Hydraulic cylinder control valve and method of operation thereof

Abstract

The application discloses a hydraulic cylinder control valve and a working method thereof, and relates to the technical field of hydraulic control, and aims at solving the problem that the power source of the reversing valve used by the hydraulic cylinder in the prior art is mostly magnetic force or manpower, the valve body can only control the flow direction of the hydraulic oil, cannot adjust the oil pressure, has poor functional performance, and cannot perform the high-precision hydraulic cylinder flow control work. The technical key points are as follows: a composite flow control mechanism is included, the composite flow control mechanism comprises a valve body and a rotor, the rotor comprises a base plate and a dumbbell-like body, the base plate is attached to the bottom surface in the valve body, a flow conveying mechanism comprises P, A, B and T ports, the P, A, B and T ports are circumferentially distributed around the valve body, and are respectively four directions of south, west, east and north, the flow control, the stepless flow adjustment and the pressure control are realized, and the multi-state accurate control of the flow direction, the flow and the pressure of the hydraulic oil is realized.

Description

Technical Field

[0001] This invention relates to the field of hydraulic control technology, specifically to a hydraulic cylinder control valve and its working method. Background Technology

[0002] Hydraulic control valves are mechanical components in hydraulic systems that control the pressure, flow rate, and direction of fluid. They drive actuators to complete predetermined actions by adjusting fluid parameters. Based on function, they are classified into pressure control valves (including relief valves, pressure reducing valves, and sequence valves), flow control valves (including throttle valves and speed control valves), and directional control valves (including check valves and directional valves). Based on structure, they can be classified into spool valves, cone valves, and ball valves. Control methods include setpoint control, proportional control, and digital control.

[0003] Currently, most hydraulic cylinders use directional valves powered by magnetism or human force. These valves can only control the flow direction of hydraulic oil and cannot regulate oil pressure. They lack functionality and cannot meet the requirements of high-precision hydraulic cylinder flow control. Summary of the Invention

[0004] The purpose of this invention is to provide a hydraulic cylinder control valve and its working method, in order to solve the problem mentioned in the background art that the power source of the current hydraulic cylinder directional valve is mostly magnetic or human force. This type of valve body can only control the flow direction of hydraulic oil and cannot regulate the oil pressure. It lacks functionality and cannot perform the high-precision hydraulic cylinder flow control work.

[0005] To achieve the above objectives, the present invention provides the following technical solution: a hydraulic cylinder control valve, comprising:

[0006] A composite flow control mechanism, comprising a valve body and a rotor, wherein the rotor comprises a chassis and a dumbbell-like body, the chassis being fitted to the bottom surface inside the valve body, and the side end face of the dumbbell-like body being fitted to the inner wall of the valve body;

[0007] The flow conveying mechanism includes a P port, an A port, a B port, and a T port, which are circumferentially distributed around the valve body in the four directions of due south, due west, due east, and due north, respectively. The dumbbell-shaped body includes a first inward-curving surface and a second inward-curving surface. The space between the inner wall of the valve body and the first inward-curving surface forms a first flow channel, and the space between the inner wall of the valve body and the second inward-curving surface forms a second flow channel.

[0008] The control system includes a magnetic block, a magnetic angle sensor, and a PLC controller. A hollow shaft is centrally located above the dumbbell-like body. A connecting shaft is connected to the upper end of the hollow shaft. The magnetic block is installed on the outside of the connecting shaft. The connecting shaft is rotatably positioned inside the magnetic angle sensor. The magnetic block and the magnetic angle sensor monitor the rotation angle, speed, and final stopping position of the connecting shaft and transmit the information to the PLC controller.

[0009] The connecting shaft is also connected to a one-way lock on its outer side. The one-way lock allows the connecting shaft to rotate counterclockwise and prevents it from rotating clockwise, thereby allowing the rotor to rotate counterclockwise and preventing it from rotating clockwise. The control system monitors the rotor's rotation angle, speed, and final stopping position. The rotation of the rotor controls the position of the first and second flow channels. The movement of the first and second flow channels controls the connection and blockage with ports P, A, B, and T, forming six control modes. The six control modes include forward flow dynamics, forward flow restriction state, reverse flow dynamics, reverse flow restriction state, first blockage state, and second blockage state.

[0010] In a preferred embodiment, the present invention can be further configured as follows: a sealing valve cover is fixedly installed above the valve body, the upper end face of the dumbbell-like body is in contact with the inner wall of the sealing valve cover, the hollow shaft passes through the sealing valve cover, and the PLC controller is fixedly installed above the sealing valve cover.

[0011] In a preferred embodiment, the present invention can be further configured as follows: a drive box is fixedly installed above the sealing valve cover; the magnetic angle sensor is fixedly installed on the inner wall of the drive box; the magnetic angle sensor is electrically connected to the PLC controller; a cover plate is fixedly installed above the drive box; a drive device is fixedly installed above the cover plate; the drive device is electrically connected to the PLC controller; and the drive device is drively connected to the connecting shaft.

[0012] In a preferred embodiment, the present invention can be further configured as follows: a plurality of ratchet teeth are provided on the inner wall of the one-way locking device; a turntable is rotatably provided inside the one-way locking device; there is a gap between the outer edge of the turntable and the ratchet teeth; the center position of the turntable is fixedly connected to the connecting shaft; a locking head is distributed around the outer circumference of the turntable; the locking head is slidably connected to the turntable; a spring is connected between the locking head and the inner wall of the turntable; the locking head engages counterclockwise with the ratchet teeth and slides clockwise.

[0013] In a preferred embodiment, the present invention can be further configured such that, during the forward flow dynamics, the first flow channel is connected to port P and port A, and the second flow channel is connected to port B and port T.

[0014] In a preferred embodiment, the present invention can be further configured such that, in the forward flow restricted state, the first flow channel connects to port P and port A, the second flow channel connects to port B and port T, and at the same time, the inflow space of port P is reduced, and the outflow space of port T is reduced.

[0015] In a preferred embodiment, the present invention can be further configured such that, during the reverse flow dynamics, the first flow channel is connected to port P and port B, and the second flow channel is connected to port A and port T.

[0016] In a preferred embodiment, the present invention can be further configured such that, in the reverse flow restriction state, the first flow channel connects to port P and port B, the second flow channel connects to port A and port T, and the inflow space of port A is reduced, while the outflow space of port B is reduced.

[0017] A method for operating a hydraulic cylinder control valve includes the following steps:

[0018] S1: P port connects to the oil pump's oil delivery end, A port connects to the hydraulic cylinder's lifting stroke oil supply end, B port connects to the hydraulic cylinder's retraction stroke oil supply end, and T port connects to the oil pump's receiving end.

[0019] S2: The connecting shaft is driven to rotate clockwise by the drive device, and the connecting shaft drives the rotor to rotate clockwise through the hollow shaft;

[0020] S3: Change the position of the first and second flow channels by rotating the rotor;

[0021] S4: When the first flow channel is connected to port P and port A, and the second flow channel is connected to port B and port T, the oil pump supplies oil through port P, and the oil in the hydraulic cylinder enters through port A and exits through port B. At this time, the working state of the hydraulic cylinder is lifting.

[0022] S5: When the first flow channel is connected to port P and port B, and the second flow channel is connected to port A and port T, the oil pump supplies oil through port P, and the hydraulic cylinder enters through port B and exits through port A. At this time, the working state of the hydraulic cylinder is recovery.

[0023] S6: When the first flow channel position and the second flow channel are in the first blocked state, there is redundancy in the internal space of the valve body at ports A and B.

[0024] S7: When the first flow channel is in position and the second flow channel is in the second blocked state, there is redundancy in the internal space of the valve body at the P port and T port.

[0025] In a preferred embodiment, the present invention can be further configured such that, in step S2, the connecting shaft can only rotate counterclockwise by means of a one-way lock, and the locking function of the one-way lock provides a limiting support force for the rotor to rotate in reverse, so that the rotor cannot rotate clockwise and can remain stable when subjected to hydraulic oil compression, thus providing a stable oil circuit delivery capability.

[0026] Compared with the prior art, the beneficial effects of the present invention are:

[0027] This invention utilizes a unique design of a composite flow control mechanism and rotor. An adjustable flow channel is formed between the dumbbell-shaped body on the rotor and the inner wall of the valve body. A non-contact detection system composed of magnetic blocks and magnetic angle sensors monitors the rotation parameters of the connecting shaft in real time. A PLC controller precisely adjusts the drive device, achieving precise closed-loop control of the rotor position with a control accuracy of ±0.5° and a system response time of less than 100ms. Furthermore, the PLC controller integrates multiple control algorithms, changing the cross-sectional area and connectivity of the flow channel as the rotor rotates. This enables flow direction control, stepless flow rate adjustment, and pressure control, achieving multi-state precise control of hydraulic oil flow direction, flow rate, and pressure. Simultaneously, it presets switching logic for six working modes, enabling one-button operation, reducing manual intervention, and lowering the difficulty of operation.

[0028] This invention achieves mechanical one-way locking through the ratchet chuck mechanism of the one-way locker. When the rotor is subjected to hydraulic shock, the chuck engages with the ratchet under the action of the spring to form a mechanical interlock, effectively preventing the rotor from accidentally reversing under pressure fluctuations. At the same time, through the unique design of the rotor and valve body, the direction of the oil circuit can be changed by one-way rotation. It can also control the oil delivery volume and pressure by one-way rotation. The structure is simple and the use is reliable.

[0029] By setting a first blocking state and a second blocking state, a redundant space is formed when the rotor rotates to a specific angle. Position locking is achieved by adjusting the oil volume, and the position holding accuracy can reach ±0.1mm, which solves the position drift problem of traditional hydraulic systems under pressure holding conditions. Attached Figure Description

[0030] Figure 1 This is an overall schematic diagram of the rotor of the present invention;

[0031] Figure 2 This is a front view of a hydraulic cylinder control valve according to the present invention;

[0032] Figure 3 This is a schematic diagram of the forward flow dynamics of the present invention;

[0033] Figure 4 This is a schematic diagram of the forward flow confinement state of the present invention;

[0034] Figure 5 This is a schematic diagram of the reverse flow dynamics of the present invention;

[0035] Figure 6 This is a schematic diagram illustrating the reverse flow restriction dynamics of the present invention;

[0036] Figure 7 This is a schematic diagram of the first blocking state of the present invention;

[0037] Figure 8 This is a schematic diagram of the second blocking state of the present invention;

[0038] Figure 9 This is a schematic diagram of the internal structure of the drive box of the present invention;

[0039] Figure 10 This is a top view of the one-way locking device of the present invention;

[0040] Figure 11 This is a schematic diagram of the overall magnetic angle sensor of the present invention.

[0041] In the diagram: 1. Valve body; 2. Sealing valve cover; 3. Drive box; 4. Cover plate; 5. Drive device; 6. PLC controller; 7. P port; 8. A port; 9. B port; 10. T port; 11. Rotor; 12. Chassis; 13. Dumbbell-shaped body; 14. First inward-curving surface; 15. Second inward-curving surface; 16. Hollow shaft; 17. Connecting shaft; 18. Magnetic block; 19. Magnetic angle sensor; 20. One-way locking device; 21. Turntable; 22. Ratchet; 23. Clamp; 24. Spring. Detailed Implementation

[0042] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0043] In the description of this application, it should be noted that the terms "upper," "lower," "inner," "outer," "top / bottom," etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, 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, and therefore should not be construed as a limitation of this application. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0044] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installed," "equipped with," "sleeved / connected," "connected," etc., should be interpreted broadly. For example, "connection" 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; it can be a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0045] Please see Figure 1-9One embodiment of the present invention provides a hydraulic cylinder control valve, comprising:

[0046] The composite flow control mechanism includes a valve body 1 and a rotor 11. The rotor 11 includes a chassis 12 and a dumbbell-shaped body 13. The chassis 12 is fitted with the bottom surface inside the valve body 1, and the side end face of the dumbbell-shaped body 13 is fitted with the inner wall of the valve body 1. The valve body 1 has a cylindrical structure with a precision-machined cavity inside. The bottom surface of the cavity is precisely fitted with the chassis 12 of the rotor 11 to ensure good sealing performance. Through precision machining and fit, the sealing performance inside the valve body 1 is ensured, preventing hydraulic oil leakage and improving the working pressure range and service life of the system.

[0047] The flow transmission mechanism includes port P7, port A8, port B9, and port T10, which are circumferentially distributed around the valve body 1, corresponding to the four directions of due south, due west, due east, and due north, respectively. Through the rotation of the rotor 11, the first and second flow channels are aligned with different oil ports, achieving the switching of hydraulic oil flow direction. This symmetrical distribution design makes the flow channel switching smoother and more precise. The symmetrical distribution of the four ports optimizes the fluid flow path, reduces pressure loss, and improves system efficiency. The dumbbell-shaped body 13 includes a first inward-curving surface 14 and a second inward-curving surface 15. The space formed by the inner wall of the valve body 1 and the first inward-curving surface 14 forms the first flow channel, and the space formed by the inner wall of the valve body 1 and the second inward-curving surface 15 forms the second flow channel. The rotor 11 consists of a chassis 12 and the dumbbell-shaped body 13. 3 is a symmetrical structure with a first inward-curving arc surface 14 and a second inward-curving arc surface 15 on both sides. The base 12 is completely fitted with the bottom surface inside the valve body 1. The side end face of the dumbbell-shaped body 13 is precisely fitted with the inner wall of the valve body 1. The precise fit between the rotor 11 and the valve body 1 not only ensures sealing but also forms a precisely controllable flow channel space, providing a structural basis for precise adjustment of flow rate and direction. By rotating the rotor 11, the relative position between the inward-curving arc surface and the inner wall of the valve body 1 is changed, thereby changing the cross-sectional area and connectivity of the flow channel. The size and shape of these two flow channels will change with the rotation of the rotor 11. By changing the cross-sectional area of ​​the flow channel, stepless adjustment of flow rate is achieved, expanding the function of the valve body 1. When the rotor 11 rotates to different positions, the flow channel space formed by the inward-curving arc surface and the inner wall of the valve body 1 will change accordingly, thereby achieving precise control of flow rate.

[0048] The control system includes a magnetic block 18, a magnetic angle sensor 19, and a PLC controller 6. A hollow shaft 16 is centrally located above the dumbbell-like body 13. A locking pin is installed inside the hollow shaft 16. A connecting shaft 17 is connected to the upper end of the hollow shaft 16. The connecting shaft 17 is inserted into the hollow shaft 16 and engages with the locking pin to achieve fixation. The magnetic block 18 is installed on the outside of the connecting shaft 17. The connecting shaft 17 is rotatably positioned inside the magnetic angle sensor 19. The magnetic block 18 and the magnetic angle sensor 19 monitor the rotation angle, speed, and final stopping position of the connecting shaft 17 and transmit this information to the PLC controller 6. The dynamic parameters are obtained by using non-contact magnetoelectric sensing technology, which avoids mechanical wear and improves the reliability and service life of the system. When the connecting shaft 17 rotates, the magnetic block 18 rotates accordingly. The magnetic angle sensor 19 detects the change in magnetic field and accurately measures the angle, angular velocity and stopping position of the rotor 11. The PLC controller 6 receives the data from the magnetic angle sensor 19 and controls the action of the drive device 5 according to the preset program, realizing the intelligent control of the hydraulic cylinder control valve. It can automatically adjust the working state of the valve body 1 according to the actual working conditions. The PLC controller 6 compares the sensor data with the set value and calculates the control signal through PID and other control algorithms to drive the motor to accurately adjust the position of the rotor 11.

[0049] A one-way lock 20 is also connected to the outside of the connecting shaft 17. The one-way lock 20 allows the connecting shaft 17 to rotate counterclockwise and prevents the connecting shaft 17 from rotating clockwise. By utilizing the characteristics of the ratchet mechanism, it can rotate freely in one direction and lock in the other direction, preventing the rotor 11 from accidentally reversing under hydraulic shock and ensuring the stability of the system operation.

[0050] One-way locker 20 is also connected to the outside of connecting shaft 17. One-way locker 20 allows connecting shaft 17 to rotate counterclockwise and prevents connecting shaft 17 from rotating clockwise, thereby allowing rotor 11 to rotate counterclockwise and preventing clockwise rotation. The control system monitors the rotation angle, speed and final stop position of rotor 11. The rotation of rotor 11 controls the position of the first flow channel and the second flow channel. The position of the first flow channel and the second flow channel controls the connection and blockage with port P7, port A8, port B9 and port T10, forming six control modes. The six control modes include forward flow dynamic, forward flow restriction state, reverse flow dynamic, reverse flow restriction state, first blockage state and second blockage state.

[0051] The PLC controller 6 adopts a modular hardware structure, with a core 32-bit ARM Cortex-M7 processor, equipped with 1 MB of SRAM and 2 MB of Flash memory. The memory connects to various functional modules via a high-speed bus. Its digital input module uses optocoupler isolation technology and includes 16 input channels specifically for receiving digital signals from the magnetic angle sensor 19. The analog input module uses a 16-bit ADC converter to process analog signals from the sensor. The digital output module is directly connected to the drive unit 5, outputting control signals to drive the motor. The PLC controller 6 processes the rotor 11 position data from the magnetic angle sensor 19 in real time, collecting angle information every 10ms. After processing by a digital filtering algorithm, the control quantity is calculated by a PID control algorithm and output to the drive unit 5. The control logic adopts a hierarchical strategy: when a large-range movement is required, it enters the coarse adjustment mode, controlling the speed to 30r / min to quickly approach the target; when approaching the target, it switches to the fine adjustment mode, reducing the speed to 5r / min to achieve precise positioning; after reaching the target, it enters the holding mode, maintaining stability through fine adjustments. The system monitors operating parameters in real time, automatically depressurizing when the pressure exceeds 25MPa, and executing an anti-jamming algorithm when rotor 11 is detected to ensure smooth switching between six control modes, achieving precise control of hydraulic oil direction, flow, and pressure.

[0052] The magnetic angle sensor 19 operates based on the magnetoresistive effect or Hall effect. A fixed sensor chip senses the change in the direction of the magnetic field generated by the magnetic block 18, which rotates synchronously with the connecting shaft 17. The magnetic field vector information is converted into sine and cosine analog electrical signals or directly calculated into digital signals. The arctangent operation is then performed via an internal circuit or an external PLC controller 6 to accurately calculate the real-time rotation angle of the connecting shaft 17. In system control, this sensor acts as a core feedback element, continuously transmitting the measured actual angle of the rotor 11 to the PLC controller 6. The controller compares this actual value with the target angles of six preset control modes to obtain the position deviation. It then performs calculations using a PID control algorithm (proportional element for fast response to deviation, integral element for eliminating steady-state error, and derivative element for suppressing overshoot and oscillation) and outputs control commands to the drive device 5. This dynamically adjusts the rotation speed and position of the rotor 11, ultimately forming a closed-loop control system capable of precise positioning, smooth movement, and state maintenance. This ensures that the hydraulic cylinder control valve can operate accurately and stably in the specified flow or blockage state under various working conditions.

[0053] Please see Figure 9A sealing valve cover 2 is fixedly installed on the top of the valve body 1. The upper end face of the dumbbell-shaped body 13 is in contact with the inner wall of the sealing valve cover 2. The hollow shaft 16 passes through the sealing valve cover 2. The PLC controller 6 is fixedly installed on the top of the sealing valve cover 2. A fixing seat for sealing is provided at the connection between the sealing valve cover 2 and the hollow shaft 16. The hollow shaft 16 is rotatably connected to the fixing seat and is sealed by an oil seal.

[0054] Please see Figure 9 A drive box 3 is fixedly installed above the sealing valve cover 2. A magnetic angle sensor 19 is fixedly installed on the inner wall of the drive box 3. The magnetic angle sensor 19 is electrically connected to the PLC controller 6. A cover plate 4 is fixedly installed above the drive box 3. A drive device 5 is fixedly installed above the cover plate 4. The drive device 5 is electrically connected to the PLC controller 6. The drive device 5 is connected to the connecting shaft 17 for transmission. The drive device 5 includes a servo motor.

[0055] Please see Figure 10 The inner wall of the one-way locking device 20 is provided with a number of ratchet teeth 22, with a total of 72 teeth. A turntable 21 is rotatably arranged inside the one-way locking device 20. There is a gap between the outer edge of the turntable 21 and the ratchet teeth 22. The center position of the turntable 21 is fixedly connected to the connecting shaft 17. There are 14 locking heads 23 distributed around the outer circumference of the turntable 21. The locking heads 23 are slidably connected to the turntable 21. A spring 24 is connected between the locking heads 23 and the inner wall of the turntable 21. The locking heads 23 and the ratchet teeth 22 engage counterclockwise and slide clockwise. The cooperation between the ratchet teeth 22 and the locking heads 23 provides a reliable one-way locking function. The spring 24 ensures continuous contact between the locking heads 23 and the ratchet teeth 22. When rotating counterclockwise, the locking heads 23 slide on the ratchet teeth 22. When attempting to rotate clockwise, the locking heads 23 engage with the ratchet teeth 22, realizing mechanical locking.

[0056] like Figure 4 As shown, in the forward flow dynamic, the first flow channel connects port P7 and port A8, and the second flow channel connects port B9 and port T10. At this time, hydraulic oil flows from port P7 into port A8, pushing the hydraulic cylinder piston to move in one direction. At the same time, the oil on the other side flows back from port B9 through port T10. The rotor 11 rotates to a specific angle, so that the first flow channel is aligned with port P7 and port A8, and the second flow channel is aligned with port B9 and port T10, realizing the normal lifting function of the hydraulic cylinder. The flow channels are fully open, and the pressure loss is small.

[0057] like Figure 5As shown, in the forward flow restriction state, the first flow channel connects port P7 and port A8, and the second flow channel connects port B9 and port T10. However, at the same time, the inlet space of port P is reduced and the outlet space of port T is reduced. When the rotor 11 rotates and reduces the inlet space of port P7, the inlet channel is partially blocked, reducing the effective flow volume. Flow restriction is achieved while keeping the flow direction unchanged. This can be used for slow operation or pressure maintenance of hydraulic cylinders.

[0058] The magnetic angle sensor 19, based on the magnetoresistive effect or Hall effect, senses the change in the direction of the magnetic field generated by the magnetic block 18, which rotates synchronously with the connecting shaft 17, through a fixed sensor chip. It converts the magnetic field vector information into sine and cosine analog electrical signals or directly calculates it into digital signals. The arctangent operation is then performed by the built-in circuit or the external PLC controller 6 to accurately calculate the real-time rotation angle of the connecting shaft 17. In the system control, this sensor, as the core feedback element, continuously transmits the measured actual angle of the rotor 11 to the PLC controller 6. The controller compares this actual value with the target angle of six preset control modes and obtains the position deviation. Then, it performs calculations through the PID control algorithm (proportional link for fast response to deviation, integral link for eliminating steady-state error, and derivative link for suppressing overshoot and oscillation) and outputs control commands to the drive device 5 to dynamically adjust the rotation speed and position of the rotor 11. Finally, a closed-loop control system is formed that can achieve precise positioning, smooth movement, and state maintenance, ensuring that the hydraulic cylinder control valve can work accurately and stably in the specified flow state or blockage state under various working conditions.

[0059] Furthermore, to achieve precise control of flow rate and pressure, the system establishes a correspondence model between the rotation angle of rotor 11 and the equivalent cross-sectional area of ​​the flow channel. Through experimental calibration or fluid simulation, the equivalent flow area curves of the first and second flow channels of rotor 11 at different angles corresponding to each oil port (P, A, B, T) are obtained. This relationship model is pre-stored in the memory of PLC controller 6 in the form of a data table or fitting function. When it is necessary to adjust the flow rate or pressure, PLC controller 6 calculates the target angle required by rotor 11 in real time based on the target flow rate value (combined with the pump's displacement characteristics) or target pressure value (feedback from the system pressure sensor) and the flow area-angle model, and compares it with the actual angle fed back by magnetic angle sensor 19 to obtain the angle deviation.

[0060] Subsequently, the PLC controller 6 performs calculations using a PID control algorithm (proportional element for fast response to deviation, integral element for eliminating steady-state error, and derivative element for suppressing overshoot and oscillation) and outputs control commands to the drive device 5. This dynamically adjusts the rotation speed and position of the rotor 11, ultimately forming a closed-loop control system capable of precise positioning, smooth motion, and state maintenance. For example, in flow regulation mode, the controller looks up the target angle from a table based on the target flow rate and drives the rotor 11 to rotate to that angle, changing the cross-sectional area of ​​the flow channel and thus achieving stepless flow regulation. In pressure control mode, the controller receives system pressure feedback and dynamically adjusts the angle of the rotor 11 through PID calculations, changing the flow channel resistance until the actual pressure matches the target pressure.

[0061] Regarding the mechanism for achieving high-precision position locking and pressure maintenance through "redundant space": When the rotor 11 rotates to the vicinity of the first or second blocking state, the outer end face of the dumbbell-like body 13 forms a closed or nearly closed micro-variable volume cavity with the inner wall of the valve body 1 and the edge of the oil port, which is the "redundant space". Through the precise micro-motion control of the drive device 5 by the PLC controller 6, the rotor 11 can be finely adjusted within a very small angle range (e.g., within ±0.5°). Each micro-adjustment step changes the volume of this redundant space. When the hydraulic cylinder needs to be locked in position, the system controls the rotor 11 to make a micro-adjustment. The change in the volume of the redundant space will absorb or release a small amount of oil, thereby finely adjusting the amount of oil in the closed oil cavity, offsetting the small displacement of the piston caused by internal leakage or temperature changes, and achieving position locking with an accuracy of ±0.1mm. Under pressure maintenance conditions, the compensation effect of the redundant space on the system pressure is changed by the micro-feedback adjustment of the rotor 11 angle, maintaining the stability of the pipeline pressure.

[0062] like Figure 6 As shown, in reverse flow dynamics, the first flow channel connects port P7 and port B9, and the second flow channel connects port A8 and port T10. The rotor 11 rotates 180 degrees, reversing the connection between the flow channel and the oil port. At this time, hydraulic oil flows from port P7 into port B9, pushing the hydraulic cylinder piston to move in the opposite direction, realizing the normal recovery function of the hydraulic cylinder and completing a complete working cycle.

[0063] like Figure 7 As shown, in the reverse flow restricted state, the first flow channel connects port P7 and port B9, and the second flow channel connects port A8 and port T10. However, at the same time, the inlet space of port A8 is reduced and the outlet space of port B9 is reduced. By rotating the rotor 11, the inlet space of port A8 is reduced, and the flow channel is partially blocked. Flow control is achieved in reverse flow, which expands the application range of valve body 1.

[0064] like Figure 8As shown, in the first blocking state, there is redundancy in the internal space of the valve body 1 at port A 8 and port B 9, and the flow channel is partially or completely blocked. When the rotor 11 rotates to the point that the outer edge of the dumbbell-like body 13 blocks port P 7 and port T 10, the flow channel is disconnected from the working oil port.

[0065] In the second blocking state, there is redundancy in the internal space of valve body 1 at port P7 and port T10, and the flow channel is partially or completely blocked, which blocks the passage between the oil inlet and the oil return port, thus achieving unloading or safety protection of the system.

[0066] Please see Figure 1-11 A method for operating a hydraulic cylinder control valve includes the following steps:

[0067] S1: P port 7 connects to the oil pump's oil supply end, A port 8 connects to the oil supply end of the hydraulic cylinder's lifting stroke, B port 9 connects to the oil supply end of the hydraulic cylinder's retraction stroke, and T port 10 connects to the oil pump's oil receiving end.

[0068] S2: The drive device 5 drives the connecting shaft 17 to rotate clockwise, and the connecting shaft 17 drives the rotor 11 to rotate clockwise through the hollow shaft 16.

[0069] S3: Change the position of the first flow channel and the second flow channel by rotating the rotor 11;

[0070] S4: When the first flow channel is connected to port P7 and port A8, and the second flow channel is connected to port B9 and port T10, the oil pump supplies oil through port P7, and the oil in the hydraulic cylinder enters through port A8 and exits through port B9. At this time, the working state of the hydraulic cylinder is lifting.

[0071] S5: When the first flow channel is connected to port P and port B, and the second flow channel is connected to port A8 and port T10, the oil pump supplies oil through port P7, and the hydraulic cylinder enters through port B9 and exits through port A8. At this time, the working state of the hydraulic cylinder is recovery.

[0072] S6: When the first flow channel position and the second flow channel are in the first blocked state, there is redundancy in the internal space of valve body 1 at port A 8 and port B 9.

[0073] S7: When the first flow channel is in position and the second flow channel is in the second blocked state, there is redundancy in the internal space of valve body 1 at port P7 and port T10.

[0074] Please see Figure 9 and Figure 10 In S2, the one-way lock 20 makes the connecting shaft 17 rotate only counterclockwise, and the locking function of the one-way lock 20 provides a reverse limiting support force for the rotor 11, so that the rotor 11 cannot rotate clockwise, and can remain stable when squeezed by hydraulic oil, providing a stable oil circuit delivery capacity.

[0075] Working principle: During use, after the entire system is started, the PLC controller 6 drives the device 5 according to the preset instructions. This drives the rotor 11 to rotate precisely within the valve body 1 via the connecting shaft 17 and the hollow shaft 16. The magnetic angle sensor 19 monitors the rotation angle and speed of the connecting shaft 17 in real time and feeds the data back to the PLC controller 6 to form a closed-loop control. When the rotor 11 rotates, the position of the flow channel formed by the first and second inward-curving surfaces 14 and 15 on its dumbbell-like body 13 and the inner wall of the valve body 1 changes continuously. In forward flow, the first flow channel connects to port P7 and port A8, and the second flow channel connects to port B9 and port T10, causing the hydraulic oil to push the hydraulic cylinder upward. In reverse flow, the flow channel connection is reversed, and the hydraulic cylinder returns to its original position. By controlling the rotor 11 to a specific intermediate position, the cross-sectional area of ​​the flow channel can be reduced to form a flow restriction state, thereby achieving flow regulation. When the rotor 11 is in a blocked state, its angle can be finely adjusted to form a variable sealed redundant space between port A8 and port B9 or port P7 and port T10. In the first blocked state, the piston stroke and pre-pressure are adjusted by changing the oil volume in the hydraulic cylinder working chamber. In the second blocked state, the pressure and flow of the system are controlled by adjusting the oil volume distribution of the pump pipeline. Throughout the process, the one-way lock 20 ensures that the rotor 11 can only rotate in one direction, preventing hydraulic shock from causing reverse rotation. Finally, through the precise switching and seamless transition of six control modes, multi-functional integrated intelligent control of the hydraulic cylinder's movement direction, speed, position, and output force is achieved.

[0076] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. A hydraulic cylinder control valve characterized by: include: A composite flow control mechanism, comprising a valve body and a rotor, wherein the rotor comprises a chassis and a dumbbell-like body, the chassis being fitted to the bottom surface inside the valve body, and the side end face of the dumbbell-like body being fitted to the inner wall of the valve body; The flow conveying mechanism includes a P port, an A port, a B port, and a T port, which are circumferentially distributed around the valve body in the four directions of due south, due west, due east, and due north, respectively. The dumbbell-shaped body includes a first inward-curving surface and a second inward-curving surface. The space between the inner wall of the valve body and the first inward-curving surface forms a first flow channel, and the space between the inner wall of the valve body and the second inward-curving surface forms a second flow channel. The control system includes a magnetic block, a magnetic angle sensor, and a PLC controller. A hollow shaft is centrally located above the dumbbell-like body. A connecting shaft is connected to the upper end of the hollow shaft. The magnetic block is installed on the outside of the connecting shaft. The connecting shaft is rotatably positioned inside the magnetic angle sensor. The magnetic block and the magnetic angle sensor monitor the rotation angle, speed, and final stopping position of the connecting shaft and transmit the information to the PLC controller. The connecting shaft is also connected to a one-way lock on its outer side. The one-way lock allows the connecting shaft to rotate counterclockwise and prevents it from rotating clockwise, thereby allowing the rotor to rotate counterclockwise and preventing it from rotating clockwise. The control system monitors the rotor's rotation angle, speed, and final stopping position. The rotation of the rotor controls the position of the first and second flow channels. The movement of the first and second flow channels controls the connection and blockage with ports P, A, B, and T, forming six control modes. The six control modes include forward flow dynamics, forward flow restriction state, reverse flow dynamics, reverse flow restriction state, first blockage state, and second blockage state.

2. The hydraulic cylinder control valve according to claim 1, characterized in that: A sealing valve cover is fixedly installed on the top of the valve body. The upper end face of the dumbbell-shaped body is in contact with the inner wall of the sealing valve cover. The hollow shaft passes through the sealing valve cover. The PLC controller is fixedly installed on the top of the sealing valve cover.

3. A hydraulic cylinder control valve according to claim 2, characterized in that: A drive box is fixedly installed above the sealing valve cover. The magnetic angle sensor is fixedly installed on the inner wall of the drive box and is electrically connected to the PLC controller. A cover plate is fixedly installed above the drive box, and a drive device is fixedly installed above the cover plate. The drive device is electrically connected to the PLC controller and is driven by the connecting shaft.

4. A hydraulic cylinder control valve according to claim 1, characterized in that: The inner wall of the one-way locking device is provided with several ratchet teeth. A turntable is rotatably arranged inside the one-way locking device. There is a gap between the outer edge of the turntable and the ratchet teeth. The center position of the turntable is fixedly connected to the connecting shaft. Clamping heads are distributed around the outer circumference of the turntable. The clamping heads are slidably connected to the turntable. A spring is connected between the clamping heads and the inner wall of the turntable. The clamping heads and ratchet teeth engage counterclockwise and slide clockwise.

5. A hydraulic cylinder control valve according to claim 1, characterized in that: During the forward flow dynamics, the first flow channel connects to port P and port A, and the second flow channel connects to port B and port T.

6. A hydraulic cylinder control valve according to claim 1, characterized in that: In the forward flow restricted state, the first flow channel connects to port P and port A, and the second flow channel connects to port B and port T. At the same time, the inflow space of port P is reduced, and the outflow space of port T is reduced.

7. A hydraulic cylinder control valve according to claim 1, characterized in that: During the reverse flow dynamics, the first flow channel connects to ports P and B, and the second flow channel connects to ports A and T.

8. A hydraulic cylinder control valve according to claim 1, characterized in that: In the reverse flow restricted state, the first flow channel connects to ports P and B, and the second flow channel connects to ports A and T. At the same time, the inflow space of port A is reduced, and the outflow space of port B is reduced.

9. A method for operating a hydraulic cylinder control valve, implemented based on a hydraulic cylinder control valve according to any one of claims 1-8, characterized in that, Includes the following steps: S1: P port connects to the oil pump's oil delivery end, A port connects to the hydraulic cylinder's lifting stroke oil supply end, B port connects to the hydraulic cylinder's retraction stroke oil supply end, and T port connects to the oil pump's receiving end. S2: The connecting shaft is driven to rotate clockwise by the drive device, and the connecting shaft drives the rotor to rotate clockwise through the hollow shaft; S3: Change the position of the first and second flow channels by rotating the rotor; S4: When the first flow channel is connected to port P and port A, and the second flow channel is connected to port B and port T, the oil pump supplies oil through port P, and the oil in the hydraulic cylinder enters through port A and exits through port B. At this time, the working state of the hydraulic cylinder is lifting. S5: When the first flow channel is connected to port P and port B, and the second flow channel is connected to port A and port T, the oil pump supplies oil through port P, and the hydraulic cylinder enters through port B and exits through port A. At this time, the working state of the hydraulic cylinder is recovery. S6: When the first flow channel position and the second flow channel are in the first blocked state, there is redundancy in the internal space of the valve body at ports A and B. S7: When the first flow channel is in position and the second flow channel is in the second blocked state, there is redundancy in the internal space of the valve body at the P port and T port.

10. The method for operating a hydraulic cylinder control valve according to claim 9, characterized in that: In S2, the connecting shaft can only rotate counterclockwise by a one-way lock, and the locking function of the one-way lock provides a limiting support force for the rotor to rotate in reverse, so that the rotor cannot rotate clockwise. When subjected to hydraulic oil compression, it can remain stable and provide a stable oil circuit delivery capability.

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