Rotary direct drive multi-nozzle jet electro-hydraulic servo valve

Abstract

The application provides a rotary direct drive multi-nozzle jet electro-hydraulic servo valve and belongs to the technical field of electro-hydraulic control. The rotary direct drive multi-nozzle jet electro-hydraulic servo valve comprises a valve body, a rotary valve core and a servo motor. Four jet nozzles for oil injection are arranged on the rotary valve core and are communicated with internal oil channels. Four receiving holes are arranged on the inner wall of the valve body, each receiving hole is communicated with a corresponding control oil channel and corresponds to a jet nozzle, and in use, two receiving holes are located on the front side of the corresponding oil injection structure in the rotation direction, and the other two receiving holes are located on the rear side of the corresponding oil injection structure in the rotation direction. The electro-hydraulic servo valve designed in the application has the remarkable characteristics of simple structure, high efficiency, low processing cost, strong anti-pollution performance, high reliability, convenient maintenance and application, etc.

Description

Technical Field

[0001] This invention relates to a rotary direct-drive multi-nozzle jet electro-hydraulic servo valve, belonging to the field of electro-hydraulic control technology. Background Technology

[0002] The electro-hydraulic servo valve is the core control component of an electro-hydraulic servo control system, connecting the electrical and hydraulic components. It acts as both an electro-hydraulic conversion element and a power amplification element, converting low-power electrical signals into high-power hydraulic energy that is related to the magnitude and polarity of the control signal. This allows for the control of the displacement (or rotational speed), speed (or angular velocity), acceleration (or angular acceleration), and force (or torque) of the hydraulic actuator. Therefore, the performance of the electro-hydraulic servo valve directly affects the control accuracy and response speed of the entire electro-hydraulic servo system, and also directly impacts the system's reliability and lifespan. Currently, electro-hydraulic servo valves can be mainly classified by structure into direct-drive electro-hydraulic servo valves, rotary direct-drive electro-hydraulic servo valves, dual-nozzle baffle electro-hydraulic servo valves, jet tube electro-hydraulic servo valves, and deflected jet electro-hydraulic servo valves. Among these, jet tube electro-hydraulic servo valves and deflected jet electro-hydraulic servo valves have the best anti-contamination performance.

[0003] The hydraulic amplifiers constituting an electro-hydraulic servo valve mainly consist of spool valves, rotary spool valves, dual-nozzle baffle valves, jet pipe valves, and deflecting jet valves. Among these, the jet pipe valve and the deflecting jet valve are usually used in conjunction with the spool valve to form a two-stage electro-hydraulic servo valve, that is, the jet pipe valve and the deflecting jet valve are usually used as the pre-stage of a two-stage electro-hydraulic servo valve. For example, Chinese invention patent application CN108386566A discloses a jet pipe electro-hydraulic servo valve (i.e., an electro-hydraulic servo valve) adapted to a variable temperature field. In this valve, the jet nozzle and the receiver constitute the pre-stage of the jet pipe servo valve, controlling the movement of the spool valve. After the torque motor applies a control current, it drives the jet pipe to deflect, and the energy of the two jet receiving holes of the receiver is no longer the same. The resulting pressure difference drives the valve core to move.

[0004] The aforementioned electro-hydraulic servo valve is a two-stage valve, with the main valve being a spool valve requiring high machining precision. Therefore, its structure is complex and its cost is high. Furthermore, due to the load-bearing capacity limitations of the torque motor for the jet valve and the deflector jet valve, the nozzles are relatively small. After prolonged operation, they are easily clogged by particles and other impurities in the oil, leading to nozzle malfunction and low reliability. Simultaneously, the complex two-stage valve structure results in numerous potential failure points, further contributing to low reliability. Additionally, the small nozzle size leads to a low flow rate. Moreover, the jet nozzle's position in the middle of the two receiving holes prevents a significant amount of oil from flowing into the receiving holes, resulting in a large mid-position leakage flow and low energy utilization. Therefore, it is typically only used as the first stage of a two-stage electro-hydraulic servo valve. Summary of the Invention

[0005] The purpose of this invention is to provide a rotary direct-drive multi-nozzle jet electro-hydraulic servo valve to solve the problems of existing jet pipe valves and deflector jet valves having small flow rates, usually requiring cooperation with slide valves to form a two-stage electro-hydraulic servo valve, which has the problems of complex structure, high cost and low reliability.

[0006] To achieve the above objectives, the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve of the present invention adopts the following technical solution:

[0007] A rotary direct-drive multi-nozzle jet electro-hydraulic servo valve includes a valve body, a rotary valve core disposed within the valve body, and a rotary power source mounted on the valve body and pulsatorically connected to the rotary valve core to control the rotation angle of the rotary valve core. The valve body is provided with an oil inlet channel and at least two control oil channels. The rotary valve core is provided with an internal oil channel and a connecting structure connecting the internal oil channel and the oil inlet channel. The rotary valve core is also provided with at least two injection structures that communicate with the internal oil channels and are used for oil injection. The inner wall of the valve body is provided with at least two receiving holes, each receiving hole communicating with a corresponding control oil channel and corresponding one-to-one with an injection structure. In use, at least one receiving hole is located on the front side of the rotation direction of the corresponding injection structure, and at least one receiving hole is located on the rear side of the rotation direction of the corresponding injection structure.

[0008] The beneficial effects of the above technical solution are as follows: This invention proposes a pioneering rotary direct-drive multi-nozzle jet electro-hydraulic servo valve. This electro-hydraulic servo valve includes a valve body, a rotary valve core, and a rotary power source. The rotary power source directly drives the rotary valve core to rotate and can control the rotation angle of the rotary valve core. An internal oil passage is provided inside the rotary valve core, and a connecting structure is provided on the rotary valve core to connect the internal oil passage and the oil inlet channel on the valve body. This allows external oil to sequentially enter the internal oil passage of the rotary valve core through the oil inlet channel on the valve body and the connecting structure. The rotary valve core is also provided with at least two oil spraying structures that communicate with the internal oil passage and are used for oil spraying, allowing oil to be sprayed out through the oil spraying structures. The valve body inner wall is provided with... The device has at least two receiving holes, each connected to a corresponding control oil passage and corresponding to a specific injection structure. During operation, at least one receiving hole is located on the front side of the corresponding injection structure's rotation direction, and at least one receiving hole is located on the rear side. When the rotary valve core rotates in one direction, some injection structures will have a larger overlap area with the receiving hole on the front side, increasing the flow area, pressure, and flow rate. Simultaneously, some injection structures will be further offset from the receiving hole on the rear side, further reducing the overlap area, decreasing the flow area, pressure, and flow rate. Since the receiving holes are connected to corresponding control oil passages, the output pressure and flow rate of different control oil passages are adjusted. The effect is the same when the rotary valve core rotates in the opposite direction, thus directly controlling the different actions of the actuators.

[0009] In summary, the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve of this invention eliminates the need for a spool valve, making it a single-stage electro-hydraulic servo valve. By eliminating the spool valve, the structure is simplified, reducing costs. Furthermore, the simplified structure reduces the number of components, consequently decreasing potential failure points and increasing reliability. Additionally, since the rotary valve core is driven by a rotary power source on the valve body, a more powerful rotary power source can be selected, allowing for the selection of larger nozzles. This makes the nozzles less prone to clogging by contaminants, resulting in higher contamination resistance and improved reliability.

[0010] Furthermore, the receiving hole located on the front side of the rotation direction of the fuel injection structure is defined as the front receiving hole, and the receiving hole located on the rear side of the rotation direction of the fuel injection structure is defined as the rear receiving hole. There are at least two front receiving holes and at least two rear receiving holes. The control oil passages corresponding to the at least two front receiving holes are connected through the first connecting oil passage, and the control oil passages corresponding to the at least two rear receiving holes are connected through the second connecting oil passage.

[0011] The beneficial effects of the above technical solution are that: at least two front receiving holes and at least two rear receiving holes are provided, and under the connection between the first connecting oil passage and the second connecting oil passage, the output flow of the control oil passage is greater.

[0012] Furthermore, the valve body includes a plate and an annular body connected to the plate. The control oil passage is located within the plate and the annular body. The first connecting oil passage and the second connecting oil passage are both located within the plate. Both the first connecting oil passage and the second connecting oil passage include at least one straight oil passage.

[0013] The beneficial effects of the above technical solution are: it facilitates the setting and processing of the first connecting oil passage and the second connecting oil passage.

[0014] Furthermore, the number of receiving holes and oil injection structures is even, and each receiving hole and each oil injection structure is evenly distributed around the circumference.

[0015] The advantages of the above technical solution are: balanced force distribution and convenient adjustment of the output pressure and flow rate of different control oil passages.

[0016] Furthermore, the internal oil passage includes a cross-shaped oil passage and a central oil passage connected to the center of the cross-shaped oil passage. Four oil injection structures are located at the outlets of the cross-shaped oil passages, and the connecting structures are located at the ends of the central oil passages.

[0017] The advantages of the above technical solution are: it facilitates oil inlet and oil spraying, has a simple and symmetrical structure, and is easy to process and manufacture.

[0018] Furthermore, the oil injection structure is a jet nozzle installed on a rotary valve core, and the distance between the jet nozzle and the inner wall of the valve body is 1 to 2 times the diameter of the jet nozzle.

[0019] The beneficial effects of the above technical solution are: too small a distance will generate a large counter-impact force, while too large a distance will affect the flow rate and pressure of the liquid discharge. A distance of 1 to 2 times the diameter of the jet nozzle is most suitable.

[0020] Furthermore, the oil injection structure is a jet nozzle mounted on a rotary valve core, and the orifice area of ​​the receiving hole is 1 to 3 times the nozzle area of ​​the jet nozzle.

[0021] The beneficial effects of the above technical solution are as follows: if the receiving area of ​​the receiving hole is too small or too large, the jet nozzle will be unable to change the flow difference and pressure difference of the control oil passage within a large angle range, resulting in poor performance. The receiving area of ​​the receiving hole is most suitable to be 1 to 3 times the nozzle area of ​​the jet nozzle.

[0022] Furthermore, the connecting structure is a connecting pipe with one end fixedly connected to the rotary valve core and the other end extending into the oil inlet channel of the valve body and sealingly fitted with the oil inlet channel.

[0023] The advantages of the above technical solution are: the connection structure is simple, easy to manufacture and assemble, and facilitates the oil to enter the internal oil passage of the rotary valve core through the oil inlet channel of the valve body.

[0024] Furthermore, one end of the valve body is an open end, and the rotary power source is installed at the open end of the valve body and together with the valve body, forms a chamber for setting the rotary valve core.

[0025] The beneficial effects of the above technical solution are: the use of a rotary power source to jointly form a chamber for setting the rotary valve core results in a compact structure and facilitates the assembly of the electro-hydraulic servo valve.

[0026] Furthermore, the rotational power source is a servo motor.

[0027] The advantages of the above technical solution are: the servo motor has strong load-bearing capacity, high precision, and can be precisely controlled. Attached Figure Description

[0028] Figure 1 This is a front sectional view of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve of the present invention;

[0029] Figure 2 This is a top sectional view of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve of the present invention;

[0030] Figure 3 This is a schematic diagram of the flow area of ​​the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve in this invention.

[0031] In the diagram: 1. Servo motor; 2. Screw; 3. Internal oil passage; 3-1. Cross-shaped oil passage; 3-2. Central oil passage; 4. Right receiving hole; 5. Right jet nozzle; 6. Rotary valve core; 7. Valve body; 7-1. Plate; 7-2. Annular body; 8. Connecting pipe; 9. Dynamic sealing ring; 10. Chamber; 11. Left jet nozzle; 12. Left receiving hole; 13. Sealing ring; 14. Front jet nozzle; 15. Front receiving hole; 16. Rear jet nozzle; 17. Rear receiving hole; 18. First connecting oil passage; 19. Second connecting oil passage; 20. Right control oil passage; 21. Left control oil passage; 22. Return oil passage; 23. Front control oil passage; 24. Rear control oil passage; 25. Inlet oil passage; P is the inlet, T is the return port, and A and B are the control ports. Detailed Implementation

[0032] The features and performance of the present invention will be further described in detail below with reference to embodiments.

[0033] Example 1 of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve of the present invention:

[0034] This embodiment of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve consists of a servo motor, a rotary valve core, a valve body, jet nozzles, and receiving ports. There are four jet nozzles and four receiving ports, with two ports located in front of the two jet nozzles in their rotation direction and the other two ports located behind the other two jet nozzles in their rotation direction. By changing the relative positions of the jet nozzles and receiving ports, the kinetic energy and momentum of the hydraulic oil received by the receiving ports change, thereby changing the pressure and flow rate within the receiving ports. The relative positions of the jet nozzles and receiving ports are determined by the rotation angle of the rotary valve core, which is controlled by the servo motor. Therefore, by controlling the rotation angle of the servo motor, the flow rate and pressure control of the rotary direct-drive four-nozzle jet electro-hydraulic servo valve can be achieved.

[0035] Specifically, such as Figure 1 and Figure 2 As shown, the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve includes a valve body 7, a rotary valve core 6 disposed within the valve body 7, and a rotary power source mounted on the valve body 7 and drivenly connected to the rotary valve core 6 to control the rotation angle of the rotary valve core 6. In this embodiment, the rotary power source is a servo motor 1. The valve body 7 includes a bottom plate 7-1 and an annular body 7-2 connected to the plate 7-1. The upper end of the valve body 7 is an open end. The servo motor 1 is mounted on the open end of the valve body 7 by screws 2. The servo motor 1 and the valve body 7 together form a chamber 10 in which the rotary valve core 6 is disposed. To ensure sealing, a sealing ring 13 is provided between the servo motor 1 and the valve body 7.

[0036] like Figure 1 and Figure 2As shown, the valve body 7 is provided with an oil inlet channel 25 and four control oil channels. The oil inlet channel 25 is located at the center of the plate 7-1, and its port forms the oil inlet P. The four control oil channels all extend vertically and are respectively the front control oil channel 23, the rear control oil channel 24, the left control oil channel 21, and the right control oil channel 20. The four control oil channels are all located within the plate 7-1 and the annular body 7-2, and are evenly distributed in a circle. Among them, the rear control oil channel 24 and the right control oil channel 20 are connected by a first connecting oil channel 18 provided within the plate 7-1. The first connecting oil channel 18 is L-shaped and includes two straight oil channels. The rear control oil channel 24 and the right control oil channel 20 have a control oil port on the valve body 7, namely the control oil port B. The control oil port B is also the lower port of the right control oil channel 20.

[0037] Similarly, the left control oil passage 21 and the front control oil passage 23 are connected by a second connecting oil passage 19 located within the plate 7-1. The second connecting oil passage 19 is L-shaped and includes two straight oil passages. The left control oil passage 21 and the front control oil passage 23 also have another control port on the valve body 7, namely control port A. Control port A is also the lower port of the left control oil passage 21. Additionally, the plate 7-1 is also provided with a return oil passage 22 that directly communicates with the chamber 10. The lower port of the return oil passage 22 constitutes the return oil port T.

[0038] like Figure 1 and Figure 2 As shown, four receiving holes are provided on the inner wall of the valve body 7: a front receiving hole 15, a rear receiving hole 17, a left receiving hole 12, and a right receiving hole 4. All four receiving holes extend radially along the valve body 7 and are evenly distributed circumferentially, with an included angle of 90 degrees between adjacent receiving holes. Each receiving hole is connected to a corresponding control oil passage; that is, the front receiving hole 15 is connected to the front control oil passage 23, the rear receiving hole 17 is connected to the rear control oil passage 24, the left receiving hole 12 is connected to the left control oil passage 21, and the right receiving hole 4 is connected to the right control oil passage 20.

[0039] like Figure 1 and Figure 2 As shown, the rotary valve core 6 has an internal oil passage 3, which includes a cross-shaped oil passage 3-1 and a central oil passage 3-2 connected to the center of the cross-shaped oil passage 3-1. The rotary valve core 6 has a connecting structure that connects the internal oil passage 3 and the oil inlet channel 25. The connecting structure is located at the end of the central oil passage 3-2, specifically a connecting pipe 8. The upper end of the connecting pipe 8 is welded and fixed to the rotary valve core 6, and the lower end extends into the oil inlet channel 25 and is sealed to the oil inlet channel 25 through a dynamic sealing ring 9.

[0040] The rotary valve core 6 is also provided with four oil spraying structures that are connected to the internal oil passage 3 and used for oil spraying. In this embodiment, the oil spraying structure is a jet nozzle installed on the rotary valve core 6. The four jet nozzles are respectively connected to the four branch oil passages of the cross-shaped oil passage 3-1. The four jet nozzles are the front jet nozzle 14, the rear jet nozzle 16, the left jet nozzle 11 and the right jet nozzle 5. The four jet nozzles are all connected to the rotary valve core 6 by threads and are evenly distributed in a circle. The included angle between adjacent jet nozzles is 90 degrees.

[0041] The four jet nozzles correspond one-to-one with the four receiving holes. The axes of the receiving holes and the jet nozzles are not concentric, but they are at the same height. Taking the clockwise rotation direction of the rotary valve core 6 as a reference, the right receiving hole 4 and the rear receiving hole 17 are located on the opposite side of the right jet nozzle 5 and the rear jet nozzle 16, respectively, that is, on the rear side in the clockwise rotation direction. They can be temporarily called rear receiving holes because when the rotary valve core 6 rotates clockwise by a certain angle, the right receiving hole 4 and the rear receiving hole 17 are offset from the corresponding jet nozzles by a greater margin. The left receiving hole 12 and the front receiving hole 15 are located on the same side as the left jet nozzle 11 and the front jet nozzle 14, respectively, that is, on the front side in the clockwise rotation direction. They can be temporarily called front receiving holes because when the rotary valve core 6 rotates clockwise by a certain angle, the overlapping area of ​​the left receiving hole 12 and the front receiving hole 15 with the corresponding jet nozzles increases.

[0042] Conversely, if the rotary valve core 6 rotates counterclockwise, the right receiving hole 4 and the rear receiving hole 17 are located on the clockwise side, becoming the front receiving holes, while the left receiving hole 12 and the front receiving hole 15 are located on the counterclockwise side, becoming the rear receiving holes. In short, two of the four receiving holes are front receiving holes, and the other two are rear receiving holes. The two front receiving holes and the two rear receiving holes are connected through the corresponding control oil passages and connecting oil passages, respectively.

[0043] In operation, the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve supplies high-pressure oil to the rotary valve core 6 through the inlet P, inlet channel 25, and connecting pipe 8. The oil is then ejected at high speed from the jet nozzle and enters the receiving hole. Due to the impact, the oil pressure in the receiving hole increases, thus converting the oil's kinetic energy into pressure energy. For example... Figure 3 As shown, the area where the projected surfaces of the jet nozzle and the receiving hole intersect is the impact area of ​​the jet nozzle on the receiving hole (i.e., the flow area of ​​the receiving hole). High-speed hydraulic oil ejected from the left jet nozzle 11 impacts the left receiving hole 12, with an impact area of ​​A1. High-speed hydraulic oil ejected from the lower jet nozzle 14 impacts the lower receiving hole 15, with an impact area of ​​A2. A1 = A2. The receiving hole is connected to the control port A via an oil passage. High-speed hydraulic oil ejected from the right jet nozzle 5 impacts the right receiving hole 4, with an impact area of ​​B1. High-speed hydraulic oil ejected from the upper jet nozzle 16 impacts the upper receiving hole 17, with an impact area of ​​B2. B1 = B2. The receiving hole is connected to the control port B via an oil passage.

[0044] Furthermore, the distance between the jet nozzle and the inner wall of the valve body should be 1 to 2 times the diameter of the jet nozzle, specifically 1, 1.5, or 2 times. In other words, the distance from the jet nozzle to the corresponding receiving hole needs to be controlled within a suitable range. Too small a distance will generate a large back impact force, while too large a distance will affect the flow rate and pressure of the discharged fluid. Simultaneously, the receiving area of ​​the receiving hole should be 1 to 3 times the nozzle orifice area, specifically 1, 2, or 3 times. If the receiving area of ​​the receiving hole is too small or too large, the jet nozzle will be unable to change the flow rate and pressure difference of the control oil passage within a large angle range, resulting in poor performance.

[0045] The working principle of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve in this invention is as follows:

[0046] High-pressure hydraulic oil flows into the internal oil passage 3 of the rotary valve core through the internal connecting pipe 8, and is converted into high-speed flowing liquid through the jet nozzles, impacting the liquid in the receiving holes. In the neutral position, the overlapping area of ​​the four jet nozzles and the four receiving holes is the same, the pressure in the receiving holes is also equal, and the pressures at control ports A and B are also equal, with no pressure difference.

[0047] Assuming a counter-clockwise rotation command is given to servo motor 2, servo motor 2 will drive rotary valve core 6 to rotate counter-clockwise, and the four jet nozzles will also rotate counter-clockwise by an angle. At this time, the right receiving hole 4 and the rear receiving hole 17 are on the clockwise side, serving as the front receiving holes, while the left receiving hole 12 and the front receiving hole 15 are on the counter-clockwise side, serving as the rear receiving holes. Therefore, as... Figure 3 As shown, the impact area B2 of the rear jet nozzle 16 on the rear receiving hole 17 and the impact area B1 of the right jet nozzle 5 on the right receiving hole 4 increase, while the impact area A2 of the front jet nozzle 14 on the front receiving hole 15 and the impact area A1 of the left jet nozzle 11 on the left receiving hole 12 decrease. This results in increased high-speed oil received by the rear receiving hole 17 and the right receiving hole 4, leading to increased oil impact and increased pressure and flow rate at control port B. Conversely, decreased high-speed oil received by the front receiving hole 15 and the left receiving hole 12 results in decreased oil impact and decreased pressure and flow rate at control port A. Within a certain range, the larger the rotation angle of the servo motor 2, the greater the pressure difference between control ports A and B.

[0048] Assuming a clockwise rotation command is given to servo motor 2, the rotary valve core 6 will drive the four jet nozzles to rotate clockwise by an angle. At this time, the left receiving port 12 and the front receiving port 15 are located on the clockwise side, forming the front receiving port, while the right receiving port 4 and the rear receiving port 17 are located on the counter-clockwise side, forming the rear receiving port. The impact area B2 of the rear jet nozzle 16 on the rear receiving port 17 and the impact area B1 of the right jet nozzle 5 on the right receiving port 4 decrease, while the impact area A2 of the front jet nozzle 14 on the front receiving port 15 and the impact area A1 of the left jet nozzle 11 on the left receiving port 12 increase. The high-speed oil received by the rear receiving port 17 and the right receiving port 4 decreases, resulting in a decrease in the oil impact and a drop in pressure and flow rate at control port B. Conversely, the high-speed oil received by the front receiving port 15 and the left receiving port 12 increases, resulting in a greater oil impact and increased pressure and flow rate at control port A. Within a certain range, the larger the rotation angle of servo motor 2, the greater the pressure difference between control ports A and B.

[0049] The magnitude and polarity of the pressure difference between control port A and control port B are related to the magnitude and direction of the rotation angle of servo motor 2. Therefore, by controlling the servo motor, the output pressure and flow rate of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve can be controlled. Furthermore, for the actuator connected to the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve, such as a hydraulic cylinder, control ports A and B are connected to the rod-side and rodless-side chambers of the hydraulic cylinder, respectively. The movement and speed of the hydraulic cylinder's extension rod can be controlled in different directions by varying the pressure difference between control ports A and B.

[0050] The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve designed in this invention has the following advantages compared with existing jet-type electro-hydraulic servo valves: 1. It is a single-stage direct-acting electro-hydraulic servo valve, without a spool valve, resulting in a simple structure, reduced costs, fewer parts, fewer potential failure points, and higher reliability. 2. The jet nozzles have a larger orifice diameter, making them less prone to clogging by particles and other impurities in the oil, providing stronger anti-contamination performance and higher reliability. 3. The four jet nozzles correspond to four receiving holes, resulting in a large flow rate and flexible arrangement, improving the utilization rate of the jet oil and reducing mid-position leakage flow. 4. The four jet nozzles are symmetrically distributed, resulting in balanced radial force and lower hydraulic torque compared to traditional rotary spool valves. 5. It uses a standard servo motor as the electro-mechanical conversion element, providing stronger load capacity. Feedback is achieved through the encoder integrated into the servo motor, facilitating digital control and convenient maintenance. 6. The absence of a spool valve with high machining requirements, combined with the large diameter of the jet nozzles and receiving holes, reduces machining requirements, lowers the overall cost of the electro-hydraulic servo valve, and makes it suitable for factory use.

[0051] Therefore, the electro-hydraulic servo valve designed in this invention has significant advantages such as simple structure, high efficiency, low processing cost, strong anti-pollution performance, high reliability, and convenient maintenance and application.

[0052] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve: the form of the rotary power source can be different, such as a torque motor, hydraulic motor, pneumatic motor or stepper motor.

[0053] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve: the structure of the valve body can be different. For example, the valve body end is provided with an end plate, and the valve body itself can form a chamber. In this case, the output shaft of the rotary power source passes through the valve body and is connected to the rotary valve core for transmission.

[0054] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve, the form of the connecting structure can be different. For example, when a connecting pipe is fixed on the valve body, the connecting structure on the rotary valve core is a connecting port for inserting the connecting pipe and sealingly engaging with the connecting pipe.

[0055] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve: depending on the actual dimensions of the valve core and valve core, the orifice area of ​​the receiving hole can be slightly smaller than the nozzle area of ​​the jet nozzle or slightly larger than three times the nozzle area of ​​the jet nozzle. Of course, the distance between the jet nozzle and the inner wall of the valve body can also be slightly smaller than one time the jet nozzle diameter or slightly larger than two times the jet nozzle diameter.

[0056] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve: depending on actual needs, each control oil passage can have a control oil port, and each control oil port needs to be connected to the actuator.

[0057] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve: the internal oil passage structure of the valve core can be different. Instead of the four branch oil passages being straight cross-shaped oil passages, they can be arc-shaped or have bends.

[0058] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve: the first connecting oil passage and the second connecting oil passage can also be set in the annular body, or connected to the control oil passage through an external oil pipe. In this case, the shape of the valve body is not limited to the form of a plate or annular body, for example, it can be composed only of annular body.

[0059] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve: the four receiving holes and the four jet nozzles may not be evenly distributed in a circle, that is, the included angle between adjacent receiving holes and the included angle between adjacent jet nozzles may not be 90 degrees, for example, it may be 60 degrees or other suitable degrees.

[0060] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve: the number of receiving holes and jet nozzles can each be only two, in which case there are also only two control oil passages. In use, one receiving hole is the front receiving hole, and the other is the rear receiving hole. Of course, depending on actual needs, six receiving holes and six jet nozzles can also be provided, with three of the six receiving holes being the front receiving holes and the other three being the rear receiving holes.

[0061] In other embodiments of the rotary direct-drive multi-nozzle jet electro-hydraulic servo valve: the oil injection structure on the rotary valve core can also be in other forms, such as directly using the outlet of the internal oil passage as the nozzle, and the nozzle forming the oil injection structure.

[0062] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. The scope of patent protection of the present invention shall be determined by the claims. Similarly, any equivalent structural changes made based on the description and drawings of the present invention shall also be included within the scope of protection of the present invention.

Claims

1. A rotary direct-drive multi-nozzle jet electro-hydraulic servo valve, characterized in that, The valve body (7) includes a valve core (6) located inside the valve body (7) and having an internal oil passage, and a rotational power source mounted on the valve body (7) and connected to the rotary valve core (6) to control the rotation angle of the rotary valve core (6). The valve body (7) is provided with an oil inlet channel (25) and at least two control oil passages. The rotary valve core is provided with a connecting structure that connects the internal oil passage and the oil inlet channel, as well as an even number of oil spraying structures that connect to the internal oil passage and are used for oil spraying. There is a distance between the oil spraying structures and the inner wall of the valve body. When in use, high-pressure hydraulic oil flows into the internal oil passage through the oil inlet channel and is sprayed out through all the oil spraying structures. The bottom of the valve body is provided with a connection to the inner cavity of the valve body. The valve body (7) has a return oil passage. The inner wall of the valve body (7) is provided with receiving holes that are connected to the corresponding control oil passage and correspond one-to-one with the injection structure. Each receiving hole is not concentric with the axis of the corresponding injection structure, but at the same height. When each receiving hole is in use, at least one receiving hole is located on the front side of the rotation direction of the corresponding injection structure, and at least one receiving hole is located on the rear side of the rotation direction of the corresponding injection structure. When the rotary valve core rotates a certain angle, the overlapping area of ​​the receiving hole on the front side of the rotation direction and the corresponding injection structure increases, and the overlapping area of ​​the receiving hole on the rear side of the rotation direction and the corresponding injection structure decreases. In the neutral position, the overlapping area of ​​each receiving hole and the corresponding injection structure is the same.

2. The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve according to claim 1, characterized in that, The receiving hole located on the front side of the rotation direction of the fuel injection structure is defined as the front receiving hole, and the receiving hole located on the rear side of the rotation direction of the fuel injection structure is defined as the rear receiving hole. There are at least two front receiving holes and at least two rear receiving holes. The control oil passages corresponding to the at least two front receiving holes are connected through the first connecting oil passage (18), and the control oil passages corresponding to the at least two rear receiving holes are connected through the second connecting oil passage (19).

3. The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve according to claim 2, characterized in that, The valve body (7) includes a plate (7-1) and an annular body (7-2) connected to the plate (7-1). The control oil passage is located in the plate (7-1) and the annular body (7-2). The first connecting oil passage (18) and the second connecting oil passage (19) are both located in the plate (7-1). The first connecting oil passage (18) and the second connecting oil passage (19) each include at least one straight oil passage.

4. The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve according to any one of claims 1 to 3, characterized in that, All receiving holes and all oil spraying structures are evenly distributed around the circumference.

5. The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve according to claim 4, characterized in that, There are four receiving holes and four oil injection structures. The internal oil passage (3) includes a cross-shaped oil passage (3-1) and a central oil passage (3-2) connected to the center of the cross-shaped oil passage (3-1). The four oil injection structures are located at the outlet of the cross-shaped oil passage (3-1) and the connecting structure is located at the end of the central oil passage (3-2).

6. The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve according to any one of claims 1 to 3, characterized in that, The oil injection structure is a jet nozzle installed on the rotary valve core (6), and the distance between the jet nozzle and the inner wall of the valve body (7) is 1 to 2 times the diameter of the jet nozzle.

7. The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve according to any one of claims 1 to 3, characterized in that, The oil injection structure is a jet nozzle installed on the rotary valve core (6), and the orifice area of ​​the receiving hole is 1 to 3 times the nozzle area of ​​the jet nozzle.

8. The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve according to any one of claims 1 to 3, characterized in that, The connecting structure is a connecting pipe (8) with one end fixedly connected to the rotary valve core (6) and the other end extending into the oil inlet channel (25) of the valve body (7) and sealed to the oil inlet channel (25).

9. The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve according to any one of claims 1 to 3, characterized in that, One end of the valve body (7) is an open end. The rotational power source is installed at the open end of the valve body (7) and together with the valve body (7) forms a chamber (10) for setting the rotary valve core (6).

10. The rotary direct-drive multi-nozzle jet electro-hydraulic servo valve according to any one of claims 1 to 3, characterized in that, The rotational power source is a servo motor.

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