valve assembly A (17) is connected with the inlet of a balance valve (28), the B port of the multi-way valve assembly A (17) is connected with the upper oil port of a hydraulic cylinder (29), the outlet of the balance valve (28) is connected with the lower oil port of the hydraulic cylinder (29), the pilot oil discharge port of the multi-way valve assembly A (17) is connected with the P port of a hydraulic control reversing valve A (15), the load feedback outlet of the multi-way valve assembly A (17) is connected with a throttle valve B (16), and the T port of the multi-way valve assembly A (17) is connected with the tank (1); the A port of the multi-way valve assembly B (19) is connected with the P port of an electromagnetic reversing valve (30) and the lower oil port of a hydraulic motor A (31), the B port of the multi-way valve assembly B (19) is connected with the lower oil port of a hydraulic motor B (32) and the T port of the electromagnetic reversing valve (30), the pilot oil discharge port of the multi-way valve assembly B (19) is connected with the P port of the hydraulic control reversing valve A (15), the load feedback outlet of the multi-way valve assembly B (19) is connected with the load feedback inlet of the multi-way valve assembly A (17), and the T port of the multi-way valve assembly B (19) is connected with the tank (1); the A port of the multi-way valve assembly C (26) is connected with the P port of the electromagnetic reversing valve (30) and the lower oil port of the hydraulic motor A (31), the B port of the multi-way valve assembly C (26) is connected with the lower oil port of the hydraulic motor B (32) and the T port of the electromagnetic reversing valve (30), the pilot oil discharge port of the multi-way valve assembly C (26) is connected with the P port of a hydraulic control reversing valve B (24), the load feedback outlet of the multi-way valve assembly C (26) is connected with a throttle valve D (25), and the T port of the multi-way valve assembly C (26) is connected with the tank (1).

2. The pressurized swash plate hydraulic control system having multiple operating modes of claim 1, wherein, Three working modes are provided: a pressurized feeding working mode, a single pump driving rotary rock breaking working mode and a double pump driving rotary rock breaking working mode.

3. The pressurized rotary progression hydraulic control system with multiple operating modes of claim 2, wherein, In the pressurized feeding working mode, the inlet of the load sensing pump A (5) is connected with the oil tank (1) through the oil suction filter A (4); the outlet of the load sensing pump A (5) is connected with the inlet of the manual overflow valve A (12), the inlet of the hydraulic control overflow valve A (13), the lower control port of the hydraulic control overflow valve A (13), the inlet of the throttle valve A (14) and the P port of the multi-way valve assembly A (17) respectively; the A port of the multi-way valve assembly A (17) is communicated with the inlet of the balance valve (28); the outlet of the balance valve (28) is connected with the upper oil port of the hydraulic cylinder (29); the lower oil port of the hydraulic cylinder (29) is connected with the B port of the multi-way valve assembly A (17); the pilot oil discharge port of the multi-way valve assembly A (17) is connected with the P port of the hydraulic control reversing valve A (15); the load feedback outlet of the multi-way valve assembly A (17) is connected with the inlet of the throttle valve B (16); the control ports a and b of the hydraulic control reversing valve A (15) are connected with the outlets of the throttle valve A (14) and the throttle valve B (16) respectively; the outlets of the manual overflow valve A (12), the hydraulic control overflow valve A (13), the T port of the hydraulic control reversing valve A (15) and the T port of the multi-way valve assembly A (17) are communicated with the oil tank (1).

4. The pressurized rotary progression hydraulic control system having multiple operating modes of claim 3, wherein, In the single pump driving rotary rock breaking working mode, the inlet of the load sensing pump B (7) is connected with the oil tank (1) through the oil suction filter B (6); the outlet of the load sensing pump B (7) is connected with the inlet of the manual overflow valve B (21), the inlet of the hydraulic control overflow valve B (22), the lower control port of the hydraulic control overflow valve B (22), the inlet of the throttle valve C (23) and the P port of the multi-way valve assembly C (26) respectively; the A port of the multi-way valve assembly C (26) is connected with the P port of the electromagnetic reversing valve (30) and the lower oil port of the hydraulic motor A (31); the upper oil port of the hydraulic motor A (31) is communicated with the A port of the electromagnetic reversing valve (30); the B port of the electromagnetic reversing valve (30) is connected with the upper oil port of the hydraulic motor B (32); the lower oil port of the hydraulic motor B (32) is connected with the T port of the electromagnetic reversing valve (30) and further connected with the B port of the multi-way valve assembly C (26); the pilot oil discharge port of the multi-way valve assembly C (26) is connected with the P port of the hydraulic control reversing valve B (24); the load feedback outlet of the multi-way valve assembly C (26) is connected with the inlet of the throttle valve D (25); the control ports a and b of the hydraulic control reversing valve B (24) are connected with the outlets of the throttle valve C (23) and the throttle valve D (25) respectively; the outlets of the manual overflow valve B (21), the hydraulic control overflow valve B (22), the T port of the hydraulic control reversing valve B (24) and the T port of the multi-way valve assembly C (26) are communicated with the oil tank (1).

5. The pressurized swash plate hydraulic control system having multiple operating modes of claim 4, wherein, In the double-pump driving rotary rock breaking mode, the inlet of the load-sensitive pump A (5) is connected with the oil tank (1) through the oil suction filter A (4); the outlet of the load-sensitive pump A (5) is connected with the inlet of the manual overflow valve A (12), the inlet of the hydraulic control overflow valve A (13), the lower control port of the hydraulic control overflow valve A (13), the inlet of the throttle valve A (14), the P port of the multi-way valve assembly A (17), and the P port of the multi-way valve assembly B (19) respectively; the A port of the multi-way valve assembly A (17) is communicated with the inlet of the balance valve (28); the outlet of the balance valve (28) is connected with the upper oil port of the hydraulic cylinder (29); the lower oil port of the hydraulic cylinder (29) is connected with the B port of the multi-way valve assembly A (17); the A port of the multi-way valve assembly B (19) is connected with the P port of the electromagnetic reversing valve (30) and the lower oil port of the hydraulic motor A (31); the upper oil port of the hydraulic motor A (31) is communicated with the A port of the electromagnetic reversing valve (30); the B port of the electromagnetic reversing valve (30) is connected with the upper oil port of the hydraulic motor B (32); the lower oil port of the hydraulic motor B (32) is connected with the T port of the electromagnetic reversing valve (30), and is further communicated with the B port of the multi-way valve assembly B (19); the pilot oil discharge port of the multi-way valve assembly B (19) and the pilot oil discharge port of the multi-way valve assembly A (17) are connected with the P port of the hydraulic control reversing valve A (15) respectively; the load feedback outlet of the multi-way valve assembly B (19) is communicated with the load feedback inlet of the multi-way valve assembly A (17), and is further connected with the inlet of the throttle valve B (16); the control ports a and b of the hydraulic control reversing valve A (15) are connected with the outlet of the throttle valve A (14) and the outlet of the throttle valve B (16) respectively; the outlets of the manual overflow valve A (12), the hydraulic control overflow valve A (13), the hydraulic control reversing valve A (15), the multi-way valve assembly A (17), and the multi-way valve assembly B (19) are communicated with the oil tank (1).

6. The pressurized rotary progression hydraulic control system having multiple operating modes of claim 5, wherein, The pilot oil discharge port of the multi-way valve assembly B (19) is connected with the P port of the hydraulic control reversing valve A (15) through the pilot oil discharge port in the multi-way valve assembly A (17); the load feedback outlet of the multi-way valve assembly B (19) is connected with the inlet of the throttle valve B (16) through the shuttle valve in the multi-way valve assembly A (17).

7. The pressurized rotary progression hydraulic control system having multiple operating modes of claim 5, wherein, The outlets of the one-way valve (10) are connected with the inlets of the proportional pressure reducing valve A (18), the proportional pressure reducing valve B (20), and the proportional pressure reducing valve C (27) respectively; the outlet of the proportional pressure reducing valve A (18) is connected with the pilot oil supply port of the multi-way valve assembly A (17); the outlet of the proportional pressure reducing valve B (20) is connected with the pilot oil supply port of the multi-way valve assembly B (19); the outlet of the proportional pressure reducing valve C (27) is connected with the pilot oil supply port of the multi-way valve assembly C (26).

8. The pressurized rotary progression hydraulic control system having multiple operating modes of claim 1, wherein, The load sensing pump A (5), the load sensing pump B (7) and the pilot pump (9) are all connected with the motor (2) through a coupling (3).

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