A super-high pressure and large flow two-way cartridge servo valve

Abstract

This invention discloses an ultra-high pressure, high-flow two-way cartridge servo valve, belonging to the field of hydraulic valve technology. It mainly consists of a valve body, valve sleeve, main valve core, pilot servo valve, and a rotary isolation drive assembly. The rotary isolation drive assembly includes a rotating sleeve, which, by switching between a locked and unlocked position, can cut off the connection between each oil port of the pilot servo valve and the relevant flow path of the main valve, enabling online pressure replacement of the pilot servo valve. Simultaneously, when the rotating sleeve rotates, it drives the valve sleeve to generate axial displacement through a mechanical transmission structure, forming a preset bypass valve port with the main valve core, allowing the system to enter a degraded operation mode in the event of pilot failure. This invention solves the technical problems of existing servo valves having only one failure condition and requiring complete machine shutdown for maintenance, providing reliable isolation and helping to reduce unplanned downtime costs.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic valve technology, and particularly relates to an ultra-high pressure, high flow rate two-way cartridge servo valve. Background Technology

[0002] Two-way cartridge servo valves are widely used in hydraulic servo control systems of metallurgical rolling mills, construction machinery, injection molding equipment, and continuous chemical production plants due to their advantages such as large flow capacity, low pressure drop, fast response, and easy high integration within the valve block. In such systems, two-way cartridge servo valves typically adopt a "pilot valve + main cartridge valve core" structure. The pilot pressure controls the pressure in the main valve control chamber, thereby regulating the opening of the main valve core and the pressure or flow of the actuator.

[0003] However, in existing technologies, to ensure system safety in the event of electrical signal or control air source failure, a single, fixed failure condition is generally achieved by relying on the direction of spring return force, such as failure to close the valve or failure to open the valve. For process industrial plants with high continuity requirements, simply closing or opening the valve often means a forced interruption of production, which can easily lead to significant unplanned downtime losses. At the same time, in some industrial scenarios, the single failure mode of existing two-way cartridge servo valves is insufficient to simultaneously meet the requirements of safety and continuous operation.

[0004] On the other hand, in typical two-way cartridge servo valves, the pilot valve is often subjected to high pressure, high frequency operation, or contaminated environments, making coil burnout or valve core jamming common failures. Existing designs typically require the entire system to be shut down and depressurized before the pilot valve can be disassembled and replaced. To reduce downtime risks, some solutions employ methods such as adding a manual bypass valve or redundant pilot valve manifolds; however, these designs are complex and the operation is intricate, making it difficult to safely and quickly replace a single pilot valve online while the system is under pressure.

[0005] Therefore, there is an urgent need for a two-way cartridge servo valve structure that can improve system operational flexibility and reduce downtime losses under pilot failure or maintenance conditions. Summary of the Invention

[0006] Technical problem to be solved: The present invention provides an ultra-high pressure, high flow rate two-way cartridge servo valve, which can solve the above-mentioned problems.

[0007] Technical Solution: To achieve the above objectives, the present invention adopts the following technical solution: an ultra-high pressure, high flow rate two-way cartridge servo valve, comprising: The valve body includes a valve sleeve and a main valve core slidably disposed within the valve sleeve; the valve sleeve is axially movable within the valve body; the main valve core, the valve sleeve, and the valve body together define at least one pressure control chamber for driving the main valve core to move. A rotary isolation drive assembly includes a rotating sleeve rotatably mounted on the valve body; A pilot servo valve is mounted on the rotating sleeve, and the pilot servo valve has a pilot control port for controlling the pressure of the pressure control chamber; The valve body is provided with a control flow channel that connects to the pressure control chamber; The rotating sleeve is configured to switch between a locked position and an unlocked position: when the rotating sleeve is in the locked position, the pilot control port is connected to the control flow channel through the flow channel inside the rotating sleeve; when the rotating sleeve is in the unlocked position, the rotating sleeve rotates relative to the valve body to cut off the connection between the pilot control port and the control flow channel. A mechanical transmission structure is provided between the rotating sleeve and the valve sleeve. The mechanical transmission structure is configured to drive the valve sleeve to move axially when the rotating sleeve rotates to the unlocked position, thereby forming a bypass valve port between the main valve core and the valve sleeve.

[0008] As a preferred embodiment of the present invention, the rotary isolation drive assembly further includes a control slot block arranged coaxially with and connected to the rotary sleeve in a transmission manner; the mechanical transmission structure includes a control slot group formed on the inner circumferential wall of the control slot block, and a control pin disposed on the valve sleeve; a vertical slot is formed on the valve body along the axial direction, and the control pin passes through the vertical slot and is slidably embedded in the control slot group.

[0009] As a preferred embodiment of the present invention, the control groove group includes a spiral groove and an arc groove that are connected end to end; the plane in which the arc groove is located is perpendicular to the axis of the control groove block, and the spiral groove is inclined relative to the axis of the control groove block.

[0010] As a preferred embodiment of the present invention, it further includes a trigger unlocking component for limiting the position of the rotating sleeve; the trigger unlocking component includes an electromagnet, an unlocking plate driven by the electromagnet, a reset spring connected to the unlocking plate, and a locking member; the electromagnet is disposed at the upper end of the valve body, and the unlocking plate is slidably connected to the upper end of the valve body; a fixing groove is provided on the rotating sleeve; when the rotating sleeve is in the locked position, the locking member is confined within the fixing groove; when it is necessary to switch the rotating sleeve to the unlocked position, the electromagnet drives the unlocking plate to move, thereby releasing the locking member and causing the locking member to exit from the fixing groove.

[0011] As a preferred embodiment of the present invention, the valve body has a through hole, the unlocking plate has an unlocking groove, and the locking element is a steel ball; the return spring drives the unlocking plate to move in a direction offset from the unlocking groove and the through hole; when the rotating sleeve is in the locked position, the steel ball is at least partially located in the through hole and the fixing groove; when the unlocking plate moves to the point where the unlocking groove is aligned with the through hole, the steel ball exits the fixing groove and at least partially enters the unlocking groove; a torsion spring is connected between the rotating sleeve and the valve body.

[0012] As a preferred embodiment of the present invention, the pressure control chamber includes an upper control chamber and a lower control chamber, and the control flow channel correspondingly includes a first control flow channel and a second control flow channel; the valve body is also provided with a pilot inlet flow channel and a pilot outlet flow channel corresponding to the oil supply port and oil return port of the pilot servo valve; a flow groove is formed on the inner circumferential wall of the rotating sleeve; when the rotating sleeve is in the locked position, the flow groove is offset from the first control flow channel and the second control flow channel, and the oil supply port and the oil return port are respectively connected to the pilot inlet flow channel and the pilot outlet flow channel; when the rotating sleeve is in the unlocked position, the rotating sleeve rotates relative to the valve body, cutting off the connection between the pilot control port and the first control flow channel and the second control channel, and simultaneously cutting off the connection between the oil supply port, the oil return port and the pilot inlet flow channel and the pilot outlet flow channel, while the flow groove connects the first control flow channel and the second control channel.

[0013] As a preferred embodiment of the present invention, the valve body is provided with a limiting pin, and the protruding end of the limiting pin is slidably embedded in the flow groove; when the rotating sleeve is in the unlocked position, the limiting pin abuts against the end of the flow groove.

[0014] As a preferred embodiment of the present invention, the main valve core is provided with a valve core groove along its axis, the upper end face of the valve sleeve and the valve body form a balance cavity, and the main oil inlet at the bottom of the valve sleeve is in fluid communication with the balance cavity through the valve core groove.

[0015] As a preferred embodiment of the present invention, it further includes an opening preset adjustment component; the opening preset adjustment component includes an adjustment ring sleeved on the outside of the rotating sleeve and fixedly connected to the control slot block, and an adjustment worm gear rotatably mounted on the adjustment ring; a worm wheel is fixedly provided on the rotating sleeve, and the adjustment worm gear meshes with the worm wheel.

[0016] As a preferred embodiment of the present invention, it further includes a displacement sensor, which is vertically mounted on the top of the valve body, and its probe extends downward and is fixedly connected to the main valve core.

[0017] Compared with the prior art, the advantages of the present invention are: 1. By setting up a rotary isolation drive assembly including a rotating sleeve, when the system fails or requires maintenance, the rotating sleeve is unlocked and rotated to the unlocked position. The mechanism cuts off the fluid connection between each oil port of the pilot servo valve and the relevant flow channel of the main valve, which can realize the online pressure replacement of the pilot servo valve in the main circuit without depressurization, avoiding the loss caused by the shutdown of the entire system.

[0018] 2. Through a mechanical transmission structure (such as the cooperation between the spiral groove and the control pin), the valve sleeve can be driven to generate axial displacement while isolating the pilot servo valve failure, forming a preset bypass valve port with the main valve core, so that the system enters the degraded operation mode, maintains the basic flow circulation of the pipeline, and thus improves the problem that the failure conditions of traditional two-way cartridge servo valves are relatively simple.

[0019] 3. By setting the valve core groove and the balance chamber, a hydraulic self-balancing structure is formed. This design helps to reduce the pressure difference between the two ends of the valve sleeve caused by the high-pressure fluid, so that the valve sleeve displacement process mainly overcomes frictional resistance, thereby improving the operational reliability of the mechanical degradation protection mechanism under extreme working conditions.

[0020] 4. The trigger unlocking component has a compact structure and a clear action path, enabling rapid emergency downgrade isolation when used with a torsion spring. Furthermore, the worm gear structure allows for not only preset valve opening but also manual adjustment by operators using external tools during emergency repairs and maintenance, minimizing the impact on the main oil circuit during maintenance. Attached Figure Description

[0021] Figure 1 This is a cross-sectional view of the present invention when it is installed on the valve block; Figure 2 For the present invention Figure 1 A cross-sectional view along the AA direction; Figure 3 For the present invention Figure 1 Cross-sectional view along the BB direction; Figure 4 For the present invention Figure 1 A cross-sectional view along the CC direction; Figure 5 For the present invention Figure 1 A cross-sectional view along the DD direction; Figure 6 For the present invention Figure 2 A cross-sectional view along the EE direction; Figure 7 For the present invention Figure 2 A cross-sectional view along the FF direction; Figure 8 This is a three-dimensional view of the control slot block of the present invention.

[0022] Reference numerals: Valve body 1, Pilot inlet channel 2, Pilot outlet channel 3, First control channel 4, Second control channel 5, Upper control chamber 6, Lower control chamber 7, Vertical groove 8, Limit pin 9, Main valve core 10, Shoulder 11, Valve core groove 12, Valve sleeve 13, Balance chamber 14, Control pin 15, Rotating sleeve 16, Flow groove 17, Fixed groove 18, Worm gear 19, Adjusting ring 20, Worm 21, Torsion spring 22, Control groove block 23, Spiral groove 24, Arc groove 25, Main spring 26, Unlocking plate 27, Unlocking groove 28, Steel ball 29, Through hole 30, Pilot servo valve 31, Displacement sensor 32, Electromagnet 33, Return spring 34. Detailed Implementation

[0023] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings, but the present invention can be implemented in many different ways as defined and covered by the claims.

[0024] See Figures 1 to 8 An ultra-high pressure, high-flow two-way cartridge servo valve is disclosed in this embodiment. The valve body 1 contains a valve sleeve 13 and a main valve core 10 slidably disposed within the valve sleeve 13. The valve sleeve 13 is axially movable within the valve body 1. The main valve core 10, the valve sleeve 13, and the valve body 1 together define at least one pressure control chamber for driving the main valve core 10. Specifically, in this embodiment, the main valve core 10 has a shoulder 11 that divides the internal space of the valve body 1, thereby forming an upper control chamber 6 and a lower control chamber 7, serving as the pressure control chamber for driving the main valve core 10. A main spring 26 is also provided between the upper end of the main valve core 10 and the valve body 1.

[0025] The rotary isolation drive assembly includes a rotating sleeve 16 rotatably mounted on the valve body 1.

[0026] The pilot servo valve 31 is mounted on the rotating sleeve 16. In this embodiment, the pilot servo valve 31 includes an oil supply port, an oil return port, and a pilot control port for controlling the pressure of the pressure control chamber. The pilot control port in this embodiment includes port A and port B, which are respectively connected to the first control flow channel 4 and the second control flow channel 5. The oil supply port and the oil return port are respectively connected to the pilot inlet flow channel 2 and the pilot outlet flow channel 3. The valve body 1 has a control flow channel connecting to the pressure control chamber.

[0027] The rotating sleeve 16 is configured to switch between a locked position and an unlocked position: when the rotating sleeve 16 is in the locked position, the pilot control port is connected to the control flow channel through the flow channel inside the rotating sleeve 16, and the oil supply port and oil return port are connected to the pilot inlet flow channel 2 and the pilot outlet flow channel 3, respectively; when the rotating sleeve 16 is in the unlocked position, the rotating sleeve 16 rotates relative to the valve body 1 to cut off the connection between the pilot control port and the control flow channel, and simultaneously cut off the connection between the oil supply port, oil return port and the pilot inlet flow channel 2 and the pilot outlet flow channel 3. At the same time, a mechanical transmission structure is provided between the rotating sleeve 16 and the valve sleeve 13. When the rotating sleeve 16 rotates to the unlocked position, it drives the valve sleeve 13 to move axially, thereby forming a bypass valve port between the main valve core 10 and the valve sleeve 13.

[0028] In this embodiment, the rotary isolation drive assembly not only isolates and cuts off the flow of each port of the pilot servo valve, preventing the oil in the main oil circuit from leaking out through the pilot servo valve, but also allows for online pressure replacement of the pilot servo valve 31. At the same time, it drives the valve sleeve 13 to move through the transmission mechanism, forming a preset bypass valve port with the main valve core 10, enabling the system to enter a degraded operation mode and maintain the basic flow circulation of the pipeline.

[0029] In this embodiment, the rotary isolation drive assembly further includes a control slot block 23 coaxially arranged and driveably connected to the rotary sleeve 16. Specifically, the mechanical transmission structure employs a configuration where the control slot group of the control slot block 23 engages with the control pin 15 on the valve sleeve 13. (See reference...) Figure 2 , Figure 7 and Figure 8 The control groove assembly is formed on the inner circumferential wall of the control groove block 23, and the control pin 15 is set on the valve sleeve 13; a vertical groove 8 is formed on the valve body 1 along the axial direction, and the control pin 15 passes through the vertical groove 8 and is slidably embedded in the control groove assembly. The control groove assembly includes a spiral groove 24 and an arc groove 25 that are connected end to end; the plane where the arc groove 25 is located is perpendicular to the axis of the control groove block 23, and the spiral groove 24 is inclined relative to the axis of the control groove block 23.

[0030] In other embodiments, the mechanical transmission structure may also employ a gear and rack transmission mechanism, a cam and push rod transmission mechanism, or a screw transmission mechanism, etc. Any equivalent alternative to this invention can be used as long as the relative rotation of the rotating sleeve can be reliably converted into an axial thrust to drive the valve sleeve and open the bypass valve port.

[0031] See Figure 1 and Figure 5The invention also includes a trigger unlocking assembly for defining the position of the rotating sleeve 16. This assembly includes an electromagnet 33, an unlocking plate 27 driven by the electromagnet 33, a return spring 34 connected to the unlocking plate 27, and a steel ball 29 serving as a locking element. The electromagnet 33 is disposed at the upper end of the valve body 1, and the unlocking plate 27 is slidably connected to the upper end of the valve body 1. A through hole 30 is provided on the valve body 1, an unlocking groove 28 is provided on the unlocking plate 27, and a fixing groove 18 is provided on the rotating sleeve 16. The return spring 34 drives the unlocking plate 27 to move in a direction offset from the unlocking groove 28 and the through hole 30.

[0032] Its working logic is as follows: A torsion spring 22 in a pre-tightened state is connected between the rotating sleeve 16 and the valve body 1 to provide rotational power at the moment of unlocking. When the rotating sleeve 16 is in the locked position, the return spring 34 drives the solid part of the unlocking plate 27 to press and confine the steel ball 29 within the through hole 30 and the fixing groove 18; when it is necessary to switch the rotating sleeve 16 to the unlocking position, the electromagnet 33 is energized, driving the unlocking plate 27 to move against the elastic force of the return spring 34. When the unlocking plate 27 moves to the point where the unlocking groove 28 is aligned with the through hole 30, the space is released, and under the drive of the torsion spring 22, the rotating sleeve 16 generates a rotational tendency, squeezing the steel ball 29 out of the fixing groove 18 and at least partially entering the unlocking groove 28, thereby completing the release action.

[0033] In other embodiments, the power source for triggering the unlocking component can also be a miniature cylinder, a hydraulic push rod, or a manual mechanical pull rod to replace the electromagnet 33, and the locking component can also be replaced by a cylindrical locking pin or a chamfered wedge block.

[0034] See Figures 1 to 3 The control channels include a first control channel 4 and a second control channel 5; a flow groove 17 is provided on the inner circumferential wall of the rotating sleeve 16; the valve body 1 is provided with a pilot inlet flow channel 2 and a pilot outlet flow channel 3. When the rotating sleeve 16 is in the locked position, the flow groove 17 is offset from the first control channel 4 and the second control channel 5; when the rotating sleeve 16 is in the unlocked position, the rotating sleeve 16 rotates relative to the valve body 1, cutting off the connection between the pilot control port of the pilot servo valve 31 and the first control channel 4 and the second control channel 5, and simultaneously cutting off the connection between the oil supply port, the oil return port and the pilot inlet flow channel 2 and the pilot outlet flow channel 3, realizing the complete fluid isolation of the pilot servo valve 31; at the same time, the flow groove 17 connects the first control channel 4 and the second control channel 5. (See also...) Figure 3 The valve body 1 is provided with a limiting pin 9, and the protruding end of the limiting pin 9 is slidably embedded in the flow channel 17; when the rotating sleeve 16 is in the unlocked position, the limiting pin 9 abuts against the end of the flow channel 17.

[0035] See Figure 1 and Figure 2To reduce the resistance when the valve sleeve 13 is pressed down, the main valve core 10 has a valve core groove 12 along its axis. The upper end face of the valve sleeve 13 and the valve body 1 form a balance chamber 14. The main oil inlet at the bottom of the valve sleeve 13 is in fluid communication with the balance chamber 14 through the valve core groove 12, forming a self-balancing structure.

[0036] See Figure 1 , Figure 2 and Figure 6 The invention also includes an opening preset adjustment component. This component includes an adjusting ring 20 sleeved on the outside of the rotating sleeve 16 and fixedly connected to the control slot block 23, and an adjusting worm 21 rotatably mounted on the adjusting ring 20. A worm wheel 19 is fixedly mounted on the rotating sleeve 16, and the adjusting worm 21 meshes with the worm wheel 19. Through the worm wheel 19 and the worm 21, not only can the valve opening be preset, but also, during emergency repairs and maintenance, the operator can rotate the worm 21 to move the valve sleeve 13, adjusting the degraded valve opening. When using this invention, rotating the worm 21, due to the meshing of the worm wheel 19 and the worm 21, drives the adjusting ring 20 to rotate relative to the rotating sleeve 16, thereby driving the control slot block 23 to rotate relative to the rotating sleeve 16. This allows adjustment of the relative position of the control slot block 23 and the rotating sleeve 16. After adjustment, normal use can resume.

[0037] In other embodiments, the opening preset adjustment component may also employ a bevel gear transmission mechanism or an external stepper motor drive component. Furthermore, the displacement sensor 32 is vertically mounted on the top of the valve body 1, and its probe extends downwards and is fixedly connected to the main valve core 10 to achieve closed-loop feedback of the valve core displacement.

[0038] The working principle of this ultra-high pressure, high flow rate two-way cartridge servo valve is as follows: When the two-way cartridge servo valve is working normally, the reset spring 34 causes the unlocking plate 27 to remain in a position where the unlocking groove 28 and the through hole 30 are misaligned, so that the steel ball 29 is located in the through hole 30 and the fixing groove 18, locking the rotating sleeve 16. In this embodiment, the A port and B port of the pilot servo valve 31 are respectively connected to the first control flow channel 4 and the second control flow channel 5, and the oil supply port and the oil return port are respectively connected to the pilot inlet flow channel 2 and the pilot outlet flow channel 3. External control high-pressure oil enters the pilot servo valve 31 through the pilot inlet flow channel 2. By switching the pilot servo valve 31, the oil pressure in the upper control chamber 6 and the lower control chamber 7 is changed, driving the main valve core 10 to move against the main spring 26 to the required position to open the valve port. The displacement sensor 32 monitors the position of the main valve core in real time to realize closed-loop control.

[0039] When the pilot servo valve 31 experiences control failure such as coil burnout or valve core jamming, the control system sends a signal to energize the electromagnet 33, attracting the unlocking plate 27 to overcome the sliding of the reset spring 34. When the unlocking groove 28 aligns with the through hole 30, the rotating sleeve 16 is pushed to rotate under the action of the torsion spring 22, and the steel ball 29 exits the fixed groove 18 and enters the unlocking groove 28. The rotating sleeve 16 unlocks and rotates, cutting off the connection between all oil ports of the pilot servo valve 31 (i.e., pilot control port, oil supply port, and oil return port) and the main oil passage, and connecting the first control passage 4 and the second control passage 5 through the flow groove 17, so that the oil pressure in the upper control chamber 6 and the lower control chamber 7 tends to be balanced, and the main valve core 10 moves downward to reset under the action of the main spring 26.

[0040] As the rotating sleeve 16 rotates, it drives the control slot block 23 to rotate, causing the control pin 15 to slide within the control slot assembly. When the control pin 15 enters the spiral groove 24, it drives the valve sleeve 13 to move downwards. Since the valve core groove 12 introduces high-pressure fluid into the balance chamber 14, the valve sleeve 13 is in a pressure balance state, so its downward movement mainly overcomes frictional resistance. As the valve sleeve 13 descends, a bypass valve port is formed between the main valve core 10 and the valve sleeve 13. While isolating the faulty pilot valve, the main circuit retains a bypass flow to maintain the minimum operation of the production line, thereby achieving degraded operation.

[0041] After the pilot servo valve is replaced, the operator can overcome the torque of the torsion spring 22 to rotate the rotating sleeve 16 back to the initial position. The reset spring 34 will then cause the unlocking plate 27 to press the steel ball 29 into the fixing groove 18, and the system can resume normal operation.

[0042] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A high-pressure, high-flow-rate two-way cartridge servo valve, characterized in that, include: A valve body (1) is provided with a valve sleeve (13) and a main valve core (10) slidably disposed within the valve sleeve (13); the valve sleeve (13) is axially movable within the valve body (1); the main valve core (10), the valve sleeve (13), and the valve body (1) together define at least one pressure control chamber for driving the main valve core (10) to move; A rotary isolation drive assembly includes a rotating sleeve (16) rotatably mounted on the valve body (1). A pilot servo valve (31) is mounted on the rotating sleeve (16), and the pilot servo valve (31) has a pilot control port for controlling the pressure of the pressure control chamber; The valve body (1) is provided with a control flow channel that connects to the pressure control chamber; the rotating sleeve (16) is configured to switch between a locked position and an unlocked position: when the rotating sleeve (16) is in the locked position, the pilot control port is connected to the control flow channel through the flow channel inside the rotating sleeve (16); when the rotating sleeve (16) is in the unlocked position, the rotating sleeve (16) rotates relative to the valve body (1) to cut off the connection between the pilot control port and the control flow channel; a mechanical transmission structure is provided between the rotating sleeve (16) and the valve sleeve (13), and the mechanical transmission structure is configured to drive the valve sleeve (13) to move axially when the rotating sleeve (16) rotates to the unlocked position, thereby forming a bypass valve port between the main valve core (10) and the valve sleeve (13).

2. The ultra-high pressure, high flow rate, two-way cartridge servo valve according to claim 1, characterized in that, The rotary isolation drive assembly also includes a control slot block (23) that is coaxially arranged and connected to the rotary sleeve (16) in a transmission manner; the mechanical transmission structure includes a control slot group opened on the inner circumferential wall of the control slot block (23) and a control pin (15) set on the valve sleeve (13); a vertical slot (8) is opened on the valve body (1) along the axial direction, and the control pin (15) passes through the vertical slot (8) and is slidably embedded in the control slot group.

3. The ultra-high pressure, high flow rate, two-way cartridge servo valve according to claim 2, characterized in that, The control groove group includes a spiral groove (24) and an arc groove (25) connected end to end; the plane where the arc groove (25) is located is perpendicular to the axis of the control groove block (23), and the spiral groove (24) is inclined relative to the axis of the control groove block (23).

4. The ultra-high pressure, high flow rate, two-way cartridge servo valve according to claim 1, characterized in that, It also includes a trigger unlocking assembly for limiting the position of the rotating sleeve (16); the trigger unlocking assembly includes an electromagnet (33), an unlocking plate (27) driven by the electromagnet (33), a reset spring (34) connected to the unlocking plate (27), and a locking member; the electromagnet (33) is disposed at the upper end of the valve body (1), and the unlocking plate (27) is slidably connected to the upper end of the valve body (1); a fixing groove (18) is provided on the rotating sleeve (16); when the rotating sleeve (16) is in the locked position, the locking member is limited to the fixing groove (18); when it is necessary to switch the rotating sleeve (16) to the unlocked position, the electromagnet (33) drives the unlocking plate (27) to move to release the locking member and make the locking member exit from the fixing groove (18).

5. The ultra-high pressure, high flow rate, two-way cartridge servo valve according to claim 4, characterized in that, The valve body (1) has a through hole (30), the unlocking plate (27) has an unlocking groove (28), the locking element is a steel ball (29), and the return spring (34) drives the unlocking plate (27) to move in a direction that is offset from the unlocking groove (28) and the through hole (30). When the rotating sleeve (16) is in the locked position, the steel ball (29) is at least partially located in the through hole (30) and the fixing groove (18). When the unlocking plate (27) moves to the point where the unlocking groove (28) is aligned with the through hole (30), the steel ball (29) exits the fixing groove (18) and at least partially enters the unlocking groove (28). A torsion spring (22) is connected between the rotating sleeve (16) and the valve body (1).

6. The ultra-high pressure, high flow rate, two-way cartridge servo valve according to claim 1, characterized in that, The pressure control chamber includes an upper control chamber (6) and a lower control chamber (7), and the control flow channels correspondingly include a first control flow channel (4) and a second control flow channel (5); the valve body (1) is also provided with a pilot inlet flow channel (2) and a pilot outlet flow channel (3) corresponding to the oil supply port and oil return port of the pilot servo valve (31); a flow groove (17) is provided on the inner circumferential wall of the rotating sleeve (16); when the rotating sleeve (16) is in the locked position, the flow groove (17) is offset from the first control flow channel (4) and the second control flow channel (5), and the oil supply... The port and the return port are respectively connected to the pilot inlet flow channel (2) and the pilot outlet flow channel (3); when the rotating sleeve (16) is in the unlocked position, the rotating sleeve (16) rotates relative to the valve body (1), cutting off the connection between the pilot control port and the first control flow channel (4) and the second control flow channel (5), and simultaneously cutting off the connection between the oil supply port, the return port and the pilot inlet flow channel (2) and the pilot outlet flow channel (3), while the flow channel (17) connects the first control flow channel (4) and the second control flow channel (5).

7. The ultra-high pressure, high flow rate, two-way cartridge servo valve according to claim 6, characterized in that, The valve body (1) is provided with a limiting pin (9), and the protruding end of the limiting pin (9) is slidably embedded in the flow channel (17); when the rotating sleeve (16) is in the unlocked position, the limiting pin (9) abuts against the end of the flow channel (17).

8. The ultra-high pressure, high flow rate, two-way cartridge servo valve according to claim 1, characterized in that, The main valve core (10) has a valve core groove (12) along its axis. The upper end face of the valve sleeve (13) and the valve body (1) form a balance chamber (14). The main oil inlet at the bottom of the valve sleeve (13) is in fluid communication with the balance chamber (14) through the valve core groove (12).

9. The ultra-high pressure, high flow rate, two-way cartridge servo valve according to claim 2, characterized in that, It also includes an opening preset adjustment component; the opening preset adjustment component includes an adjustment ring (20) sleeved on the outside of the rotating sleeve (16) and fixedly connected to the control slot block (23), and an adjustment worm (21) rotatably mounted on the adjustment ring (20); a worm wheel (19) is fixedly provided on the rotating sleeve (16), and the adjustment worm (21) meshes with the worm wheel (19).

10. The ultra-high pressure, high flow rate, two-way cartridge servo valve according to claim 1, characterized in that, It also includes a displacement sensor (32), which is vertically mounted on the top of the valve body (1) and its probe extends downward and is fixedly connected to the main valve core (10).

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