Electro-hydraulic ball valve and control method of electro-hydraulic ball valve

Abstract

This invention provides an electro-hydraulic ball valve and its control method, suitable for media of different viscosities and high-pressure, high-flow-rate applications. The electro-hydraulic ball valve includes an integrated drive assembly, a pilot stage assembly, a power stage assembly, and a flow distribution valve body assembly. The drive assembly includes a drive motor for outputting rotational motion. The power stage assembly includes a motor-end ball and a flow distribution-side ball positioned opposite each other. The spherical surface of the flow distribution-side ball is provided with a first flow distribution groove and a second flow distribution groove, both of which are arc-shaped groove structures with three levels of different areas. The flow distribution valve body assembly includes a connector end cap, on which a P-port pipe connector, a T-port pipe connector, an A-port pipe connector, and a B-port pipe connector are provided. The drive assembly drives the motor-end ball and the flow distribution-side ball to rotate via the pilot stage assembly, thereby switching the connection state of the first and second flow distribution grooves relative to the P-port, T-port, A-port, and B-port pipe connectors.

Description

Technical Field

[0001] This invention relates to the field of fluid transmission and control technology, and in particular to an electro-hydraulic ball valve and a control method for the electro-hydraulic ball valve. Background Technology

[0002] With the continuous development of hydraulic or water-driven mechanical equipment such as engineering machinery, mining machinery, and agricultural machinery, the performance requirements of mechanical products are becoming increasingly demanding. Under the huge market demand at home and abroad, it is of great significance to provide a variable opening servo valve that is simple in structure, easy to control, has high control precision, is applicable to a wide range of media viscosity, and is suitable for ultra-high pressure and high flow applications.

[0003] Existing servo valves mainly consist of spool valves, but the spool valve core is subject to complex forces and is prone to wear and leakage, resulting in a high failure rate, poor product consistency, and limitations in structure that prevent them from operating in high-pressure, high-flow-rate applications. Furthermore, most existing servo valves use hydraulic oil as the medium, which significantly reduces efficiency or even causes unstable operation with low-viscosity fluids such as water. Finally, existing digital valve technology has a complex feedback loop, employing multiple mechanical structures to achieve closed-loop control. This complex structure leads to high product costs, large errors, and hinders widespread application.

[0004] Therefore, there is an urgent need to research a servo valve that is suitable for media of various viscosities and for ultra-high pressure and high flow rate applications. Summary of the Invention

[0005] This invention provides an electro-hydraulic ball valve and its control method to address the shortcomings of existing servo valves, such as limited application in ultra-high pressure and high flow rate applications, poor adaptability to media of different viscosities, and high cost and large error due to complex structure. The invention achieves a simplified structure, convenient control, improved control accuracy, and servo valves that are widely applicable to media of different viscosities and suitable for ultra-high pressure and high flow rate applications.

[0006] This invention provides an electro-hydraulic ball valve, comprising an integrated drive assembly, a pilot stage assembly, a power stage assembly, and a flow distribution valve body assembly. The drive assembly includes a drive motor for outputting rotational motion. The power stage assembly includes a motor-end ball and a flow distribution-side ball disposed opposite to each other. The spherical surface of the flow distribution-side ball is provided with a first flow distribution groove and a second flow distribution groove, both of which are arc-shaped groove structures with three levels of different areas. The flow distribution valve body assembly includes a connector end cap, on which a P-port pipe connector, a T-port pipe connector, an A-port pipe connector, and a B-port pipe connector are disposed. The drive assembly drives the motor-end ball and the flow distribution-side ball to rotate via the pilot stage assembly, thereby switching the connection state of the first flow distribution groove and the second flow distribution groove relative to the P-port pipe connector, the T-port pipe connector, the A-port pipe connector, and the B-port pipe connector.

[0007] According to an electro-hydraulic ball valve provided by the present invention, the pilot stage assembly includes a pilot stage valve core, a pilot stage copper sleeve, two floating vanes disposed opposite each other, and two fixed vanes disposed opposite each other. The flow distribution valve body assembly includes an external pipe connector. The drive motor is driven in conjunction with the pilot stage valve core. The pilot stage copper sleeve is coaxially disposed with the pilot stage valve core. The floating vanes and the fixed vanes are disposed between the pilot stage copper sleeve and the pilot stage valve core to separate four pilot fluid chambers surrounding the pilot stage valve core. The fixed blade is fixed relative to the valve body, and the floating blade is fixed to the pilot stage copper sleeve. The pilot stage copper sleeve is positioned and engaged with the motor end ball and the distribution side ball. The pilot stage valve core is supplied with pilot pressure oil through the external pipe joint. During rotation, the pressure difference between the pilot stage valve core and the pilot fluid cavity is applied to the floating blade by switching the communication state between the pilot stage valve core and the pilot fluid cavity, thereby driving the pilot stage copper sleeve to rotate the motor end ball and the distribution side ball.

[0008] According to an electro-hydraulic ball valve provided by the present invention, the pilot stage valve core is provided with a central hole, a first drainage groove and a second drainage groove. One end of the central hole is connected to the external pipe connector, and the first drainage groove and the second drainage groove are radially connected to the central hole. The floating blade is provided with a first drainage hole and a second drainage hole whose axial positions correspond to the first drainage groove and the second drainage groove, respectively. One end of the first drainage hole faces the pilot stage valve core, and the other end faces the pilot fluid cavity on one side of the floating blade. One end of the second drainage hole faces the pilot stage valve core, and the other end faces the pilot fluid cavity on the other side of the floating blade. During the rotation of the pilot stage valve core, the flow area of ​​the first drainage hole and the first drainage groove is inversely proportional to the flow area of ​​the second drainage hole and the second drainage groove.

[0009] According to an electro-hydraulic ball valve provided by the present invention, the pilot stage valve core is provided with a limiting groove, the limiting groove being an elongated hole or groove with its length direction perpendicular to the axis of the pilot stage valve core; the floating blade is provided with a limiting post that cooperates with the limiting groove to limit the rotation angle range of the floating blade relative to the pilot stage valve core; within the rotation angle range, the first drainage hole and the first drainage groove are always in communication, and the second drainage hole and the second drainage groove are always in communication.

[0010] An electro-hydraulic ball valve according to the present invention includes a housing and a motor end cover. The motor end cover and the connector end cover are respectively sealed and fitted at both ends of the housing. The pilot stage assembly and the power stage assembly are both located within a sealing structure between the housing, the motor end cover and the connector end cover. The drive assembly includes a motor junction box disposed on the outside of the motor end cover and a motor mounting bracket disposed on the inside of the motor end cover. The drive motor is mounted on the motor mounting bracket.

[0011] According to an electro-hydraulic ball valve provided by the present invention, a motor end copper sleeve is provided between the motor end ball and the motor end cover, and a distribution side copper sleeve is provided between the distribution side ball and the connector end cover; both the motor end copper sleeve and the distribution side copper sleeve have concave spherical support structures on their inner sides; the distribution side copper sleeve is provided with through holes corresponding to the P-port connector, the T-port connector, the A-port connector, and the B-port connector respectively; the motor end ball and the distribution side ball are spaced apart to form a pressure relief chamber between them, and a leakage pipe connector is provided on the outer shell at the position corresponding to the pressure relief chamber.

[0012] According to an electro-hydraulic ball valve provided by the present invention, a spherical spring clamping screw is provided on the side of the motor end cover facing the motor end copper sleeve; under the elastic force of the spherical spring clamping screw, there is a wear compensation gap between the motor end cover and the motor end copper sleeve.

[0013] According to an electro-hydraulic ball valve provided by the present invention, the pilot stage assembly includes a motor-end pilot stage end cap and a connector-side pilot stage end cap; both ends of the pilot stage valve core are rotatably fitted to the motor-end pilot stage end cap and the connector-side pilot stage end cap, respectively; the motor-end pilot stage end cap is fixed to the motor end cap, the connector-side pilot stage end cap is fixed to the connector end cap, and the end of the pilot stage valve core facing the drive motor is provided with a spline passing through the motor-end pilot stage end cap, and the pilot stage valve core is connected to the drive shaft of the drive motor through the spline.

[0014] The present invention also provides a control method for an electro-hydraulic ball valve, used to control the electro-hydraulic ball valve described in any of the above embodiments; the method includes: inputting a control command; controlling a drive motor to output a counterclockwise rotation action or a clockwise rotation action according to the control command, so as to realize the on / off combination of pressure port P, pressure port T, hydraulic port A, and hydraulic port B; the on / off combination includes a first combination of P and A being connected and B and T being connected, and a second combination of P and B being connected and A and T being connected.

[0015] According to a control method for an electro-hydraulic ball valve provided by the present invention, the electro-hydraulic ball valve has an initial state in which the initial angle is 0°, and the pressure port P, the pressure port T, the hydraulic port A, and the hydraulic port B are all disconnected; the control command includes a target rotation angle based on the initial angle; the step of controlling the drive motor to output a counterclockwise rotation action or a clockwise rotation action according to the control command includes: controlling the drive motor to output the rotation action of the target rotation angle according to the control command.

[0016] The electro-hydraulic ball valve and its control method provided by this invention achieve effective control of media with different viscosities while possessing high control precision, making it suitable for high-pressure, high-flow-rate applications. When the drive motor rotates, the pilot stage component causes the motor-end ball and the flow distribution side ball to rotate. The positions of the first and second flow distribution grooves on the flow distribution side ball change relative to ports P, T, A, and B, thereby altering the fluid flow path. Since the flow distribution grooves have different areas, the flow area at different positions can be adjusted by precisely controlling the rotation angle when the ball rotates, thus regulating the flow rate and pressure through the valve body. Through integrated structural design and precise flow distribution groove design, the electro-hydraulic ball valve can be adapted to different media viscosities and maintain good control performance under high pressure and high flow conditions. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the electro-hydraulic ball valve of the present invention.

[0019] Figure 2 This is a cross-sectional view of the electro-hydraulic ball valve of the present invention.

[0020] Figure 3 This is a radial cross-sectional view of the first drainage hole of the floating vane of the electro-hydraulic ball valve of the present invention.

[0021] Figure 4 This is a radial cross-sectional view of the second drainage hole of the floating vane of the electro-hydraulic ball valve of the present invention.

[0022] Figure 5 This is a radial cross-sectional view of the floating vane limiting mechanism of the electro-hydraulic ball valve of the present invention.

[0023] Figure 6This is a radial sectional view of the fixed blade limit of the electro-hydraulic ball valve of the present invention.

[0024] Figure 7 This is a schematic diagram of the pilot stage copper sleeve of the electro-hydraulic ball valve of the present invention.

[0025] Figure 8 This is a schematic diagram of the pilot stage valve core of the electro-hydraulic ball valve of the present invention.

[0026] Figure 9 This is a schematic diagram of the flow distribution side ball of the electro-hydraulic ball valve of the present invention.

[0027] Figure 10 This is a schematic diagram of the structure of the motor end ball of the electro-hydraulic ball valve of the present invention.

[0028] Figure 11 This is a schematic diagram of the copper sleeve on the flow distribution side of the electro-hydraulic ball valve of the present invention.

[0029] Figure 12 This is a schematic diagram of the structure of the copper sleeve at the motor end of the electro-hydraulic ball valve of the present invention.

[0030] Figure 13 This is a schematic diagram of the connector end cap of the electro-hydraulic ball valve of the present invention.

[0031] Figure label:

[0032] 1. Motor junction box; 2. Motor end cover; 3. Motor mounting bracket; 4. Felt ring seal; 5. End cover sealing ring; 6. Pilot stage copper sleeve; 8. Ball spring clamping screw; 10. Housing; 11. Drive motor; 12. Motor end pilot stage end cover; 13. Motor end copper sleeve; 14. Motor end ball; 15. Pilot copper sleeve fixing screw; 16. Limiting post; 17. Floating positioning pin; 18. Connector end cover; 19. Pipe connector sealing ring; 20. B-port pipe connector; 22. End cover positioning pin; 23. End cover fixing screw; 24. Connector side pilot stage end cover; 26. External pipe connector; 28. Pilot stage valve core; 2801. First limiting groove; 2802. First drainage groove; 2803. Second drainage groove; 2804. Second limiting groove; 2807, Center Hole; 29, A-port Pipe Connector; 30, Distribution Side Sphere; 3001, First Distribution Channel; 3002, Second Distribution Channel; 31, Distribution Side Copper Sleeve; 33, P-port Pipe Connector; 34, T-port Pipe Connector; 35, Leakage Pipe Connector; 3601, First Fixed Blade; 3602, Second Fixed Blade; 3701, First Floating Blade; 3702, Second Floating Blade; 38, First Pilot Fluid Chamber; 39, Second Pilot Fluid Chamber; 40, Third Pilot Fluid Chamber; 41, Fourth Pilot Fluid Chamber; 4201, Second Blade First Drain Hole; 4202, First Blade First Drain Hole; 4203, Second Blade Second Drain Hole; 4204, First Blade Second Drain Hole; 44, Fixed Blade Fixing Screw. Detailed Implementation

[0033] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0034] In the description of the embodiments of the present invention, it should be noted that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of the present invention 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. Therefore, they should not be construed as limitations on the embodiments of the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance. It should also be noted that in the description of the present invention, unless otherwise explicitly specified and limited, the terms "set," "install," and "connect" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection. Those skilled in the art can understand the specific meaning of the above terms in the present invention according to the specific circumstances.

[0035] The purpose of this invention is to provide a rotary high-flow electro-hydraulic ball valve and its control method. This invention changes the contact area between the pilot valve core control chamber and the pilot pressure oil inlet by altering the rotation angle of the pilot valve core, achieving feedback and following of the ball valve and pilot valve core rotation angle under the drive of the pilot pressure oil, thus realizing rapid response and high-precision control. It employs a design with two three-stage flow distribution channels of different gradient areas to achieve the function of a three-position four-way solenoid directional valve and variable opening flow. A spherical support sealing method with spherical spring clamping screws provides seal wear compensation, achieving high efficiency, low drive power, high stability, high-precision control of the hydraulic valve, and applicability to various viscosity media.

[0036] The following is combined with Figures 1 to 13 A specific embodiment of the electro-hydraulic ball valve of the present invention is described.

[0037] like Figure 1 , Figure 2 , Figure 9 , Figure 10 and Figure 13As shown, the present invention provides an electro-hydraulic ball valve, comprising an integrated drive assembly, a pilot stage assembly, a power stage assembly, and a flow distribution valve body assembly. The drive assembly includes a drive motor 11 for outputting rotary motion. The power stage assembly includes a motor-end ball 14 and a flow distribution-side ball 30 disposed opposite to each other. The spherical surface of the flow distribution-side ball 30 is provided with a first flow distribution groove 3001 and a second flow distribution groove 3002, both of which are arc-shaped groove structures with three levels of different areas. The flow distribution valve body assembly includes a connector end cap 18, on which a P-port pipe connector 33, a T-port pipe connector 34, an A-port pipe connector 29, and a B-port pipe connector 20 are disposed. The drive assembly drives the ball at the end of the motor 11 and the ball on the distribution side 30 to rotate through the pilot stage assembly, so as to switch the connection state of the first distribution channel 3001 and the second distribution channel 3002 relative to the P port pipe connector 33, T port pipe connector 34, A port pipe connector 29 and B port pipe connector 20.

[0038] Specifically, the electro-hydraulic ball valve consists of four main parts: a drive assembly, a pilot stage assembly, a power stage assembly, and a distribution valve body assembly. The drive assembly includes a drive motor 11 responsible for outputting rotational motion. The power stage assembly comprises a motor-end ball 14 and a distribution-side ball 30. The surface of the distribution-side ball 30 is provided with two types of arc-shaped distribution grooves (first distribution groove 3001 and second distribution groove 3002) with three-level gradient area changes. This design allows for precise control of the fluid's direction and flow rate. The distribution valve body assembly includes a connector end cap 18, on which four pipe connectors (P port, T port, A port, and B port) are installed for connecting different fluid channels. The entire system drives the two balls to rotate via the pilot stage assembly through the drive assembly, thereby changing the connection state between the first and second distribution grooves 3001 and 3002 and these pipe connectors, thus achieving precise control of the fluid direction and flow rate. This design is not only simple in structure and easy to control, but it can also adapt to media of different viscosities and maintain good performance in ultra-high pressure and high flow rate applications.

[0039] The pilot stage assembly of an electro-hydraulic ball valve is one of the key components for achieving precise control, such as... Figure 2 , Figure 3 , Figure 4 , Figure 5 , Figure 6 , Figure 7 ,and Figure 8As shown, according to an electro-hydraulic ball valve provided by the present invention, the pilot stage assembly includes a pilot stage valve core 28, a pilot stage copper sleeve 6, two floating vanes disposed opposite each other, and two fixed vanes disposed opposite each other. The distribution valve body assembly includes an external pipe connector 26. The drive motor 11 is driven and engaged with the pilot stage valve core 28. The pilot stage copper sleeve 6 is coaxially disposed with the pilot stage valve core 28. The floating vanes and fixed vanes are disposed between the pilot stage copper sleeve 6 and the pilot stage valve core 28 to separate four pilot fluid chambers surrounding the pilot stage valve core 28. The fixed vanes are fixed relative to the valve body, and the floating vanes are fixed to the pilot stage copper sleeve 6. The pilot stage copper sleeve 6 is positioned and engaged with the motor end ball 14 and the distribution side ball 30. Pilot stage valve core 28 is supplied with pilot pressure oil through external pipe joint 26. During rotation, the connection state between pilot stage valve core 28 and pilot fluid chamber is switched, so that the pressure difference between each pilot fluid chamber acts on the floating blade, thereby driving pilot stage copper sleeve 6 to drive motor end ball 14 and distribution side ball 30 to rotate.

[0040] Specifically, four pilot fluid chambers are formed between two floating vanes and two fixed vanes. The fixed vanes are fixed relative to the valve body, while the floating vanes are fixed to the pilot stage copper sleeve 6. The pilot stage copper sleeve 6 is coaxially arranged with the pilot stage valve core 28 and is positioned and engaged with the motor end ball 14 and the distribution side ball 30 to ensure that they can rotate synchronously. When the drive motor 11 starts, it drives the pilot stage valve core 28 to rotate. At this time, pilot pressure oil is introduced into the pilot stage valve core 28 through the external pipe joint 26. As the pilot stage valve core 28 rotates, it changes the communication state with the four pilot fluid chambers, resulting in pressure differences between the pilot fluid chambers. This pressure difference acts on the floating vanes, causing the pilot stage copper sleeve 6 to start rotating. Since the pilot stage copper sleeve 6 is positioned and engaged with the motor end ball 14 and the distribution side ball 30, the rotation of the pilot stage copper sleeve 6 will cause the two balls to rotate together, thereby changing the position of the first distribution groove 3001 and the second distribution groove 3002, and ultimately realizing the control of the fluid direction and flow rate in the main valve body.

[0041] According to an electro-hydraulic ball valve provided by the present invention, a pilot-stage valve core 28 is provided with a central hole 2807, a first drainage groove 2802, and a second drainage groove 2803. One end of the central hole 2807 is connected to an external pipe connector 26, and the first drainage groove 2802 and the second drainage groove 2803 are radially connected to the central hole 2807. A floating blade is provided with a first drainage hole and a second drainage hole whose axial positions correspond to the first drainage groove 2802 and the second drainage groove 2803, respectively. One end of the first drainage hole faces the pilot-stage valve core 28, and the other end faces the pilot fluid cavity on one side of the floating blade. One end of the second drainage hole faces the pilot-stage valve core 28, and the other end faces the pilot fluid cavity on the other side of the floating blade. During the rotation of the pilot-stage valve core 28, the flow area of ​​the first drainage hole and the first drainage groove 2802 is inversely proportional to the flow area of ​​the second drainage hole and the second drainage groove 2803. When the pilot stage valve core 28 rotates, the flow area between the first flow-inlet and the first flow-inlet groove 2802 changes accordingly. Simultaneously, the flow area between the second flow-inlet and the second flow-inlet groove 2803 also changes accordingly, but the changes in their flow areas are inversely proportional. This means that when the flow area between the first flow-inlet and the first flow-inlet groove 2802 increases, the flow area between the second flow-inlet and the second flow-inlet groove 2803 decreases, and vice versa. This design allows the pilot stage assembly to drive the floating blades by precisely controlling the pressure difference between each pilot fluid chamber during rotation, thereby driving the pilot stage copper sleeve 6 to rotate, and ultimately controlling the rotation of the motor end ball 14 and the distribution side ball 30, achieving precise adjustment of fluid direction and flow rate.

[0042] According to an electro-hydraulic ball valve provided by the present invention, a pilot stage valve core 28 is provided with a limiting groove, which is an elongated hole or groove with its length direction perpendicular to the axis of the pilot stage valve core 28; a floating blade is provided with a limiting post 16 that cooperates with the limiting groove to limit the rotation angle range of the floating blade relative to the pilot stage valve core 28; within the rotation angle range, the first drainage hole and the first drainage groove 2802 are always in communication, and the second drainage hole and the second drainage groove 2803 are always in communication. The function of the limiting post 16 is to limit the rotation angle range of the floating blade relative to the pilot stage valve core 28, ensuring that the floating blade can only rotate within a specific angle range.

[0043] Specifically, during the rotation of the pilot stage valve core 28, the limiting post 16 moves within the limiting groove to limit the maximum rotation angle of the floating blade. Within this rotation angle range, the first drainage hole remains connected to the first drainage groove 2802, and the second drainage hole remains connected to the second drainage groove 2803. This design ensures that regardless of how the pilot stage valve core 28 rotates, the first and second drainage holes on the floating blade will remain connected to the first and second drainage grooves 2802 and 2803 on the pilot stage valve core 28, thereby ensuring that the pilot stage assembly can continuously and effectively control the pressure changes in the pilot fluid chamber, thus achieving precise control of the entire electro-hydraulic ball valve. This limiting mechanism helps improve the reliability and stability of the system while also simplifying the control process.

[0044] An electro-hydraulic ball valve according to the present invention includes a housing 10 and a motor end cover 2. The motor end cover 2 and the connector end cover 18 are respectively sealed and fitted at both ends of the housing 10. The pilot stage assembly and the power stage assembly are both located within a sealed structure between the housing 10, the motor end cover 2, and the connector end cover 18. The motor end cover 2 and the connector end cover 18 are respectively sealed and fitted at both ends of the housing 10, forming a closed space to ensure that the pilot stage assembly and the power stage assembly are safely housed inside this sealed structure, preventing external impurities from entering and protecting the internal components from damage. The drive assembly includes a motor junction box 1 disposed on the outside of the motor end cover 2 and a motor mounting bracket 3 disposed on the inside of the motor end cover 2. The drive motor 11 is mounted on the motor mounting bracket 3.

[0045] like Figure 11 and Figure 12 As shown, according to an electro-hydraulic ball valve provided by the present invention, a motor-end copper sleeve 13 is provided between the motor-end ball 14 and the motor-end cover 2, and a distribution-side copper sleeve 31 is provided between the distribution-side ball 30 and the connector end cover 18. Both the motor-end copper sleeve 13 and the distribution-side copper sleeve 31 have concave spherical support structures on their inner sides, which can ensure stable support for the motor-end ball 14 and the distribution-side ball 30 during rotation. The distribution-side copper sleeve 31 is provided with through holes corresponding to the P-port connector 33, T-port connector 34, A-port connector 29, and B-port connector 20, respectively, for connecting various fluid interfaces to ensure that fluid can flow along a predetermined path. The motor-end ball 14 and the distribution-side ball 30 are spaced apart to form a pressure relief chamber between them. At the position corresponding to the pressure relief chamber, the outer casing 10 is provided with a leakage pipe connector 35 to guide any leaking fluid out, preventing abnormal increases in internal pressure and damage to the system.

[0046] According to an electro-hydraulic ball valve provided by the present invention, a spherical spring clamping screw 8 is provided on the side of the motor end cover 2 facing the motor end copper sleeve 13. The elastic force provided by the spherical spring clamping screw 8 supports the contact between the motor end cover 2 and the motor end copper sleeve 13. Under the support of the elastic force of the spherical spring clamping screw 8, a wear compensation gap exists between the motor end cover 2 and the motor end copper sleeve 13. The existence of the wear compensation gap is to cope with wear that may occur during long-term operation. By reserving a certain gap, even if slight wear occurs between components, it will not lead to poor contact or jamming, thereby ensuring the stability and reliability of the electro-hydraulic ball valve in long-term use.

[0047] According to an electro-hydraulic ball valve provided by the present invention, the pilot stage assembly includes a motor-end pilot stage end cap 12 and a connector-side pilot stage end cap 24. The two ends of the pilot stage valve core 28 are rotatably fitted to the motor-end pilot stage end cap 12 and the connector-side pilot stage end cap 24, respectively. The motor-end pilot stage end cap 12 is fixed to the motor end cap 2, and the connector-side pilot stage end cap 24 is fixed to the connector end cap 18. A spline passing through the motor-end pilot stage end cap 12 is provided at the end of the pilot stage valve core 28 facing the drive motor 11, and the pilot stage valve core 28 is connected to the drive shaft of the drive motor 11 via the spline. Through the spline, the pilot stage valve core 28 and the drive shaft of the drive motor 11 achieve a highly synchronous mechanical connection. When the drive motor 11 operates, it transmits torque to the pilot stage valve core 28 through the spline, thereby driving the pilot stage valve core 28 to rotate.

[0048] like Figures 1 to 13 As shown, according to a preferred embodiment of the present invention, the electro-hydraulic ball valve structure includes a drive assembly, a pilot stage assembly, a power stage assembly, and a flow distribution valve body assembly.

[0049] The drive assembly preferably includes a motor junction box 1, a motor end cover 2, a felt ring seal 4, an end cover sealing ring 5, a motor mounting bracket 3, a ball spring clamping screw 8, and a drive motor 11. The drive motor 11 is mounted on the second mounting surface of the motor mounting bracket 3. When the motor terminal is energized, the magnetic field generated between the stator and rotor assemblies of the motor produces torque, causing the rotor assembly to rotate, which in turn drives the rotating shaft of the drive motor 11.

[0050] The pilot stage valve core 28 of the pilot stage assembly is connected to the rotating shaft of the drive motor 11 via a spline. When the motor rotating shaft rotates, it drives the pilot stage valve core 28 to rotate. The first to fourth pilot fluid chambers 41 consist of two sets of fixed blades, two sets of floating blades, the pilot stage valve core 28, and the pilot stage copper sleeve 6. The floating blades are connected to the pilot stage copper sleeve 6 and the pilot stage valve core 28 via pilot stage copper sleeve fixing screws 15, limiting posts 16, and floating positioning pins 17. The limiting posts 16 can limit the maximum relative rotation angle between the floating blades and the pilot stage valve core to ensure the effectiveness of the flow distribution area. The fixed blades contact the pilot stage copper sleeve 6 and the pilot stage valve core 28 through surface contact and are fixed to the end caps on both sides by fixed blade fixing screws 44. When the motor drive shaft rotates, it drives the pilot valve core 28 to rotate. The fluid medium enters the central hole 2807 through the external pipe joint 26, and then enters the first and second flow channels 2803 of the pilot valve core 28. At the same time, the fluid medium enters the three-stage stepped flow distribution channel through the P-port pipe joint 33 to achieve spherical flow distribution.

[0051] The power stage assembly includes a motor-end copper sleeve 13, a motor-end ball 14, a distribution-side ball 30, a distribution-side copper sleeve 31, and a ball spring clamping screw 8. The first mounting surface of the motor-end copper sleeve 13 is connected to the second mounting surface of the motor-end cover 2 via the ball spring clamping screw 8, and the inner circumference of the motor-end copper sleeve 13 is connected to the motor-end ball 14. The second mounting surface of the distribution-side copper sleeve 31 is connected to the first mounting surface of the connector end cover 18, and the inner circumference of the distribution-side copper sleeve 31 is connected to the distribution-side ball 30. The inner circumference of the power stage valve core is connected to the pilot stage copper sleeve 6, and synchronous rotation with the floating blades is achieved through a floating positioning pin 17 and a boss on the pilot stage copper sleeve 6. In the preferred embodiment, the surface of the distribution-side sphere 30 is machined with two distribution grooves of different areas in three-level gradients. When it is in relative cooperation and rotation with the distribution hole of the distribution-side copper sleeve 31, it can achieve three different constant flow areas, such as stable flow rates of 100, 300 and 600 L / min under rated pressure difference of 4 MPa and emulsion medium.

[0052] The flow distribution valve assembly includes a rubber gasket, a connector end cap 18, a housing 10, a pipe connector sealing ring 19, an external pipe connector 26, an end cap positioning pin 22, an end cap fixing screw 23, a connector-side pilot stage end cap 24, a P-port pipe connector 33, a T-port pipe connector 34, an A-port pipe connector 29, a B-port pipe connector 20, and a leakage pipe connector 35. The first mounting surface of the housing 10 is connected to the first mounting surface of the motor end cap 2 via a rubber gasket, and the second mounting surface of the housing 10 is connected to the first mounting surface of the connector end cap 18 via a rubber gasket. The leakage pipe connector 35 is mounted on the outer mounting surface of the housing 10, while the P-port pipe connector 33, A-port pipe connector 29, B-port pipe connector 20, T-port pipe connector 34, and external pipe connector 26 are mounted on the second mounting surface of the connector end cap 18. The function of the flow distribution valve assembly is to distribute flow to each pipe interface as the power stage valve core rotates.

[0053] Based on the above structure, the process of the pilot stage valve core 28 driving the power stage valve core to achieve three-stage flow distribution is as follows: Taking the counterclockwise rotation angle control analysis as an example, when the first drainage groove 2802 in the pilot stage valve core 28 rotates to a larger contact area with the first drainage hole 4202 of the first blade and the first drainage hole 4201 of the second blade, the high-pressure fluid medium in the first drainage groove 2802 of the pilot stage valve core 28 enters the third pilot fluid cavity 40 and the fourth pilot fluid cavity 41 through the first drainage hole 4202 and the first drainage hole 4201 of the second blade. At the same time, the second drainage groove 2803 in the pilot stage valve core 28 rotates to a smaller contact area with the second drainage hole 4204 and the first drainage hole 4202 of the first blade, and the low-pressure fluid medium in the second drainage groove 2803 of the pilot stage valve core 28 enters the first pilot fluid cavity 38 and the second pilot fluid cavity 39 through the second drainage hole 4204 and the first drainage hole 4202 of the first blade. In this state, the first floating vane 3701 and the second floating vane 3702, under the pressure difference between the high-pressure fluid medium and the low-pressure fluid medium in the pilot fluid chamber, drive the power stage valve core to rotate via the floating positioning pin 17 and the pilot stage copper sleeve 6. The three flow distribution grooves of different areas on the power stage ball valve core achieve three-stage flow distribution during rotation. Finally, the drive motor 11 controls the rotation angle of the pilot stage valve core 28, thereby achieving the final rotation angle control of the power stage ball valve core.

[0054] This invention achieves combined on / off control of pressure port P, pressure port T, hydraulic port A, and hydraulic port B through a two-stage transmission ball valve structure. When the valve core rotates counterclockwise, pressure port P is connected to hydraulic port A, and hydraulic port B is connected to pressure port T; when it rotates clockwise, pressure port P is connected to hydraulic port B, and pressure port T is connected to hydraulic port A.

[0055] The control method of the electro-hydraulic ball valve provided by the present invention is described below. The control method of the electro-hydraulic ball valve described below can be referred to in correspondence with the electro-hydraulic ball valve described above.

[0056] The present invention also provides a control method for an electro-hydraulic ball valve, used to control the electro-hydraulic ball valve of any of the above embodiments; the method includes:

[0057] Step 100: Input control commands.

[0058] The control system receives control signals or commands from external sources. These commands are typically issued by the operator or generated by the automated control system. Control commands can be digital signals, analog signals, or data packets using a specific communication protocol, used to instruct the electro-hydraulic ball valve to perform specific actions.

[0059] Step 200: Control the drive motor 11 to output counterclockwise or clockwise rotation according to the control command, so as to realize the on / off combination of pressure oil port P, pressure oil port T, hydraulic oil port A, and hydraulic oil port B. The on / off combination includes a first combination of P and A being connected and B and T being connected, and a second combination of P and B being connected and A and T being connected.

[0060] Based on the received control command, the control system analyzes the type of action to be performed, i.e., counterclockwise or clockwise rotation. The control system then sends a corresponding control signal to the drive motor 11 to start the motor and make it rotate in the specified direction. The drive motor 11 drives the pilot valve core 28 to rotate via its rotating shaft, thereby controlling the working state of the entire electro-hydraulic ball valve.

[0061] In the first configuration, when the pilot valve core 28 rotates counterclockwise, pressure port P connects to hydraulic port A, and hydraulic port B connects to pressure port T. In this case, the fluid medium input from pressure port P flows to hydraulic port A, while the fluid from hydraulic port B is discharged into pressure port T.

[0062] In the second configuration, when the pilot valve spool 28 rotates clockwise, pressure port P connects to hydraulic port B, and hydraulic port A connects to pressure port T. In this case, the fluid medium input from pressure port P flows to hydraulic port B, while the fluid from hydraulic port A is discharged into pressure port T.

[0063] In practical applications, the electro-hydraulic ball valve is first ensured to be in its initial or known position to correctly execute subsequent control actions. Initialization may include checking the status of the drive motor 11 to ensure all components are ready to receive new control commands. Control commands are received from the control system or operator, containing information about the desired on / off combination. The control commands are parsed to determine the required rotation direction (counterclockwise or clockwise) and the expected on / off combination (first combination or second combination). Based on the parsing results, the drive motor 11 is controlled to rotate in the corresponding direction. If the first combination is required, the motor is controlled to rotate counterclockwise; if the second combination is required, the motor is controlled to rotate clockwise. The rotation status of the motor is monitored to ensure it rotates as expected. Sensors can be used to detect the actual position of the pilot stage valve core 28 to verify whether the predetermined on / off combination has been achieved. Confirmation that the electro-hydraulic ball valve has achieved the desired on / off combination can be accomplished by detecting the flow of the fluid medium at each port.

[0064] After completing the control action, the motor can be stopped, and the system placed in standby mode to await the next control command. Through the above control method, the on / off combinations of the electro-hydraulic ball valve can be effectively controlled, thereby achieving precise control of the hydraulic system.

[0065] Referring to the electro-hydraulic ball valve described earlier, when the drive motor 11 receives an electrical signal, the coil inside the motor generates a magnetic field. The interaction of the magnetic fields between the motor stator and rotor generates torque, which causes the rotor to rotate. The rotor is connected to the pilot-stage valve core 28 via a spline connection mechanism, so the rotation of the rotor is directly transmitted to the pilot-stage valve core 28. The rotation of the pilot-stage valve core 28 is directly driven by the rotor of the drive motor 11. The rotation of the pilot-stage valve core 28 causes the connected floating vanes to rotate. The floating vanes have drainage holes, which allow the fluid medium to pass through the pilot fluid chamber when the pilot-stage valve core 28 rotates. Due to the structural design of the pilot fluid chamber, a pressure difference is formed in the chamber when the fluid medium passes through. The force of the pressure difference drives the power stage valve core to rotate, thereby realizing the on / off control of the fluid medium. This linkage mechanism established between the pilot-stage valve core 28 and the power stage valve core provides two levels of mechanical position feedback. The first level of feedback comes from the rotational position of the pilot-stage valve core 28, which directly affects the position of the floating vanes. The second-stage feedback indirectly affects the position of the power stage valve core by changing the position of the floating vanes, thereby controlling the flow direction of the fluid medium. This two-stage feedback mechanism ensures that the electro-hydraulic ball valve can operate accurately according to the preset control commands.

[0066] In summary, the control method of the electro-hydraulic ball valve is to drive the pilot valve core 28 to rotate via the drive motor 11, and then drive the floating vanes via the pilot valve core 28, using the pressure difference of the fluid medium to drive the power valve core, ultimately achieving the control of the fluid medium's flow. This two-stage mechanical position feedback design ensures accuracy and stability during the control process.

[0067] According to a control method for an electro-hydraulic ball valve provided by the present invention, the electro-hydraulic ball valve has an initial state in which the initial angle is 0°, and all connections between pressure port P, pressure port T, hydraulic port A, and hydraulic port B are disconnected. The control command preferably includes a target rotation angle based on the initial angle. That is, the control command contains information about the target rotation angle, which is based on the initial angle (0°). The control command can be a counter-clockwise or clockwise rotation to achieve different on / off combinations.

[0068] Based on this, the step of controlling the drive motor 11 to output counterclockwise or clockwise rotation according to the control command preferably further includes:

[0069] Step 201: Control the drive motor 11 to output the rotation action of the target rotation angle according to the control command.

[0070] Specifically, the control system receives a control command from an external source specifying the desired target rotation angle. Based on the received command, the control system calculates the target rotation angle and determines whether the drive motor 11 needs to rotate counter-clockwise or clockwise. When counter-clockwise rotation is required, the control system sends a counter-clockwise rotation control signal to the drive motor 11. When clockwise rotation is required, the control system sends a clockwise rotation control signal to the drive motor 11. Upon receiving the control signal, the drive motor 11 generates a magnetic field between the stator and rotor via its coils, creating torque that drives the motor to rotate. The motor, through a spline connection, drives the pilot stage valve core 28 to rotate, achieving the predetermined target rotation angle. The rotation of the pilot stage valve core 28 causes fluid medium to flow into the pilot fluid chamber through the drainage holes of the floating vanes, creating a pressure difference. This pressure difference acts on the floating vanes, driving the power stage valve core to rotate via the floating positioning pin 17 and the pilot stage copper sleeve 6. The flow distribution grooves of different areas on the power stage valve core achieve three-stage flow distribution during rotation, thereby realizing the on / off combinations of pressure port P, pressure port T, hydraulic port A, and hydraulic port B. Specifically, when the pilot stage valve core 28 rotates counterclockwise, the first combination is achieved: pressure port P is connected to hydraulic port A, and hydraulic port B is connected to pressure port T. When the pilot stage valve core 28 rotates clockwise, the second combination is achieved: pressure port P is connected to hydraulic port B, and hydraulic port A is connected to pressure port T. In this way, the electro-hydraulic ball valve can achieve precise on / off control of the fluid medium according to control commands, thus meeting the needs of different application scenarios.

[0071] The electro-hydraulic ball valve and its control method according to the preferred embodiment of the present invention have the following specific control scheme:

[0072] When the control command is PA connected and BT connected: a detailed analysis is performed by rotating counterclockwise by α° (at which time the flow rate is XL / min) (the relationship between the rotation angle and the flow rate is determined by the specific size and structure of the rotary valve, and no limitations are imposed here).

[0073] The pilot valve rotation angle control process is as follows: The input command to rotate counterclockwise by α° is an electrical control signal that generates a magnetic field between the motor stator and the motor rotor through the motor coil and the interaction generates a torque to drive the drive motor 11 to rotate counterclockwise by α°. The drive motor 11 is connected to the pilot valve core 28 through a spline, thereby driving the pilot valve core 28 to rotate counterclockwise by α°.

[0074] The high-pressure chamber of the pilot valve is controlled as follows: First pressure oil enters the central hole 2107 through the pilot valve core inlet pipe joint 22, and then enters the first guide groove 2102 of the pilot valve core. At this time, the pilot valve core 21 rotates counterclockwise by α° to make the first guide groove 2102 of the pilot valve core rotate to a larger contact area with the first guide hole 3302 and the first guide hole 3301 of the first floating blade. The high-pressure fluid medium in the first guide groove 2102 of the pilot valve core enters the third pilot fluid chamber 30 and the fourth pilot fluid chamber 31 through the first guide hole 3302 and the first guide hole 3301 of the first floating blade, which in turn causes the pressure in the fluid chamber to increase.

[0075] The low-pressure chamber control of the pilot valve is as follows: First pressure oil enters the central hole 2107 through the pilot valve core inlet pipe connector 22, and then enters the second guide groove 2103 of the pilot valve core. At this time, the pilot valve core 21 rotates counterclockwise by α°, reducing the contact area between the second guide groove 2103 of the pilot valve core and the second guide hole 3304 and the second guide hole 3303 of the first floating vane. The low-pressure fluid medium in the second guide groove 2103 of the pilot valve core enters the first pilot fluid chamber 28 and the second pilot fluid chamber 29 through the second guide hole 3304 and the second guide hole 3303 of the first floating vane, thereby causing a decrease in the pressure within the fluid chamber.

[0076] The process of the pilot valve core driving the power valve core to rotate is as follows: The drive motor 11 drives the pilot valve core 28 to rotate counterclockwise by α°. Since the pilot valve core 28 moves before the power ball valve, the resulting angle difference causes the first guide groove 2802 of the pilot valve core to rotate until the contact area with the first guide hole 4202 and the first guide hole 4201 of the first floating blade is greater than the contact area with the second guide groove 2803 of the pilot valve core and the second guide hole 4204 and the second guide hole 4203 of the first floating blade. At this time, the third pilot fluid chamber 30 and the fourth pilot fluid chamber 31 are high-pressure oil chambers, and the first pilot fluid chamber 28 and the second pilot fluid chamber 29 are low-pressure oil chambers. Therefore, under the pressure difference between the high-pressure fluid medium and the low-pressure fluid medium in the pilot fluid chamber, the first floating blade 2701 and the second floating blade 2702 drive the power ball valve core 16 to rotate counterclockwise through the transmission pin 32.

[0077] The power output process of the power stage valve core is as follows: Under the drive of the pilot stage valve core 21, the second hydraulic oil enters the first distribution groove 1601 through the P port connector 15 and is then output to the A port connector 25, realizing the flow of PA; at the same time, the third hydraulic oil flows in through the B port connector 24, flows out through the second distribution groove 1604 to the T port connector 23, realizing the flow of BT. In the example analysis, 0°-5° is the first step flow rate adjustment range, which can achieve stepless control of the flow rate from 0-100L / min; 5°-7° is the first step stable flow rate angle range, which can achieve a stable output of 100L / min; and 7°-16° is the first step flow rate adjustment angle range, which can achieve a flow rate adjustment of 100-300L / min. The system provides stepless flow rate control output in L / min. The first-stage stable flow rate angle range is 16°-18°, achieving a stable output of 300 L / min. The second-stage flow rate adjustment angle range is 18°-36°, achieving stepless flow rate control output of 300-600 L / min. The third-stage stable flow rate angle range is 36°-38°, achieving a stable output of 600 L / min. This enables graded and constant-value flow distribution in spherical distribution. In the embodiment, the stable flow rates are 100, 300, and 600 L / min under a rated pressure difference of 4 MPa and an emulsion medium, respectively. Even with a response error of ±1°, constant-value flow rate output can still be achieved, meeting the requirements for multi-stage constant-value precise flow rate output.

[0078] The angle follow-up overshoot correction process is as follows: When the rotation angle overshoot of the power stage ball valve is greater than the rotation angle of the pilot stage valve core 28, the resulting reverse angle difference causes the first guide groove 2802 of the pilot stage valve core to rotate until the contact area with the first guide hole 4202 and the first guide hole 4201 of the first floating blade is smaller than the contact area with the second guide groove 2803 of the pilot stage valve core and the second guide hole 4204 and the second guide hole 4203 of the first floating blade. At this time, the third pilot fluid chamber 30 and the first... The fourth pilot fluid chamber 31 is a low-pressure oil chamber, and the first pilot fluid chamber 28 and the second pilot fluid chamber 29 are high-pressure oil chambers. Therefore, under the pressure difference between the high-pressure fluid medium and the low-pressure fluid medium in the pilot fluid chamber, the first floating vane 3701 and the second floating vane 3702 drive the power stage ball valve core to rotate clockwise through the floating vane positioning pin 17 and the boss of the pilot stage copper sleeve 6, thereby realizing the correction of the overshoot angle. Through the combined action of the above response and overshoot correction links, the feedback and following of the rotation angle of the ball valve and the pilot valve core are completed.

[0079] When the control command is PB connection and AT connection: perform a detailed analysis by rotating clockwise by α° (at which time the flow rate is XL / min) (the relationship between the rotation angle and the flow rate is determined by the specific size and structure of the rotary valve, and no limitations are imposed here).

[0080] The pilot valve rotation angle control process is as follows: The input command to rotate clockwise by α° is an electrical control signal that generates a magnetic field between the motor stator and the motor rotor through the motor coil and the interaction generates a torque that drives the drive motor 11 to rotate clockwise by α°. The drive motor 11 is connected to the pilot valve core 28 through a spline, thereby driving the pilot valve core 28 to rotate clockwise by α°.

[0081] The high-pressure chamber of the pilot valve is controlled as follows: First pressure oil enters the central hole 2107 through the pilot valve core inlet pipe joint 22, and then enters the second guide groove 2103 of the pilot valve core. At this time, the pilot valve core 21 rotates clockwise by α° to make the second guide groove 2103 of the pilot valve core rotate to a larger contact area with the second guide hole 3304 and the second guide hole 3303 of the first floating blade. The high-pressure fluid medium in the second guide groove 2103 of the pilot valve core enters the first pilot fluid chamber 28 and the second pilot fluid chamber 29 through the second guide hole 3304 and the second guide hole 3303 of the first floating blade, thereby causing the pressure in the fluid chamber to increase.

[0082] The low-pressure chamber of the pilot valve is controlled as follows: First pressure oil enters the central hole 2107 through the pilot valve core inlet pipe connector 22, and then enters the first guide groove 2102 of the pilot valve core. At this time, the pilot valve core 21 rotates counterclockwise by α°, reducing the contact area between the first guide groove 2102 and the first guide hole 3302 and the second guide hole 3301 of the first floating vane. The low-pressure fluid medium in the first guide groove 2102 of the pilot valve core enters the third pilot fluid chamber 30 and the fourth pilot fluid chamber 31 through the first guide hole 3302 and the second guide hole 3301 of the first floating vane, thereby causing a decrease in the pressure within the fluid chamber.

[0083] The process of the pilot valve core driving the power valve core to rotate is as follows: The drive motor 11 drives the pilot valve core 28 to rotate clockwise by α°. Since the pilot valve core 28 moves before the power ball valve, the resulting angle difference causes the first guide groove 2802 of the pilot valve core to rotate to a point where the contact area with the first guide hole 4202 and the first guide hole 4201 of the first floating blade is smaller than the contact area with the second guide groove 2803 of the pilot valve core and the second guide hole 4204 and the second guide hole 4203 of the first floating blade. At this time, the third pilot fluid chamber 30 and the fourth pilot fluid chamber 31 are low-pressure oil chambers, and the first pilot fluid chamber 28 and the second pilot fluid chamber 29 are high-pressure oil chambers. Therefore, under the pressure difference between the high-pressure fluid medium and the low-pressure fluid medium in the pilot fluid chamber, the first floating blade 2701 and the second floating blade 2702 drive the power ball valve core 16 to rotate clockwise through the transmission pin 32.

[0084] The power output process of the power stage valve core is as follows: Under the drive of the pilot stage valve core 21, the second hydraulic oil enters the second distribution groove 1604 through the P port connector 15 and is then output to the B port connector 2A, realizing the flow of PB; at the same time, the third hydraulic oil flows in through the A port connector 25, flows out through the first distribution groove 1601 to the T port connector 23, realizing the flow of AT. In the example analysis, 0°-5° is the first step flow rate adjustment range, which can achieve stepless control of the flow rate from 0-100L / min; 5°-7° is the first step stable flow rate angle range, which can achieve a stable output of 100L / min; and 7°-16° is the first step flow rate adjustment angle range, which can achieve a flow rate adjustment of 100-300L / min. The system provides stepless flow rate control output in L / min. The first-stage stable flow rate angle range is 16°-18°, achieving a stable output of 300 L / min. The second-stage flow rate adjustment angle range is 18°-36°, achieving stepless flow rate control output of 300-600 L / min. The third-stage stable flow rate angle range is 36°-38°, achieving a stable output of 600 L / min. This enables graded and constant-value flow distribution in spherical distribution. In the embodiment, the stable flow rates are 100, 300, and 600 L / min under a rated pressure difference of 4 MPa and an emulsion medium, respectively. Even with a response error of ±1°, constant-value flow rate output can still be achieved, meeting the requirements for multi-stage constant-value precise flow rate output.

[0085] The angle follow-up overshoot correction process is as follows: When the rotation angle overshoot of the power stage ball valve is greater than the rotation angle of the pilot stage valve core 28, the resulting reverse angle difference causes the first guide groove 2802 of the pilot stage valve core to rotate until the contact area with the first guide hole 4202 and the first guide hole 4201 of the first floating blade is greater than the contact area with the second guide groove 2803 of the pilot stage valve core and the second guide hole 4204 and the second guide hole 4203 of the first floating blade. At this time, the third pilot fluid chamber 30 and the fourth pilot fluid chamber 30... The guide fluid chamber 31 is a high-pressure oil chamber, and the first pilot fluid chamber 28 and the second pilot fluid chamber 29 are low-pressure oil chambers. Therefore, under the pressure difference between the high-pressure fluid medium and the low-pressure fluid medium in the pilot fluid chamber, the first floating vane 3701 and the second floating vane 3702 drive the power stage ball valve core to rotate counterclockwise through the floating vane positioning pin 17 and the boss of the pilot stage copper sleeve 6, thereby realizing the correction of the overshoot angle. Through the combined action of the above response and overshoot correction links, the feedback and following of the rotation angle of the ball valve and the pilot valve core are completed.

[0086] In summary, the above control method achieves precise mechanical position feedback. When the input command rotates ±α°, the power stage ball valve core 16 can be synchronously rotated with the pilot stage valve core 21, thereby enabling the control of the rotation angle signal of the drive motor to control the opening of the rotary valve core, realizing closed-loop mechanical rotation control of the ball valve.

[0087] Compared with existing technologies, the rotary high-flow electro-hydraulic ball valve and its control method proposed in this invention have significant advantages. First, this invention adopts a modular design, sequentially stacking a drive assembly, a pilot stage assembly, a power stage assembly, and a flow distribution valve body assembly. It utilizes the ball valve core structure to achieve spherical flow distribution and uses two flow distribution grooves with three different gradient areas to achieve graded and constant-value flow distribution. This design not only reduces the manufacturing difficulty of the valve body but also improves the response speed and feedback accuracy, making the electro-hydraulic ball valve suitable for higher pressure and larger variable flow applications. Second, the power stage ball valve core assembly uses a single-turn valve to achieve three-position four-way directional valve function, employing a double-cycle symmetrical design and a spherical support sealing method, with a ball spring clamping screw 8 providing seal wear compensation. This design not only improves the stress state of the valve core, reduces vibration, and enhances stability but also effectively prevents fluid medium leakage, ensuring excellent sealing performance. Furthermore, this invention is the first to propose a control method where the power-stage ball valve spool rotates 28 degrees following the pilot-stage valve spool, effectively solving the problem of large frictional torque caused by spherical support. It also proposes a control correction method: when the power-stage valve spool rotation angle is too large, the position of the high-pressure and low-pressure oil chambers in the pilot fluid chamber can be adjusted to automatically correct the main valve spool rotation angle, thereby ensuring high-precision angle-following control. Finally, this invention has a simple structure, small size, and wide applicability, possessing high innovation and promotional value, and demonstrating broad market application prospects.

[0088] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "method," "specific method," or "some methods," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or method is included in at least one embodiment or method of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or method. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or methods. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or methods described in this specification, as well as the features of different embodiments or methods.

[0089] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. An electro-hydraulic ball valve, characterized in that, This includes the integrated drive assembly, pilot stage assembly, power stage assembly, and distribution valve body assembly; The drive assembly includes a drive motor for outputting rotational motion; The power stage component includes a motor end sphere and a distribution side sphere arranged opposite to each other. The spherical surface of the distribution side sphere is provided with a first distribution groove and a second distribution groove. Both the first distribution groove and the second distribution groove are arc-shaped groove structures with three levels of different areas. The distribution valve body assembly includes a connector end cap, on which a P-port pipe connector, a T-port pipe connector, an A-port pipe connector, and a B-port pipe connector are provided; The drive assembly drives the motor end ball and the distribution side ball to rotate through the pilot stage assembly, thereby switching the connection state of the first distribution channel and the second distribution channel relative to the P port pipe joint, the T port pipe joint, the A port pipe joint, and the B port pipe joint; The pilot stage assembly includes a pilot stage valve core, a pilot stage copper sleeve, two floating blades arranged opposite each other, and two fixed blades arranged opposite each other. The flow distribution valve body assembly includes an external pipe joint. The drive motor is driven by the pilot stage valve core. The pilot stage copper sleeve is coaxially arranged with the pilot stage valve core. The floating blade and the fixed blade are arranged between the pilot stage copper sleeve and the pilot stage valve core to separate four pilot fluid chambers surrounding the pilot stage valve core. The fixed blade is fixed relative to the valve body. The floating blade is fixed to the pilot stage copper sleeve. The pilot stage copper sleeve is positioned and engaged with the motor end ball and the flow distribution side ball. The pilot stage valve core is supplied with pilot pressure oil through the external pipe joint. During rotation, the connection state between the pilot stage valve core and the pilot fluid chamber is switched, so that the pressure difference between each pilot fluid chamber acts on the floating blade, thereby driving the pilot stage copper sleeve to drive the motor end ball and the distribution side ball to rotate. The pilot valve core is provided with a central hole, a first drainage groove and a second drainage groove. One end of the central hole is connected to the external pipe connector, and the first drainage groove and the second drainage groove are radially connected to the central hole. The floating blade is provided with a first drainage hole and a second drainage hole whose axial positions correspond to the first drainage groove and the second drainage groove, respectively. One end of the first drainage hole faces the pilot stage valve core and the other end faces the pilot fluid cavity on one side of the floating blade. One end of the second drainage hole faces the pilot stage valve core and the other end faces the pilot fluid cavity on the other side of the floating blade. During the rotation of the pilot valve core, the flow area of ​​the first drainage hole and the first drainage groove is inversely proportional to the flow area of ​​the second drainage hole and the second drainage groove.

2. The electro-hydraulic ball valve according to claim 1, characterized in that, The pilot stage valve core is provided with a limiting groove, which is an elongated hole or groove whose length direction is perpendicular to the axis of the pilot stage valve core. The floating blade is provided with a limiting post that cooperates with the limiting groove to limit the rotation angle range of the floating blade relative to the pilot stage valve core. Within the range of rotation angles, the first drainage hole and the first drainage groove are always in communication, and the second drainage hole and the second drainage groove are always in communication.

3. The electro-hydraulic ball valve according to claim 1 or 2, characterized in that, It includes an outer housing and a motor end cover, wherein the motor end cover and the connector end cover are respectively sealed and fitted at both ends of the outer housing, and the pilot stage assembly and the power stage assembly are both located within a sealed structure between the outer housing, the motor end cover and the connector end cover; The drive assembly includes a motor junction box disposed on the outside of the motor end cover and a motor mounting bracket disposed on the inside of the motor end cover, and the drive motor is mounted on the motor mounting bracket.

4. The electro-hydraulic ball valve according to claim 3, characterized in that, A motor end copper sleeve is provided between the motor end ball and the motor end cover, and a distribution side copper sleeve is provided between the distribution side ball and the connector end cover; The inner sides of both the motor end copper sleeve and the distribution side copper sleeve have concave spherical support structures. The distribution side copper sleeve is provided with through holes corresponding to the P port pipe joint, the T port pipe joint, the A port pipe joint, and the B port pipe joint, respectively. The motor end ball and the distribution side ball are spaced apart to form a pressure relief chamber between them. At the position corresponding to the pressure relief chamber, the outer shell is provided with a leakage pipe joint.

5. The electro-hydraulic ball valve according to claim 4, characterized in that, A ball spring clamping screw is provided on the side of the motor end cover facing the motor end copper sleeve; Under the elastic force of the ball spring clamping screw, there is a wear compensation gap between the motor end cover and the motor end copper sleeve.

6. The electro-hydraulic ball valve according to claim 3, characterized in that, The pilot stage assembly includes a motor-side pilot stage end cap and a connector-side pilot stage end cap; The two ends of the pilot stage valve core are respectively rotatably fitted to the motor end pilot stage end cap and the connector side pilot stage end cap; The pilot stage end cap at the motor end is fixed to the motor end cap, and the pilot stage end cap at the connector side is fixed to the connector end cap. The pilot stage valve core is provided with a spline passing through the pilot stage end cap at one end facing the drive motor, and the pilot stage valve core is connected to the drive shaft of the drive motor through the spline.

7. A control method for an electro-hydraulic ball valve, characterized in that, For controlling the electro-hydraulic ball valve according to any one of claims 1 to 6; The methods include: Input control commands; According to the control command, the drive motor is controlled to output counterclockwise or clockwise rotation to realize the on / off combination of pressure oil port P, pressure oil port T, hydraulic oil port A, and hydraulic oil port B. The on / off combinations include a first combination of P and A being connected and B and T being connected, and a second combination of P and B being connected and A and T being connected.

8. The control method for the electro-hydraulic ball valve according to claim 7, characterized in that, The electro-hydraulic ball valve has an initial state in which the initial angle is 0° and the pressure port P, the pressure port T, the hydraulic port A, and the hydraulic port B are all disconnected. The control command includes a target rotation angle based on the initial angle; The step of controlling the drive motor to output a counterclockwise rotation or a clockwise rotation according to the control command includes: The control command controls the drive motor to output the rotation action of the target rotation angle.

Images