Hydraulic control system and control method of pressurized winch for rotary drilling rig

Abstract

This invention provides a hydraulic control system and control method for a pressurized winch of a rotary drilling rig. The hydraulic control system for the pressurized winch of the rotary drilling rig includes a first oil circuit, a second oil circuit, an overflow valve, a first solenoid valve, an inverse proportional solenoid valve, and a first check valve. The first oil circuit and the second oil circuit are respectively connected to the first oil port and the second oil port of the pressurized winch motor. The overflow valve, the first solenoid valve, and the inverse proportional solenoid valve are respectively connected between the first oil circuit and the second oil circuit. The overflow valve, the first solenoid valve, and the inverse proportional solenoid valve are arranged in parallel. When the first solenoid valve is energized, the initial current of the inverse proportional solenoid valve is a first current value. When the load exceeds the lifting force of the main winch, the input current of the inverse proportional solenoid valve is reduced, thereby increasing the system pressure. At the same time, through speed matching calculation, the flow output of the main winch system is controlled so that the speed of the main winch is as close as possible to that of the pressurized winch, ensuring that the pressurized winch can lift synchronously with the main winch. The hydraulic control system of the rotary drilling rig pressurized winch of the present invention enables the pressurized winch and the main winch to be synchronized, while preventing the pressurized winch motor from sucking in air, and meeting the multi-condition requirements of the rotary drilling rig.

Description

Technical Field

[0001] This invention relates to the field of basic construction technology, and in particular to a hydraulic control system and control method for a rotary drilling rig with pressurized winch. Background Technology

[0002] The main function of the balance valve in a traditional pressure winch is to return to the neutral position when the rotary drilling rig stops pressurizing, thus maintaining pressure and keeping the power head in its current position. In the long auger drilling method (CFA method), both the main winch pulley block and the pressure winch pulley block are mounted on the power head. The main winch motor and the pressure winch motor simultaneously output torque, causing the main winch wire rope and the pressure winch wire rope to lift the power head together. When the load can be lifted by the main winch alone, the main winch drives the power head upward, and the power head's carriage rises rapidly. However, the existing balance valve assembly lacks a follow-up function. When the lifting speed of the main winch exceeds the lifting speed of the pressure winch, the pressure winch becomes a load, causing energy loss and structural damage. When the load is large and the main winch alone cannot lift it, the pressure in the existing pressure winch system relies on manual adjustment of the overflow valve, which is inconvenient to control, has poor synchronization, and unstable speed. Summary of the Invention

[0003] In view of this, the purpose of the present invention is to provide a hydraulic control system for a rotary drilling rig with a pressure winch. The balance valve group enables the pressure winch to be synchronized with the main winch, while preventing the pressure winch motor from sucking in air, and meeting the multi-condition requirements of the rotary drilling rig.

[0004] This invention provides a hydraulic control system for a pressurized winch of a rotary drilling rig, including a balance valve assembly. The balance valve assembly includes a first oil circuit, a second oil circuit, a relief valve, a first solenoid valve, an inverse proportional solenoid valve, and a first check valve. The first oil circuit and the second oil circuit are respectively connected to a first oil port and a second oil port of the pressurized winch motor. 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. The relief valve, the first solenoid valve, and the inverse proportional solenoid valve are arranged in parallel. The first check valve is connected to the first... A series of solenoid valves are connected. The first check valve allows oil to flow from the second oil circuit to the first oil circuit. When the first solenoid valve is energized, the initial current of the inverse proportional solenoid valve is the 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, and the pressure in the second oil circuit increases. At the same time, through speed matching calculation, the flow rate of the main winch system is controlled so that the speed of the main winch is equal to the speed of the pressurized winch, so that the pressurized winch can work together with the main winch to lift.

[0005] In one embodiment, the balance valve assembly further includes a third check valve connected in series with the inverse proportional solenoid valve. The third check valve allows the oil to flow from the first oil passage into the second oil passage, but does not allow the oil to flow from the second oil passage into the first oil passage.

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

[0007] In one embodiment, the rotary drilling rig further includes a pressure sensor for detecting the pressure of the main winch motor.

[0008] In one embodiment, the rotary drilling rig further includes a speed sensor for detecting the speed of the main winch motor.

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

[0010] This invention also relates to a control method for a hydraulic control system of a pressurized winch for a rotary drilling rig, the control method comprising: unlocking the brake; detecting the pressure of the main winch motor via a pressure sensor, and determining 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, energizing the first solenoid valve, allowing the oil in the second oil circuit to flow to the first oil circuit, and preventing the pressurized winch from pulling the main winch back when releasing the rope; to prevent cavitation, setting the input current of the inverse proportional solenoid valve to a first current value, so that the auxiliary pump supplies oil to the first oil circuit with a first flow rate and pressure, at which time the main winch speed is faster than the pressurized winch, and the pressurized winch follows the main winch to ensure synchronization; by installing on The pressure and speed sensors on the main winch motor determine the load based on the following conditions: 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, then the load exceeds the maximum lifting force of the main winch. This energizes the first solenoid valve, increasing the output pressure and flow rate of the auxiliary pump and auxiliary valve. Oil in the first oil circuit is not allowed to flow into the second oil circuit. The input current of the inverse proportional solenoid valve is set to the second minimum current value, increasing the pressure of the relief valve and causing the pressurized winch to output lifting force to meet the load requirements. Simultaneously, through speed matching calculations, the target output value of the main winch system pump displacement is determined, ensuring that the lifting speed of the main winch matches that of the pressurized winch. The calculation process is as follows:

[0011] 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 pump in the main winch system 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 hoist is v2;

[0012] v1=j(n1,V1,i1,d1);

[0013] v2=j(n1,V2,i2,d2);

[0014] To make v1 = v2, we can conclude that:

[0015] V2=k(n1,V1,i1,d 1, i2,d2)

[0016] Then, by using the current displacement curve, the input current of the main hoisting system pump during the CFA method is obtained.

[0017] In one embodiment, the hydraulic control system of the rotary drilling rig's pressurized winch further includes a pilot pump and a pressurized unlocking valve. The pilot pump is connected to the pressurized unlocking valve, which is connected to the brake via a third oil circuit. The brake is used to brake the power head. When the main winch can meet the lifting force requirement on its own, the solenoid valve is energized, and the pressurized winch follows the main winch's movement. The auxiliary pump outputs oil with a flow rate of less than 50 L / min and a pressure of less than 35 bar to port B of the balance valve assembly. The oil pressure is less than the inlet pressure of the pressure reducing valve, resulting in no oil entering the brake port. The oil pressure at the brake port cannot unlock the brake. The pressurized unlocking valve is energized, causing the pilot pump to output oil to the brake, thereby unlocking the brake.

[0018] In one embodiment, when the pressure of the pressurized winch oil circuit increases and the pressure output at port Br reaches its maximum value, the oil pressure on the left side of the shuttle valve is equal to the oil pressure on both the right and left sides, which can still ensure that the oil from the solenoid valve and port Br merges through the shuttle valve and is then delivered to the brake through the third oil circuit.

[0019] The hydraulic control system of the rotary drilling rig's pressurized winch of this invention adds a first solenoid valve, a first check valve, and an inverse proportional solenoid valve between the first oil circuit. The inverse proportional solenoid valve is arranged in parallel with the solenoid valve and the first check valve. When the load is small or the main winch can meet the lifting force requirement, the first solenoid valve is energized. At this time, the pressurized winch moves synchronously with the main winch, avoiding the phenomenon of the main winch motor sucking in air and preventing the pressurized winch from 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 lifting force. At the same time, through speed matching calculation, the flow rate of the main winch system is reduced to make the speed of the main winch and the pressurized winch equal, ensuring that the main winch and the pressurized winch lift synchronously to meet the load requirements and meet the needs of rotary drilling rigs in multiple working conditions such as lifting drill rods or lifting power heads. Attached Figure Description

[0020] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a hydraulic schematic diagram of the hydraulic control system of the rotary drilling rig pressurized winch of the present invention.

[0022] Explanation of reference numerals: First oil circuit - 111; Second oil circuit - 112; Third oil circuit - 113; Relief valve - 12; First solenoid valve - 13; Inverse proportional solenoid valve - 14; First check valve - 151; Third check 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.

[0023] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0024] The specific embodiments of the present invention will now be described in detail with reference to the accompanying drawings. Obviously, the described embodiments are merely some, not all, of the embodiments of the present invention. Based on the description of the present invention, all other embodiments obtained by those skilled in the art without inventive effort are within the scope of protection of the present invention.

[0025] In the description of this invention, unless otherwise explicitly specified and limited, the terms "set," "install," "connect," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms according to the specific circumstances.

[0026] The terms “upper,” “lower,” “left,” “right,” “front,” “back,” “top,” “bottom,” “inner,” and “outer,” etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship commonly used when the product of the invention is in use. They are only for the convenience of description and simplification, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the present invention.

[0027] The terms “first,” “second,” “third,” etc., are used merely to distinguish elements with similar properties, not to indicate or imply relative importance or a specific order.

[0028] The terms “include,” “comprising,” or any other variation thereof are intended to cover non-exclusive inclusion, which includes not only the elements listed but also other elements not expressly listed.

[0029] like Figure 1As shown, the hydraulic control system of the rotary drilling rig's pressurized winch includes a balance valve assembly. The balance valve assembly includes a first oil circuit 111, a second oil circuit 112, an overflow valve 12, a first solenoid valve 13, a reverse proportional solenoid valve 14, and a first check valve 151. The first oil circuit 111 and the second oil circuit 112 are respectively connected to the first and second oil ports of the pressurized winch motor. The first oil port is the forward port, and the second oil port is the reverse port. Therefore, the hydraulic fluid driving the pressurized winch motor through the first oil circuit 111 or the second oil circuit 112 can cause the pressurized winch motor to rotate forward or reverse. The overflow valve 12, the first solenoid valve 13, and the reverse proportional solenoid valve 14 are respectively connected to the first oil circuit 111 and the second oil circuit 151. Between oil circuits 112, the first solenoid valve 13 is a switching valve that controls the connection and disconnection 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 arranged in parallel. The first check valve 151 is connected in series with the first solenoid valve 13, allowing oil to flow from the second oil circuit 112 to the first oil circuit 111. The hydraulic control system of the rotary drilling rig's pressurized winch also includes a third check valve 153, which is connected in series with the inverse proportional solenoid valve 14. The input current of the inverse proportional solenoid valve 14 is 0mA~20mA, corresponding to a pressure of 350bar~35bar, preferably 350bar. The current values ​​are 1 bar, 320 bar, or 35 bar, etc.; where 20mA is the first current value, 2mA is the second current value, and the third check valve 153 allows oil to flow from the first oil passage 111 into the second oil passage 112, but does not allow oil to flow from the second oil passage 112 into the first oil passage 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. 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 and the main winch lift together. Therefore, the first check valve 151 and the third check valve 153 ensure that the first solenoid valve 13 and the inverse proportional solenoid valve 14 do not affect the use of non-CFA construction methods, meeting the needs of multi-method construction. In this embodiment, the pressure is at its maximum when the input current of the inverse proportional solenoid valve 14 is 0. As the input current increases, the pressure decreases proportionally. Therefore, when the CFA condition is not used, the input current of the inverse proportional solenoid valve 14 is 0. When the load is less than or equal to the main hoisting force, the input current of the inverse proportional solenoid valve 14 is 20mA. When the load exceeds the main hoisting force, the input current of the inverse proportional solenoid valve 14 is 2mA.

[0030] When the load is small or the main winch can meet the lifting force requirements, the first solenoid valve 13 is energized, allowing the oil in the second oil circuit 112 to flow to the first oil circuit 111. Due to the action of the first check 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. The input current of the inverse proportional solenoid valve 14 is set to the first current value, so that the auxiliary pump 181 supplies the first oil circuit 111 with the first flow rate (the first flow rate refers to a flow rate of less than 50L / min), to prevent the motor of the pressurized winch from sucking in air, causing cavitation and affecting the reliability of the motor.

[0031] When the load exceeds the lifting force of the main winch, the first solenoid valve 13 is energized, allowing the oil in the second oil circuit 112 to flow to the first oil circuit 111. The pressure winch releases the rope, and the pressure winch will not drag the main winch backward. 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 lowest current value (2mA). The pressure in the second oil circuit 112 increases. At the same time, through speed matching calculation, the flow rate of the main winch system is controlled so that the speed of the main winch is equal to the speed of the pressure winch, so that the pressure winch can work together with the main winch to lift.

[0032] Preferably, the hydraulic control system of the rotary drilling rig's pressurized winch also includes a pilot pump 161 and a pressurized unlocking valve 162. The pilot pump 161 is connected to the pressurized unlocking valve 162, which is connected to the brake 21 via a third oil circuit 113. The brake 21 is used to brake the power head. The pressurized winch uses a wire rope to control the lifting and lowering of the power head for braking. When the main winch can meet the lifting force requirement on its own, the first solenoid valve 13 is energized, and the pressurized winch follows the main winch's movement. 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 port A of the balance valve assembly. At port B, the hydraulic pressure is lower than the inlet pressure of pressure reducing valve 173, resulting in no hydraulic fluid entering the brake port and preventing brake 21 from unlocking. The CFA-manufacturing pressure unlocking valve 162 is always energized, causing pilot pump 161 to output hydraulic fluid to brake 21, thus unlocking brake 21. When energized, pressure unlocking valve 162 reverses direction, connecting pilot pump 161 to the third hydraulic circuit 113. Even when the load increases and port Br outputs pressure to its maximum value, the hydraulic pressure on both sides of the first shuttle valve 163 is equal, ensuring that the hydraulic fluid from pressure unlocking valve 162 and port Br merges and is delivered to brake 21 via the third hydraulic circuit 113. Note: If the pressure at port Br does not reach its maximum, merging will not occur; in this case, the hydraulic fluid from port 162 enters the brake. In this embodiment, the hydraulic control system of the rotary drilling rig pressurized winch also includes a secondary valve 182, which is connected to the secondary pump 181. The first oil circuit 111 and the second oil circuit 112 are respectively connected to the secondary pump 181. The secondary valve 182 is used to input the oil from the secondary pump 181 into the first oil circuit 111 or the second oil circuit 112 respectively.

[0033] Preferably, the hydraulic control system of the rotary drilling rig pressurized winch also includes a first shuttle valve 163. The first shuttle valve 163 is connected to the third oil circuit 113. The first shuttle valve 163 is located between the pressurized unlocking valve 162 and the brake 21. The main function of the first shuttle valve 163 is to control the unlocking of the brake by the two oil circuits. In non-CFA operating conditions, the oil from port Br enters the brake through this valve, while in CFA operating conditions, the oil from solenoid valve 162 enters the brake through this valve.

[0034] Preferably, the rotary drilling rig also includes a pressure sensor for detecting the pressure of the main winch motor.

[0035] Preferably, the rotary drilling rig also includes a speed sensor for detecting the speed of the main winch motor.

[0036] Preferably, the rotary drilling rig is equipped with a control system. The pressure sensor, speed sensor, first solenoid valve 13 and inverse proportional solenoid valve 14 are electrically connected to the control system. The control system analyzes the data from 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 from the pressure sensor and determines whether the lifting force of the main winch can meet the load requirements on its own or whether the load exceeds the maximum lifting force of the main winch.

[0037] The present invention also relates to a control method for a hydraulic control system of a pressurized winch for a rotary drilling rig, the control method comprising:

[0038] Unlock brake 21; specifically, when the main winch can meet the lifting force requirement on its own, the 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 port A or B of the balance valve assembly. The oil pressure is less than the inlet pressure of the pressure reducing valve 173, resulting in no oil entering the brake port, and the oil pressure at the brake port cannot unlock brake 21; the pressurized unlocking valve 162 is energized to activate the pilot pump. 161 outputs oil to brake 21, unlocking brake 21. Even when the pressure in the first oil circuit 111 increases and the pressure output at port Br reaches its maximum value, the oil pressure on both sides of the first shuttle valve 163 is equal, ensuring that the oil from the pressurized unlocking valve 162 and port Br merges through the first shuttle valve 163 and is then delivered to brake 21 through the third oil circuit 113. Note: If the pressure at port Br does not reach its maximum, the oil cannot merge. In this case, the oil from the pressurized unlocking valve 162 enters brake 21.

[0039] The control system detects the pressure of the main winch motor using a 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 from the pressure sensor and determines whether the lifting force of the main winch can meet the load's requirements alone, or whether the load exceeds the lifting force of the main winch. Furthermore, the control system controls the inverse proportional solenoid valve 14 in real time according to the load's requirements, enabling the main winch and the pressurized winch to work together to meet the load's lifting force.

[0040] When the load is less than the maximum lifting force of the main winch, the first solenoid valve 13 is energized, allowing the oil in the second oil circuit 112 to flow to the first oil circuit 111, preventing the pressure winch from pulling the main winch back when releasing the rope. To prevent cavitation, the input current of the inverse proportional solenoid valve 14 is set to the first current value (20mA), so that the auxiliary pump 181 supplies the first oil circuit 111 with oil at the first flow rate and pressure (the first flow rate is less than 50L / min and the pressure is less than 35bar), preventing the motor of the pressure winch from cavitating and affecting the reliability of the motor. At this time, the speed of the main winch is faster than that of the pressure winch, and the pressure winch follows the action of the main winch to ensure synchronization.

[0041] The load is determined by pressure and speed sensors mounted on the main winch motor. The determination criteria are: 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, then the load exceeds the maximum lifting force of the main winch. This energizes the first solenoid valve 13, and the auxiliary pump 181 and auxiliary valve 182 increase the output pressure and flow rate. The oil in the first oil circuit 111 is not allowed to flow to the second oil circuit 112. The input current of the inverse proportional solenoid valve 14 is set to the second current value, which is less than the first current value. The pressure of the relief valve 12 increases, causing the pressurized winch to output lifting force to meet the load requirements. At the same time, through speed matching calculation, the target value of the pump displacement required by the main winch system 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:

[0042] 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 pump in the main winch system 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 hoist is v2;

[0043] v1=j(n1,V1,i1,d1);

[0044] v2=j(n1,V2,i2,d2);

[0045] To make v1 = v2, we can conclude that:

[0046] V2=k(n1,V1,i1,d 1, i2,d2)

[0047] Then, by using the current displacement curve, the input current of the main hoisting system pump during the CFA method is obtained.

[0048] The hydraulic control system of the rotary drilling rig's pressurized winch of the present invention adds a first solenoid valve 13, a first check valve 151, and an inverse proportional solenoid valve 14 between the first oil circuit 111. The inverse proportional solenoid valve 14 is arranged in parallel with the solenoid valve and the first check valve 151. When the load is small or the main winch can meet the lifting force requirement, the first solenoid valve 13 is energized. At this time, the pressurized winch moves synchronously with the main winch to avoid the main winch motor from sucking in air and the pressurized winch will not drag the main winch backward. 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 a second current value (the second current value is 2mA), so that the pressurized winch outputs lifting force. The main winch and the pressurized winch lift synchronously to meet the load requirement and meet the needs of rotary drilling rigs in multiple working conditions such as lifting drill rods or lifting power heads.

[0049] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the appended claims.

Claims

1. A hydraulic control system for a pressure winch of a rotary drilling rig, characterized in that, The system includes a balance valve assembly comprising a first oil passage (111), a second oil passage (112), an overflow valve (12), a first solenoid valve (13), an inverse proportional solenoid valve (14), and a first check valve (151). The first oil passage (111) and the second oil passage (112) are respectively connected to the first oil port and the second oil port of the pressurized winch motor. The overflow valve (12), the first solenoid valve (13), and the inverse proportional solenoid valve (14) are respectively connected between the first oil passage (111) and the second oil passage (112). The overflow valve (12), the first solenoid valve (13), and the inverse proportional solenoid valve (14) are arranged in parallel. The first check valve (151) is connected in series with the first solenoid valve (13). The first check valve (151) allows oil to flow from the second oil passage (112) to the first oil passage (111). The balance valve group also includes a third check valve (153), which is connected in series with the inverse proportional solenoid valve (14). The third check valve (153) allows the oil to flow from the first oil passage (111) into the second oil passage (112), but does not allow the oil to flow from the second oil passage (112) into the first oil passage (111). When the load can be lifted independently by the main winch, the first solenoid valve (13) is energized, and 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 in 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, and the pressure of the second oil circuit (112) increases. At the same time, the flow rate 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 work together with the main winch to lift.

2. The hydraulic control system for the pressurized winch of the rotary drilling rig as described in claim 1, characterized in that, The hydraulic control system of the rotary drilling rig pressurized winch also includes a pressurized unlocking valve (162) and a first shuttle valve (163). The pressurized unlocking valve (162) is connected to the brake (21) through a third oil circuit (113). The first shuttle valve (163) is connected to the third oil circuit (113) and is located between the pressurized unlocking valve (162) and the brake (21).

3. The hydraulic control system for the pressurized winch of the rotary drilling rig as described in claim 1, characterized in that, The rotary drilling rig also includes a pressure sensor for detecting the pressure of the main winch motor.

4. The hydraulic control system for the pressurized winch of the rotary drilling rig as described in claim 3, characterized in that, The rotary drilling rig also includes a speed sensor, which is used to detect the speed of the main winch motor.

5. The hydraulic control system for the pressurized winch of the rotary drilling rig as described in claim 4, characterized in that, The rotary drilling rig is equipped with a control system. 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. The control system analyzes the data from the pressure sensor and determines the relationship between the load and the lifting force of the main winch.

6. A control method for a hydraulic control system of a pressurized winch for a rotary drilling rig according to any one of claims 1 to 5, characterized in that, The control method includes: Unlock 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). The release rope of the pressurized winch will not drag the main winch back. To prevent cavitation, the input current of the inverse proportional solenoid valve (14) is set to the first current value, so that the auxiliary pump (181) supplies the first oil circuit (111) with the first flow rate and pressure of oil. 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 greater than or equal to 320 bar, and the speed n of the speed sensor is less than or equal to 0.1 rpm. Then it is determined that the load exceeds the maximum lifting force of the main winch. The first solenoid valve (13) is energized, and the auxiliary pump (181) and 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). The input current of the inverse proportional solenoid valve (14) is set to the second current value. The pressure of the overflow valve (12) increases, so that the pressure winch outputs lifting force to meet the load demand. At the same time, the target value of the pump displacement of the main winch system is obtained through speed matching calculation, so that the lifting speed of the main winch is consistent with that of the pressure 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 pump in the main winch system 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 hoist is v2; v1=j(n1,V1,i1,d1); v2=j(n1,V2,i2,d2); To make v1 = v2, we can conclude that: V2=k(n1,V1,i1,d 1, i2,d2) Then, by using the current displacement curve, the input current of the main hoisting system pump during the CFA method is obtained.

7. The control method for the hydraulic control system of the pressurized winch of a rotary drilling rig as described in claim 6, characterized in that, The hydraulic control system of the rotary drilling rig pressurized winch 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 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 on its own, the first solenoid valve (13) is energized, and the pressurized winch follows the main winch. 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 port B of the balance valve group. The oil pressure is less than the inlet pressure of the pressure reducing valve (173), resulting in no oil entering the brake port and the brake (21) cannot be unlocked. The pressurized unlocking valve (162) is energized so that the pilot pump (161) outputs oil to the brake (21), thereby unlocking the brake (21).

8. The control method for the hydraulic control system of the pressurized winch of a rotary drilling rig as described in claim 7, characterized in that, The hydraulic control system of the rotary drilling rig pressurized winch also includes a first shuttle valve (163). When the pressure of the first oil circuit (111) increases and the pressure output of the Br port reaches the maximum value, the oil pressure on the left side of the first shuttle valve (163) is equal to the oil pressure on the right side. This ensures that the oil from the pressurized unlocking valve (162) and the Br port is combined through the shuttle valve (163) and then transported to the brake (21) through the third oil circuit (113).

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