Hydraulic control system for pressurizing winch of rotary drilling rig and control method of hydraulic control system

Abstract

The invention provides a hydraulic control system and a control method of a rotary drilling rig pressurizing winch, and the hydraulic control system of the rotary drilling rig pressurizing winch comprises a first oil path, a second oil path, an overflow valve, a first electromagnetic valve, an inverse proportion electromagnetic valve and a first one-way valve, the first oil way and the second oil way are respectively communicated with a first oil port and a second oil port of the pressurizing winch motor, the overflow valve, the first electromagnetic valve and the inverse proportion electromagnetic valve are respectively connected between the first oil way and the second oil way, and the overflow valve, the first electromagnetic valve and the inverse proportion electromagnetic valve are respectively arranged in parallel. The initial current of the inverse proportional electromagnetic valve is a first current value, when the load exceeds the lifting force of the main winch, the input current of the inverse proportional electromagnetic valve is reduced, the system pressure is increased, meanwhile, the flow output of the main winch system is controlled through speed matching calculation, and the speed of the main winch is close to that of pressurized winch as much as possible; and the pressurizing winch can cooperate with the main winch to synchronously lift. According to the hydraulic control system for the pressurization winch of the rotary drilling rig, the pressurization winch and the main winch can have synchronism, meanwhile, the pressurization winch motor is prevented from sucking air, and the multi-working-condition requirements of the rotary drilling rig are met.

Description

Technical Field

[0001] The invention relates to the technical field of foundation construction, and in particular to a hydraulic control system for a pressurized winch of a rotary drilling rig and a control method thereof. Background Art

[0002] The main function of the balance valve of the traditional pressurized winch is that when the rotary drilling rig stops operating the pressurized action, the balance valve can be returned to the middle position to achieve the pressure-maintaining action and keep the power head in the current position. When using the long spiral drill rod method (i.e. CFA method), the main winch pulley group and the winch pressurized pulley group are both installed on the power head. The main winch motor and the pressurized winch motor output torque at the same time, so that the main winch wire rope and the pressurized winch wire rope lift the power head together. When the load can be lifted by the main winch alone, the main winch drives the power head to rise, and the slide of the power head will be lifted quickly. However, the existing balance valve group does not have a follow-up function. When the lifting speed of the main winch is greater than the lifting speed of the pressurized winch, the pressurized winch will become a load, causing energy loss and damage to the structural parts. When the load is large and the main winch cannot be lifted alone, the pressure of the existing pressurized winch system is manually adjusted by the overflow valve, which is inconvenient to control the pressure and has poor synchronization and unstable speed. Summary of the invention

[0003] In view of this, the object of the present invention is to provide a hydraulic control system for a pressurized winch of a rotary drilling rig, wherein the balancing valve group can synchronize the pressurized winch with the main winch, prevent the pressurized winch motor from being sucked out of air, and meet the multi-working conditions of the rotary drilling rig.

[0004] The present invention provides a hydraulic control system for a pressurized winch of a rotary drilling rig, comprising a balancing valve group, wherein the balancing valve group comprises a first oil circuit, a second oil circuit, a relief valve, a first solenoid valve, an inverse proportional solenoid valve and a first non-return valve, wherein the first oil circuit and the second oil circuit are respectively connected to a first oil port and a second oil port of a pressurized winch motor, wherein the relief valve, the first solenoid valve and the inverse proportional solenoid valve are respectively connected between the first oil circuit and the second oil circuit, wherein the relief valve, the first solenoid valve and the inverse proportional solenoid valve are respectively arranged in parallel, wherein the first non-return valve and the first non-return valve are connected to each other. A solenoid valve is arranged in series, the first one-way valve allows oil to flow from the second oil circuit to the first oil circuit, the first solenoid valve is energized, the initial current of the inverse proportional solenoid valve is a first current value, the pressurized winch follows the action of the main winch, when the load exceeds the lifting force of the main winch, the input current of the inverse proportional solenoid valve is reduced, the pressure of the second oil circuit is increased, and at the same time, through speed matching calculation, the flow of the main winch system is controlled to make the speed of the main winch equal to the speed of the pressurized winch, so that the pressurized winch can cooperate with the main winch to lift together.

[0005] In one embodiment, the balancing valve group also includes a third one-way valve, which is connected in series with the inverse proportional solenoid valve. The third one-way valve allows the oil to flow from the first oil circuit into the second oil circuit, but does not allow the oil to flow from the second oil circuit into the first oil circuit.

[0006] In one embodiment, the hydraulic control system of the rotary drilling rig pressurized winch further includes a first shuttle valve, the first shuttle valve is connected to the third oil circuit, and the first shuttle valve is arranged between the pressurized unlocking valve and the brake.

[0007] In one embodiment, the rotary drilling rig further includes a pressure sensor, and the pressure sensor is used to detect the pressure of the main hoisting motor.

[0008] In one embodiment, the rotary drilling rig further includes a rotation speed sensor, and the rotation speed sensor is used to detect the rotation speed of the main winch motor.

[0009] In one embodiment, the rotary drilling rig is provided with a control system, and the pressure sensor, the speed sensor, the first solenoid valve, and the inverse proportional solenoid valve are electrically connected to the control system respectively, and the control system analyzes the data of the pressure sensor and determines the relationship between the load and the lifting force of the main winch.

[0010] The present invention also relates to a control method for a hydraulic control system of the above-mentioned pressurized winch of a rotary drilling rig, the control method comprising: unlocking the brake; detecting the pressure of the main winch motor by means of a pressure sensor, and the control system judging the relationship between the load and the lifting force of the main winch; when the load is less than the maximum lifting force of the main winch, the first solenoid valve is energized, and the oil in the second oil circuit is allowed to flow to the first oil circuit, and the pressurized winch will not drag the main winch when releasing the rope; to prevent air suction, the input current of the inverse proportional solenoid valve is set to the first current value, so that the auxiliary pump supplies the first oil circuit with oil of the first flow rate and pressure, at which time the main winch speed is faster than the pressurized winch, and the pressurized winch follows the action of the main winch to ensure synchronization; by installing The pressure sensor and speed sensor on the main winch motor judge the load. The judgment condition is: if the pressure value p on the main winch motor is ≥ 320 bar and the speed sensor's speed n is ≤ 0.1 rpm, it is judged that the load exceeds the maximum lifting force of the main winch, so that the first solenoid valve is energized, the auxiliary pump and the auxiliary valve increase the output pressure and output flow, the oil in the first oil circuit is not allowed to flow to the second oil circuit, and the input current of the inverse proportional solenoid valve is set to the second current value. The pressure of the overflow valve becomes higher, so that the pressurized winch outputs a lifting force to meet the load demand. At the same time, through speed matching calculation, the target value of the main winch system pump displacement output is obtained, so that the lifting speed of the main winch is consistent with that of the pressurized winch. The calculation process is as follows: Speed ​​of pressure winch v1 , n 1 is the current engine speed, V 1 is the maximum displacement of the auxiliary pump (181), and the speed ratio of the pressure winch reducer is i 1 , the diameter of the pressure winch drum is d 1， Speed ​​of main winch v 2 , V 2 is the displacement of the main winch system pump that needs to be controlled, and the speed ratio of the main winch reducer is i 2 , the diameter of the main winch drum is d 2， Speed ​​of main winch v 2 ; v 1 =j(n 1 ,V 1 ,i 1 ,d 1 ); v 2 =j(n 1 ,V 2 ,i 2 ,d 2 ); To make v 1 = v 2 , so we can get: V 2 =k(n 1 ,V 1 ,i 1 ,d 1, i 2 ,d 2 ) Then, the input current of the main winch system pump during the CFA method is obtained through the current-displacement curve.

[0011] In one embodiment, the hydraulic control system of the pressurized winch of the rotary drilling rig also includes a pilot pump and a pressurized unlocking valve, the pilot pump is connected to the pressurized unlocking valve, the pressurized unlocking valve is connected to the brake through a third oil circuit, the brake is used to brake the power head, when the main winch can meet the lifting force requirement alone, the solenoid valve is energized, the pressurized winch follows the main winch, the auxiliary pump outputs oil with a flow rate less than 50L / min and a pressure less than 35bar to the B port of the balancing valve group, the oil pressure is less than the inlet pressure of the pressure reducing valve, resulting in no oil entering the brake oil port, and the oil pressure at the brake oil port cannot unlock the brake; the pressurized unlocking valve is energized to cause the pilot pump to output oil to the brake, thereby unlocking the brake.

[0012] In one embodiment, when the pressure of the pressurized winch oil circuit increases and the pressure output at the Br port reaches the maximum value, the oil pressure on the left side of the shuttle valve is equal to the oil pressure on the right side, which can still ensure that the oil in the solenoid valve and the Br port merges through the shuttle valve and is delivered to the brake through the third oil circuit.

[0013] The hydraulic control system of the pressurized winch of the rotary drilling rig of the present invention adds a first solenoid valve, a first non-return valve and an inverse proportional solenoid valve between the first oil circuit, and the inverse proportional solenoid valve is respectively arranged in parallel with the solenoid valve and the first non-return valve. When the load is small or the main winch can meet the lifting force requirement, the first solenoid valve is energized, and the pressurized winch follows the main winch to move synchronously, avoiding the phenomenon of air suction in the motor of the main winch, and the pressurized winch will not have the problem of back-dragging the main winch. When the load exceeds the lifting force of the main winch, the first solenoid valve is energized, and the input current of the inverse proportional solenoid valve is set to the second current value, so that the pressurized winch outputs the lifting force. At the same time, through speed matching calculation, the flow of the main winch system is reduced, so that the speed of the main winch is equal to that of the pressurized winch, ensuring that the main winch and the pressurized winch are lifted synchronously to meet the load requirement and meet the needs of multi-working conditions such as lifting drill rods or lifting power heads of rotary drilling rigs. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for use in the embodiments are briefly introduced below. It should be understood that the following drawings only show certain embodiments of the present invention and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without creative work.

[0015] Figure 1 The invention discloses a hydraulic principle diagram of a hydraulic control system for a pressurized winch of a rotary drilling rig.

[0016] Explanation of the accompanying figure numbers: first oil circuit-111; second oil circuit-112; third oil circuit-113; overflow valve-12; first solenoid valve-13; inverse proportional solenoid valve-14; first one-way valve-151; third one-way valve-153; pilot pump-161; pressurized unlocking valve-162; first shuttle valve-163; pressure reducing valve-173; auxiliary pump-181; auxiliary valve-182; brake-21.

[0017] The realization of the purpose, functional features and advantages of the present invention will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0018] The specific embodiments of the present invention will be described in detail below in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all of the embodiments. Based on the description of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0019] In the description of the present invention, unless otherwise clearly specified and limited, the terms "set", "install", "connection" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to specific circumstances.

[0020] The directions or positional relationships indicated by terms such as “upper”, “lower”, “left”, “right”, “front”, “back”, “top”, “bottom”, “inside” and “outside” are based on the directions or positional relationships shown in the accompanying drawings, or are the directions or positional relationships in which the inventive product is usually placed when used. They are only for the convenience of description and simplified description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore should not be understood as a limitation on the present invention.

[0021] The terms "first", "second", "third", etc. are merely used to distinguish elements of similar nature, and do not indicate or imply relative importance or a particular order.

[0022] The terms "comprises," "comprising," or any other variations thereof, are intended to cover a non-exclusive inclusion of the elements listed and may also include additional elements not expressly listed.

[0023] like Figure 1As shown, the hydraulic control system of the pressurized winch of the rotary drilling rig includes a balancing valve group, which includes a first oil circuit 111, a second oil circuit 112, a relief valve 12, a first solenoid valve 13, an inverse proportional solenoid valve 14 and a first non-return valve 151. The first oil circuit 111 and the second oil circuit 112 are respectively connected to the first oil port and the second oil port of the pressurized winch motor, wherein the first oil port is a forward oil port and the second oil port is a reverse oil port. Therefore, the oil drives the pressurized winch motor through the first oil circuit 111 or the second oil circuit 112 to make the pressurized winch motor rotate forward or reverse. The relief valve 12, the first solenoid valve 13 and the inverse proportional solenoid valve 14 are respectively connected to the first oil circuit 111 and the second oil circuit 112. The first solenoid valve 13 is a switch valve that can control the connection and interruption of the first oil circuit 111 and the second oil circuit 112. The overflow valve 12, the first solenoid valve 13 and the inverse proportional solenoid valve 14 are respectively arranged in parallel. The first check valve 151 is arranged in series with the first solenoid valve 13. The first check valve 151 allows oil to flow from the second oil circuit 112 to the first oil circuit 111. The hydraulic control system of the rotary drilling rig pressurized winch also includes a third check valve 153. The third check valve 153 is connected in series with the inverse proportional solenoid valve 14. The input current of the inverse proportional solenoid valve 14 is 0mA~20mA, and the corresponding pressure is 350bar~35bar, preferably 350 bar, 320bar or 35bar, etc.; wherein 20mA is the first current value, 2mA is the second current value, the third one-way valve 153 allows oil to flow from the first oil circuit 111 to the second oil circuit 112, but does not allow oil to flow from the second oil circuit 112 to the first oil circuit 111. When the first solenoid valve 13 is energized, the initial current of the inverse proportional solenoid valve 14 is the first current value, i.e. 20mA, and the pressurized winch follows the main winch. When the load exceeds the lifting force of the main winch, the input current of the inverse proportional solenoid valve 14 is reduced to 2mA, so that the pressurized winch cooperates with the main winch to lift together. Therefore, the first one-way valve 151 and the third one-way valve 153 can ensure that the first solenoid valve 13 and the inverse proportional solenoid valve 14 will not affect the use scenarios of non-CFA methods, and meet the needs of multi-method construction. In this embodiment, the pressure is maximum when the input current of the inverse proportional solenoid valve 14 is 0, and the pressure decreases proportionally as the input current increases. Therefore, when the CFA working condition is not used, the input current of the inverse proportional solenoid valve 14 is 0, and when the load is less than or equal to the main winch lifting force, the input current of the inverse proportional solenoid valve 14 is 20mA. When the load exceeds the main winch lifting force, the input current of the inverse proportional solenoid valve 14 is 2mA.

[0024] When the load is small or the main winch can meet the lifting force requirement, the first solenoid valve 13 is energized, and the oil in the second oil circuit 112 is allowed to flow to the first oil circuit 111. Due to the action of the first one-way valve 151, the oil in the first oil circuit 111 is not allowed to flow to the second oil circuit 112. At this time, the pressurized winch moves synchronously with the main winch, and the input current of the inverse proportional solenoid valve 14 is set to a first current value, so that the auxiliary pump 181 supplies the first flow of oil to the first oil circuit 111 (the first flow refers to a flow less than 50L / min), so as to avoid the motor of the pressurized winch from sucking air, causing cavitation, and affecting the reliability of the motor; When the load exceeds the lifting force of the main winch, the first solenoid valve 13 is energized, and the oil in the second oil circuit 112 is allowed to flow to the first oil circuit 111, and the pressurized winch releases the rope. The pressurized winch does not drag the main winch back, and the input current of the inverse proportional solenoid valve 14 is reduced, that is, the input current of the inverse proportional solenoid valve 14 is set to the second current value (2mA). The pressure of the second oil circuit 112 is increased, and at the same time, the flow of the main winch system is controlled through speed matching calculation, so that the speed of the main winch is equal to the speed of the pressurized winch, so that the pressurized winch can cooperate with the main winch to lift together.

[0025] Preferably, the hydraulic control system of the pressurized winch of the rotary drilling rig also includes a pilot pump 161 and a pressurized unlocking valve 162, the pilot pump 161 is connected to the pressurized unlocking valve 162, the pressurized unlocking valve 162 is connected to the brake 21 through the third oil circuit 113, the brake 21 is used to brake the power head, and the pressurized winch controls the lifting and lowering of the power head through the wire rope for braking. When the main winch can meet the lifting force requirement alone, the first solenoid valve 13 is energized, the pressurized winch follows the main winch, and the auxiliary pump 181 outputs oil with a flow rate of less than 50L / min and a pressure of less than 35bar to the A port or the balance valve group. At the B port, the oil pressure is less than the inlet pressure of the pressure reducing valve 173, resulting in no oil entering the brake oil port, and the brake 21 cannot be unlocked; the CFA method pressurized unlocking valve 162 is always energized to enable the pilot pump 161 to output oil to the brake 21, so that the brake 21 is unlocked, wherein the pressurized unlocking valve 162 is energized to reverse, so that the pilot pump 161 is connected to the third oil circuit 113, even when the load increases, the pressure output of the Br port reaches the maximum value, at this time, the oil pressure on the left and right sides of the first shuttle valve 163 is equal, and it can still ensure that the oil of the pressurized unlocking valve 162 and the Br port merge and then be delivered to the brake 21 through the third oil circuit 113. Note: If the pressure at the Br port does not reach the maximum, it cannot merge, and at this time, the oil at the pressurized unlocking valve 162 port enters the brake. In this embodiment, the hydraulic control system of the rotary drilling rig pressurized winch also includes an auxiliary valve 182, the auxiliary valve 182 is connected to the auxiliary pump 181, the first oil circuit 111 and the second oil circuit 112 are respectively connected to the auxiliary pump 181, and the auxiliary valve 182 is used to input the oil of the auxiliary pump 181 into the first oil circuit 111 or the second oil circuit 112 respectively.

[0026] Preferably, the hydraulic control system of the rotary drilling rig pressurized winch also includes a first shuttle valve 163, which is connected to the third oil circuit 113 and is arranged between the pressurized unlocking valve 162 and the brake 21. The first shuttle valve 163 mainly functions to realize the control of the brake unlocking by two oil lines. In non-CFA working conditions, the oil at the Br port enters the brake through this valve, and in CFA working conditions, the oil at the solenoid valve 162 enters the brake through this valve. Preferably, the rotary drilling rig further comprises a pressure sensor, and the pressure sensor is used to detect the pressure of the main hoisting motor.

[0027] Preferably, the rotary drilling rig further comprises a rotation speed sensor, and the rotation speed sensor is used to detect the rotation speed of the main hoisting motor.

[0028] Preferably, the rotary drilling rig is provided with a control system, and the pressure sensor, the speed sensor, the first solenoid valve 13 and the inverse proportional solenoid valve 14 are electrically connected to the control system respectively. The control system analyzes the data of the pressure sensor and determines the relationship between the load and the lifting force of the main winch. For example, the control system analyzes the data of the pressure sensor and determines that the lifting force of the main winch can meet the load demand alone, or the load exceeds the maximum lifting force of the main winch.

[0029] The present invention also relates to a control method for a hydraulic control system of the above-mentioned rotary drilling rig pressurized winch, the control method comprising: Unlock the brake 21; specifically, when the main winch can meet the lifting force requirement alone, the solenoid valve 13 is energized, the pressurized winch follows the main winch, and the auxiliary pump 181 outputs oil with a flow rate less than 50L / min and a pressure less than 35bar to the A port or B port of the balancing valve group. The oil pressure is less than the inlet pressure of the pressure reducing valve 173, resulting in no oil entering the brake oil port, and the oil pressure at the brake oil port cannot unlock the brake 21; the pressurized unlocking valve 162 is energized to make the pilot pump 161 outputs oil to the brake 21 to unlock the brake 21. Even when the pressure of the first oil circuit 111 increases and the pressure at the Br port is output to the maximum value, the oil pressures on the left and right sides of the first shuttle valve 163 are equal, and the oil at the pressurized unlocking valve 162 and the Br port are combined through the first shuttle valve 163 and then delivered to the brake 21 through the third oil circuit 113. Note: If the pressure at the Br port does not reach the maximum, it cannot be combined. At this time, the oil at the pressurized unlocking valve 162 enters the brake 21.

[0030] The pressure sensor detects the pressure of the main winch motor, and the control system determines the relationship between the load and the lifting force of the main winch; for example, the control system analyzes the data of the pressure sensor and determines whether the lifting force of the main winch can meet the load demand alone, or the load exceeds the lifting force of the main winch. In addition, the control system controls the inverse proportional solenoid valve 14 in real time according to the load demand, so that the main winch and the pressure winch cooperate to meet the lifting force of the load.

[0031] When the load is less than the maximum lifting force of the main winch, the first solenoid valve 13 is energized, and the oil in the second oil circuit 112 is allowed to flow to the first oil circuit 111, so that the pressurized winch will not drag the main winch when releasing the rope; to prevent air suction, the input current of the inverse proportional solenoid valve 14 is set to a first current value (20mA), so that the auxiliary pump 181 supplies oil of a first flow rate and pressure to the first oil circuit 111 (the flow value of the first flow rate is less than 50L / min, and the pressure is less than 35bar), so as to avoid air suction of the motor of the pressurized winch, cavitation, and affect the reliability of the motor. At this time, the speed of the main winch is faster than that of the pressurized winch, and the pressurized winch follows the action of the main winch to ensure synchronization; The load is judged by the pressure sensor and speed sensor installed on the main winch motor. The judgment condition is: the pressure value p on the main winch motor is ≥ 320bar, and the speed of the speed sensor is n ≤ 0.1rpm. It is judged that the load exceeds the maximum lifting force of the main winch, so that the first solenoid valve 13 is energized, the auxiliary pump 181 and the auxiliary valve 182 increase the output pressure and output flow, the oil in the first oil circuit 111 is not allowed to flow to the second oil circuit 112, and the input current of the inverse proportional solenoid valve 14 is set to the second current value, the second current value is less than the first current value, the pressure of the overflow valve 12 becomes higher, and the pressurized winch outputs the lifting force to meet the load demand. At the same time, through the speed matching calculation, the target value of the main winch system pump displacement output is obtained, so that the lifting speed of the main winch is consistent with that of the pressurized winch. The calculation process is as follows: Speed ​​of pressure winch v 1 , n 1 is the current engine speed, V 1 is the maximum displacement of the auxiliary pump (181), and the speed ratio of the pressure winch reducer is i 1 , the diameter of the pressure winch drum is d 1， Speed ​​of main winch v 2 , V 2 is the displacement of the main winch system pump that needs to be controlled, and the speed ratio of the main winch reducer is i 2 , the diameter of the main winch drum is d 2， Speed ​​of main winch v 2 ; v 1 =j(n 1 ,V 1 ,i 1 ,d 1); v 2 =j(n 1 ,V 2 ,i 2 ,d 2 ); To make v 1 = v 2 , so we can get: V 2 =k(n 1 ,V 1 ,i 1 ,d 1, i 2 ,d 2 ) Then, the input current of the main winch system pump during the CFA method is obtained through the current-displacement curve.

[0032] The hydraulic control system of the pressurized winch of the rotary drilling rig of the present invention is additionally provided with a first solenoid valve 13, a first non-return valve 151 and an inverse proportional solenoid valve 14 between the first oil circuit 111, and the inverse proportional solenoid valve 14 is respectively arranged in parallel with the solenoid valve and the first non-return valve 151. When the load is small or the main winch can meet the lifting force requirement, the first solenoid valve 13 is energized, and the pressurized winch moves synchronously with the main winch to avoid the phenomenon of air suction in the motor of the main winch, and the pressurized winch will not have the problem of reverse dragging the main winch. When the load exceeds the lifting force of the main winch, the first solenoid valve 13 is energized, and the input current of the inverse proportional solenoid valve 14 is set to the second current value (the second current value is 2mA), so that the pressurized winch outputs the lifting force, and the main winch and the pressurized winch are lifted synchronously to meet the load requirement and meet the requirements of multi-working conditions such as lifting drill rods or lifting power heads of rotary drilling rigs.

[0033] The above are only specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily thought of by a person skilled in the art within the technical scope disclosed by the present invention should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the attached claims.

Claims

1. A hydraulic control system for a rotary drilling rig pressurized winch, characterized in that: The invention comprises a balancing valve group, wherein the balancing valve group comprises a first oil circuit (111), a second oil circuit (112), a relief valve (12), a first solenoid valve (13), an inverse proportional solenoid valve (14) and a first non-return valve (151); the first oil circuit (111) and the second oil circuit (112) are respectively connected to a first oil port and a second oil port of a pressurized hoisting motor; the relief valve (12), the first solenoid valve (13) and the inverse proportional solenoid valve (14) are respectively connected between the first oil circuit (111) and the second oil circuit (112); the relief valve (12), the first solenoid valve (13) and the inverse proportional solenoid valve (14) are respectively arranged in parallel; the first non-return valve (151) and the first solenoid valve (151) are respectively connected to the first oil circuit (111) and the second oil circuit (112); The valves (13) are arranged in series, the first one-way valve (151) allows oil to flow from the second oil circuit (112) to the first oil circuit (111), when the load is such that the main winch can be lifted alone, the first solenoid valve (13) is energized, the initial current of the inverse proportional solenoid valve (14) is the first current value, the pressurized winch follows the main winch to prevent the motor from sucking air, when the load exceeds the maximum lifting force of the main winch, the input current of the inverse proportional solenoid valve (14) is reduced, the pressure of the second oil circuit (112) is increased, and at the same time, through speed matching calculation, the flow of the main winch system is controlled to make the speed of the main winch equal to the speed of the pressurized winch, so that the pressurized winch can cooperate with the main winch to lift together.

2. The hydraulic control system for the pressurized winch of the rotary drilling rig according to claim 1, characterized in that: The balancing valve assembly further comprises a third one-way valve (153), wherein the third one-way valve (153) is connected in series with the inverse proportional solenoid valve (14), and the third one-way valve (153) allows the oil to flow from the first oil circuit (111) into the second oil circuit (112), but does not allow the oil to flow from the second oil circuit (112) into the first oil circuit (111).

3. The hydraulic control system for the pressurized winch of the rotary drilling rig according to claim 2, characterized in that: The hydraulic control system of the rotary drilling rig pressurized winch further comprises a first shuttle valve (163), the first shuttle valve (163) being connected to the third oil circuit (113), and the first shuttle valve (163) being arranged between the pressurized unlocking valve (162) and the brake (21).

4. The hydraulic control system for the pressurized winch of the rotary drilling rig according to claim 1, characterized in that: The rotary drilling rig further comprises a pressure sensor, and the pressure sensor is used to detect the pressure of the main hoisting motor.

5. The hydraulic control system for the pressurized winch of the rotary drilling rig according to claim 4, characterized in that: The rotary drilling rig further comprises a rotation speed sensor, and the rotation speed sensor is used to detect the rotation speed of the main hoisting motor.

6. The hydraulic control system for the pressurized winch of the rotary drilling rig according to claim 5, characterized in that: The rotary drilling rig is provided with a control system, wherein the pressure sensor, the rotation speed sensor, the first solenoid valve (13), and the inverse proportional solenoid valve (14) are respectively electrically connected to the control system, and the control system analyzes data from the pressure sensor and determines the relationship between the load and the lifting force of the main winch.

7. A control method for a hydraulic control system of a pressurized winch of a rotary drilling rig according to any one of claims 1 to 6, characterized in that: The control method comprises: Unlocking the brake (21); The pressure sensor detects the pressure of the main winch motor, and the control system determines the relationship between the load and the lifting force of the main winch; When the load is less than the maximum lifting force of the main winch, the first solenoid valve (13) is energized, and the oil in the second oil circuit (112) is allowed to flow to the first oil circuit (111), so that the main winch will not be dragged back when the pressurized winch releases the rope; to prevent air suction, the input current of the inverse proportional solenoid valve (14) is set to a first current value, so that the auxiliary pump (181) supplies oil of a first flow rate and pressure to the first oil circuit (111), and at this time, the speed of the main winch is faster than that of the pressurized winch, and the pressurized winch follows the action of the main winch to ensure synchronization; The load is judged by a pressure sensor and a speed sensor installed on the main winch motor. The judgment condition is: if the pressure value p on the main winch motor is ≥ 320 bar and the speed n of the speed sensor is ≤ 0.1 rpm, it is judged that the load exceeds the maximum lifting force of the main winch, the first solenoid valve (13) is energized, the auxiliary pump (181) and the auxiliary valve (182) increase the output pressure and output flow, the oil in the first oil circuit (111) is not allowed to flow to the second oil circuit (112), and the input current of the inverse proportional solenoid valve (14) is set to a second current value, the pressure of the overflow valve (12) is increased, and the pressurized winch outputs a lifting force to meet the load demand. At the same time, through speed matching calculation, the target value of the main winch system pump displacement output is obtained, so that the lifting speed of the main winch is consistent with that of the pressurized winch. The calculation process is as follows: The speed of the pressure winch is v1, n1 is the current engine speed, V1 is the maximum displacement of the auxiliary pump (181), the speed ratio of the pressure winch reducer is i1, and the diameter of the pressure winch drum is d 1， The speed of the main winch is v2, where V2 is the displacement of the main winch system pump that needs to be controlled, the speed ratio of the main winch reducer is i2, and the diameter of the main winch drum is d 2， The speed of the main winch v2; v1=j(n1,V1,i1,d1); v2=j(n1,V2,i2,d2); In order to make v1= v2, we can get: <h2 style=";text-align:left;direction:ltr">V2=k(n1,V1,i1,d<h2 style=";text-align:left;direction:ltr"> 1, <h2 style=";text-align:left;direction:ltr"> i2,d2) Then, the input current of the main winch system pump during the CFA method is obtained through the current-displacement curve.

8. The control method for the hydraulic control system of the rotary drilling rig pressurized winch according to claim 7, characterized in that: The hydraulic control system of the pressurized winch of the rotary drilling rig further comprises a pilot pump (161) and a pressurized unlocking valve (162). The pilot pump (161) is connected to the pressurized unlocking valve (162). The pressurized unlocking valve (162) is connected to the brake (21) through a third oil circuit (113). The brake (21) is used to brake the power head. When the main winch can meet the lifting force requirement alone, the first solenoid valve (13) is energized, the pressurized winch follows the main winch, and the auxiliary pump (181) outputs oil with a flow rate of less than 50 L / min and a pressure of less than 35 bar to the B port of the balancing valve group. The oil pressure is less than the inlet pressure of the pressure reducing valve (173), resulting in no oil entering the brake oil port, and the brake (21) cannot be unlocked. The pressurized unlocking valve (162) is energized to enable the pilot pump (161) to output oil to the brake (21), so that the brake (21) is unlocked.

9. The control method for the hydraulic control system of the rotary drilling rig pressurized winch according to claim 8, characterized in that: When the pressure of the pressurized winch oil circuit (111) increases and the pressure output at the Br port reaches the maximum value, the oil pressure on the left side of the shuttle valve (163) is equal to the oil pressure on the right side, which can still ensure that the oil in the solenoid valve (162) and the Br port merges through the shuttle valve (163) and is then delivered to the brake (21) through the third oil circuit (113).

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