High-response servo valve

Abstract

The utility model discloses a high-response servo valve, which relates to the technical field of rotary direct-drive servo valves and comprises a valve body, a valve core arranged in the valve body and a valve sleeve surrounding the valve core. Liquid flow channels for oil to flow through are formed in the valve body and arranged in a layered mode, oil supply ports and / or oil return ports are symmetrically formed in the ends, close to the valve sleeve, of the liquid flow channels, at least two sets of through grooves communicated with the inner wall and the outer wall are formed in the valve sleeve, and the through grooves conduct oil in the oil supply ports into the valve sleeve and conduct oil in the valve sleeve to the oil return ports. The distance between the inner walls of the through grooves is gradually reduced from the side close to the valve body to the side close to the valve element. By arranging the layered liquid flow channels, force finally acting on the valve element is evenly dispersed, the oil supply ports of the liquid flow channels of the same layer are symmetrically formed in the valve sleeve, the axial torque finally acting on the valve element is further counteracted, and the response speed of the servo valve is increased.

Description

Technical Field

[0001] This utility model relates to the field of rotary direct drive servo valve technology, and in particular to a high-response servo valve. Background Technology

[0002] With the continuous advancement of modern industrial technology, servo valves, as crucial control components in hydraulic systems, have been widely applied in many high-precision control fields. Traditional servo valves typically combine motor drive with mechanical transmission systems (such as gears, levers, etc.), transmitting the motor's power to the valve core via mechanical transmission to achieve precise control of fluid flow and pressure. However, traditional servo valves suffer from a series of problems, including complex structure, response delay, large size, and low energy efficiency, limiting their application in fields with high requirements for size, weight, response speed, and energy efficiency.

[0003] As a new type of servo valve, the rotary direct-drive servo valve directly drives the valve core with a motor, eliminating the traditional mechanical transmission part and achieving high control precision and response speed. However, in order to obtain high control precision and response speed, a series of problems have arisen, such as lower flow rate, greater weight, and larger size. Therefore, it is imperative to improve the rotary direct-drive servo valve to increase its flow rate, reduce its weight, and even reduce its size while ensuring good control precision and response speed, so as to be more widely applicable to various high-performance application scenarios. Summary of the Invention

[0004] The main objective of this invention is to propose a high-response servo valve, which aims to improve the flow rate of a rotary direct-drive servo valve while further enhancing its response speed.

[0005] To achieve the above objectives, the present invention proposes a high-response servo valve, which includes a valve body, a valve core disposed within the valve body, and a valve sleeve surrounding the valve core and disposed within the valve body.

[0006] The valve body has a liquid flow channel for oil circulation, the liquid flow channel is arranged in layers, and the liquid flow channel has a symmetrically arranged oil supply port and / or oil return port at the end near the valve sleeve. The valve sleeve has at least two sets of through grooves that connect the inner and outer walls. The through grooves guide the oil in the oil supply port to the inside of the valve sleeve and guide the oil in the valve sleeve to the oil return port. The distance between the inner walls of the through grooves gradually decreases from the side near the valve body to the side near the valve core.

[0007] In one embodiment, the through grooves are evenly arranged around the valve sleeve, and the plane of each set of through grooves is perpendicular to the axial extension line of the valve sleeve, with the spacing between two adjacent sets of through grooves being 0.5 mm to 50 mm.

[0008] In one embodiment, the same set of through slots has the same size, and adjacent sets of through slots have an angular offset, which ranges from 0° to 90°.

[0009] In one embodiment, the number of adjacent sets of through slots is the same, and their size and shape are identical.

[0010] In one embodiment, at least one of the number, size, and shape of two adjacent sets of through slots is different.

[0011] In one embodiment, the included angle formed by the through groove relative to the inner wall extension surfaces on both sides ranges from 0° to 60°.

[0012] In one embodiment, the valve sleeve is slidably fitted with the valve core, and the inner wall and outer surface of the valve sleeve are provided with pressure equalization grooves between two adjacent sets of through grooves, and / or the inner wall and outer surface of the valve sleeve are provided with pressure equalization grooves between each set of through grooves.

[0013] In one embodiment, the gap between the valve core and the valve sleeve is 0 μm-25 μm.

[0014] In one embodiment, the oil supply port and / or oil return port of the liquid flow channel in the same layer correspond to the same group of through slots opened on the valve sleeve, and the number of through slots in the same group is greater than or equal to the sum of the number of oil supply ports and the number of oil return ports of the liquid flow channel at the corresponding level of the group of through slots.

[0015] In one embodiment, the liquid flow channel includes a control port for controlling the flow direction of the oil, the oil supply ports of the same level liquid flow channel are radially symmetrically arranged around the valve sleeve, the oil return ports of the same level liquid flow channel are radially symmetrically arranged around the valve sleeve, and the control ports of the same level liquid flow channel are radially symmetrically arranged around the valve sleeve.

[0016] In one embodiment, an oil supply port, a control port, and an oil return port are provided on the same layer of liquid flow channel, wherein the three are arranged at intervals, and the oil supply ports, oil return ports, and control ports of all layers are independent of each other and the same type of oil ports are interconnected.

[0017] In one embodiment, only an oil supply port and a control port are provided on the same layer of liquid flow channel, or only an oil return port and a control port are provided on the same layer of liquid flow channel. The oil supply port and the control port are spaced apart, the oil return port and the control port are spaced apart, and the two layers of liquid flow channels with only an oil supply port and a control port and the two layers with only an oil return port and a control port are connected through the control port.

[0018] In one embodiment, at least one set of guide grooves are provided around the valve core. The guide grooves in the same set are of the same size and are radially evenly distributed on the valve core. Adjacent sets of guide grooves are offset by an angle, which ranges from 0° to 90°.

[0019] In one embodiment, the number of adjacent groups of guide channels is the same, and the size and shape of adjacent groups of guide channels are the same.

[0020] In one embodiment, at least one of the number, size, and shape of two adjacent sets of guide channels is different.

[0021] In one embodiment, the opening of the guide groove is a plane, and the plane is concave relative to the outer surface of the valve core at that location.

[0022] In one embodiment, the valve sleeve and the valve body are respectively provided with a positioning component for cooperating use, which is used to define the corresponding position of the through groove on the valve sleeve and the oil supply port of the liquid flow channel.

[0023] In one embodiment, the valve body is provided with a limiting structure to restrict the rotation angle of the valve core.

[0024] In one embodiment, the high-response servo valve further includes a servo motor that drives the valve core to move. The servo motor includes an internal rotor that is integrally connected to the valve core. The rotor is a regular polygonal structure or a circular structure, wherein the number of sides of the regular polygon is 2N+2, and N≥1.

[0025] In one embodiment, the connection end of the valve core and the rotor and / or the rotor is hollow, and the end face of the opposite end of the rotor is provided with a connection groove. The inner wall of the connection groove is provided with a plurality of machining grooves, which are used to further connect and fix the valve core and the rotor to other structures through the machining grooves.

[0026] The technical solution of this utility model sets up layered liquid flow channels, and then acts on the valve core through the through grooves opened on the valve sleeve. This makes the force of the oil acting on the valve core evenly distributed, rather than acting uniformly in a very small area of ​​the valve core. Moreover, the oil supply ports of the same layer of liquid flow channels are symmetrically arranged on the valve sleeve, so that the forces acting on the valve sleeve and even the same area of ​​the valve core in different directions cancel each other out, reducing the axial torque on the valve core. Specifically, the setting of the spacing between the inner walls of the through grooves on the valve sleeve gradually decreasing from the side closer to the valve body to the side closer to the valve core reduces or even completely eliminates the oil vortex on the outer wall of the valve sleeve when the oil flows through the through grooves, thereby reducing the energy loss of the valve body. At the same time, the oil pressure flowing through the valve core is consistent, making the force on the valve core more balanced, further canceling the axial torque on the valve core and promoting the response speed of the servo valve. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of this utility model 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 only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0028] Figure 1 A schematic diagram of the servo valve structure of an embodiment of the high-response servo valve provided by this utility model;

[0029] Figure 2 A schematic diagram of the liquid flow channel in one embodiment of the high-response servo valve provided by this utility model;

[0030] Figure 3 A cross-sectional view of the liquid flow channel in one embodiment of the high-response servo valve provided by this utility model;

[0031] Figure 4 A cross-sectional view of the valve core and valve sleeve in one embodiment of the high-response servo valve provided by this utility model;

[0032] Figure 5 A schematic diagram of the valve core and rotor in another embodiment of the high-response servo valve provided by this utility model;

[0033] Figure 6 A cross-sectional view of the valve body and valve sleeve in another embodiment of the high-response servo valve provided by this utility model;

[0034] Figure 7 A schematic diagram of the valve sleeve and positioning assembly in another embodiment of the high-response servo valve provided by this utility model;

[0035] Figure 8 A schematic diagram of the valve body in another embodiment of the high-response servo valve provided by this utility model;

[0036] Figure 9 A schematic diagram of the two-layer oil passage connecting the valve core at different angles in the high-response servo valve provided by this utility model.

[0037] Figure 10 A schematic diagram of the first layer of oil passage in the high-response servo valve provided by this utility model;

[0038] Figure 11 A structural deformation diagram of the first layer oil passage in the high-response servo valve provided by this utility model;

[0039] Figure 12 A schematic diagram of the second oil passage in the high-response servo valve provided by this utility model.

[0040] Explanation of icon numbers:

[0041] 1. High-response servo valve;

[0042] 11. Valve body; 12. Valve core; 13. Valve sleeve; 14. Positioning assembly; 15. Servo motor;

[0043] 111. Liquid flow channel; 112. Limiting structure; 121. Flow guide groove; 131. Through groove; 132. Pressure equalizing groove; 141. Positioning groove; 142. Positioning ball; 151. Rotor;

[0044] 1111, Oil supply port; 1511, Connecting groove; 1512, Machining groove.

[0045] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0046] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0047] It should be noted that if any directional indication (such as up, down, left, right, front, back, etc.) is involved in the embodiments of this utility model, such directional indication is only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indication will also change accordingly. Unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to the internal connection of two components. For those skilled in the art, the specific meaning of the above terms in this application can be understood according to the specific circumstances.

[0048] Furthermore, if the embodiments of this utility model involve descriptions such as "first," "second," etc., these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Moreover, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element. Furthermore, the use of "and / or" or "and / or" throughout the text includes three parallel options; for example, "A and / or B" includes option A, option B, or options where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or cannot be implemented, it should be considered that such combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0049] With the continuous advancement of modern industrial technology, servo valves, as crucial control components in hydraulic systems, have been widely applied in many high-precision control fields. Traditional servo valves typically combine motor drive with mechanical transmission systems (such as gears, levers, etc.), transmitting the motor's power to the valve core via mechanical transmission to achieve precise control of fluid flow and pressure. However, traditional servo valves suffer from a series of problems, including complex structure, response delay, large size, and low energy efficiency, limiting their application in fields with high requirements for size, weight, response speed, and energy efficiency.

[0050] As a new type of servo valve, the rotary direct-drive servo valve directly drives the valve core with a motor, eliminating the traditional mechanical transmission part and achieving high control precision and response speed. However, in order to obtain high control precision and response speed, a series of problems have arisen, such as lower flow rate, greater weight, and larger size. Therefore, it is imperative to improve the rotary direct-drive servo valve to increase its flow rate, reduce its weight, and even reduce its size while ensuring good control precision and response speed, so as to be more widely applicable to various high-performance application scenarios.

[0051] This utility model proposes a high-response servo valve 1.

[0052] Please combine Figures 1-4In one embodiment of the present invention, the high-response servo valve 1 includes a valve body 11, a valve core 12 disposed in the valve body 11, and a valve sleeve 13 surrounding the valve core 12 and disposed in the valve body 11.

[0053] The valve body 11 has a liquid flow channel 111 for oil circulation. The liquid flow channel 111 is arranged in layers, and the liquid flow channel 111 has a symmetrically arranged oil supply port and / or oil return port at one end near the valve sleeve 13. The valve sleeve 13 has at least two sets of through grooves 131 that connect the inner and outer walls. The through grooves 131 guide the oil in the oil supply port to the inside of the valve sleeve 13 and guide the oil in the valve sleeve 13 to the oil return port. The distance between the inner walls of the through grooves 131 gradually decreases from the side near the valve body 11 to the side near the valve core 12.

[0054] Understandably, the spacing between the inner walls of the through groove 131 gradually decreases from the side closer to the valve body 11 to the side closer to the valve core 12. That is, the through groove 131 has a certain taper. The larger end of the groove receives the oil sprayed from the liquid flow channel 111 and balances the oil pressure in the through groove 131 before being sprayed onto the surface of the valve core 12 from the smaller end of the groove. At this time, the eddy current generated by the oil acting on the valve sleeve 13 and the valve core 12 is smaller, and the axial torque transmitted to the valve sleeve 13 and even the valve core 12 is smaller.

[0055] It should be noted that the layered arrangement of the liquid flow channel 111 means that the oil supply port 1111 end of the liquid flow channel 111 is arranged in multiple layers along the axial extension direction on the outer surface of the valve sleeve 13. Among them, the oil supply port 1111 of each layer of the liquid flow channel 111 is arranged radially symmetrically on the valve sleeve 13, so that when the hydraulic pressure is the same, the line connecting the points where the oil injected from the liquid flow channel 111 impacts the valve sleeve 13 forms a circle. Specifically, the plane where the circle is located is perpendicular to the axial extension direction of the valve sleeve 13.

[0056] Understandably, by designing the position of the oil supply port 1111 in each liquid flow channel 111, the overall force acting on the valve sleeve 13 after the oil flows out can cancel each other out. When the oil flows to the surface of the valve core 12 through the through groove 131, the axial torque on the valve core 12 can also be canceled out by the design of the through groove 131, and the total axial torque is zero.

[0057] Specifically, in the specific embodiment of this utility model, the oil supply port 1111 end of the liquid flow channel 111 is arranged in an axisymmetric manner. Through the axisymmetric arrangement, the forces of two opposite oil supply ports 1111 can be completely canceled out when the oil pressure is the same. That is, the number of oil supply ports 1111 in the same level is 2N, where N≥1.

[0058] More specifically, the arrangement of the liquid flow channels 111 outlets between different levels along the axial direction on the valve sleeve 13 can be equidistant or unequal; they can be located near the middle of the valve sleeve 13 or at both ends of the valve sleeve 13 along the axial direction. There are no restrictions here, and the actual production shall prevail.

[0059] In the embodiments of this utility model, through grooves 131 are evenly arranged around the valve sleeve 13, and the plane of each group of through grooves 131 is perpendicular to the axial extension line of the valve sleeve 13, and the distance between two adjacent groups of through grooves 131 is 0.5 mm-50 mm.

[0060] Understandably, the same set of through grooves 131 corresponds to multiple oil supply ports 1111 at the same level. In order to ensure that the axial torque of the oil sprayed from the oil supply port 1111 on the valve sleeve 13 can be canceled, the line connecting the points where the oil sprayed from the liquid flow channel impacts the valve sleeve 13 is a circle. The plane of this circle is perpendicular to the axial extension direction of the valve sleeve 13. The landing point of the oil on the valve sleeve 13 is also in the through groove 131 of the valve sleeve 13. Therefore, the plane of each set of through grooves 131 should also be perpendicular to the axial extension line of the valve sleeve 13.

[0061] Optionally, the spacing between two adjacent sets of through slots 131 can be 0.5 mm, 1.8 mm, 2.6 mm, 5.0 mm, 7.8 mm, 10 mm, 14.2 mm, 26.5 mm, 33.1 mm, 45.7 mm, or 50 mm.

[0062] Preferably, the spacing between two adjacent sets of through slots 131 is 0.5 mm to 10 mm.

[0063] In the embodiments of this utility model, the same group of through slots 131 have the same size, and adjacent groups of through slots 131 have an angular offset, the angular offset range being 0°-90°.

[0064] Optionally, in one embodiment of the present invention, the number of adjacent sets of through slots 131 is the same, and their size and shape are identical.

[0065] Alternatively, in another embodiment of the present invention, at least one of the number, size, and shape of two adjacent sets of through slots 131 is different.

[0066] Specifically, the outline shape of the through groove 131 can be triangular, circular, elliptical, or polygonal.

[0067] It should be noted that, based on the different shapes of the through grooves 131, the angle of the through grooves 131 can be adjusted accordingly, so that the arrangement of two adjacent sets of through grooves 131 can be made more compact without changing the size of the through grooves 131, thereby reducing the overall volume of the valve sleeve 13.

[0068] More specifically, the polygon includes regular quadrilaterals and skew quadrilaterals, specifically rectangles and squares.

[0069] Optionally, the angular offset between two adjacent sets of through slots 131 can be 0°, 5°, 10°, 23.5°, 30°, 45°, 67.5°, 81°, or 90°.

[0070] Specifically, the angular offset between two adjacent sets of through slots 131 is 0°-45°.

[0071] In an embodiment of this utility model, the number of through grooves 131 is greater than the number of oil inlets 1111 of the liquid flow channels 111 of the corresponding level of the group of through grooves 131, and the oil inlets 1111 of the liquid flow channels 111 of the same level correspond to the through grooves 131 of the same group opened on the valve sleeve 13.

[0072] Please combine Figure 1 , Figure 4 and Figure 5 In the embodiments of this utility model, the included angle formed by the through groove 131 relative to the inner wall extension surfaces on both sides ranges from 0° to 60°.

[0073] It should be noted that the included angle range mentioned here is also the taper range of the through groove 131. If the taper is too large, the shape and size of the outer wall of the through groove 131 will be difficult to control, and at the same time, the oil flow to the surface of the valve core 12 will be too small, affecting the practicality.

[0074] It can be seen that when the through groove 131 is circular, elliptical, triangular or non-regular polygonal, it is limited by the taper of the cone, the taper of the elliptical cone, the taper of the triangular pyramid and the range of the included angle formed by the extended surfaces of the opposite sides of the non-regular polygon, respectively.

[0075] Preferably, the included angle formed by the through groove 131 relative to the inner wall extension surfaces on both sides is in the range of 0°-35°.

[0076] Please combine Figures 5-8 In an embodiment of this utility model, the valve sleeve 13 and the valve body 11 are respectively provided with a positioning component 14 for cooperating use, which is used to limit the corresponding position of the through groove 131 on the valve sleeve 13 and the oil supply port 1111 of the liquid flow channel 111.

[0077] It should be noted that during the assembly process of the servo valve, assembly errors will affect the accuracy of the servo valve. The reduction in accuracy will lead to a reduction in the response speed of the servo valve. Therefore, in order to ensure a sufficiently excellent response speed, the accuracy requirements must be met.

[0078] Understandably, by setting up a positioning component 14 for use in conjunction with the valve, the valve sleeve 13 and valve body 11 are ensured to be installed in place during assembly through the mating relationship of the components, thus meeting the accuracy requirements.

[0079] Specifically, in this embodiment of the present invention, positioning notches are provided on both sides of at least one end face of the valve sleeve 13 and the inner wall of the valve body 11 at the same location. The positioning notches of the valve sleeve 13 and the valve body 11 at the same location define a positioning groove 141. A positioning ball 142 is provided in the positioning groove 141. When the valve sleeve 13 and the valve body 11 are fully engaged, the positioning ball 142 is adapted to the positioning groove 141 and abuts against the inner wall of the positioning groove 141. When the positions of the valve sleeve 13 and the valve body 11 are offset, the positioning ball 142 cannot be adapted to the positioning groove 141. At this time, the positioning ball 142 cannot fall into the positioning groove 141. The user can determine whether the valve sleeve 13 and the valve body 11 are installed in place by observing the state of the positioning ball 142.

[0080] In the embodiments of this utility model, the valve sleeve 13 is slidably fitted with the valve core 12, and the inner wall and outer surface of the valve sleeve 13 are provided with pressure equalization grooves 132 between two adjacent sets of through grooves 131, and / or the inner wall and outer surface of the valve sleeve 13 are provided with pressure equalization grooves 132 between each set of through grooves 131.

[0081] It should be noted that the pressure equalization groove 132 on the outer surface of the valve sleeve 13 is used to reduce oil leakage between the valve sleeve 13 and the valve body 11.

[0082] The pressure equalization groove 132 on the inner wall of the valve sleeve 13 is used to reduce the friction between the valve sleeve 13 and the valve core 12 and reduce oil leakage between the valve sleeve 13 and the valve core 12. This design can effectively prevent the valve core 12 from jamming.

[0083] Specifically, there can be multiple equalizing grooves 132 between two adjacent groups of through grooves 131, and / or between two adjacent through grooves 131 within the same group.

[0084] More specifically, the shape of each equalizing groove 132 is not limited and can be a straight line, a broken line, a curve, a graphic or a symbol.

[0085] Specifically, there is a gap between the valve core 12 and the valve sleeve 13, which ranges from 0 μm to 25 μm.

[0086] Understandably, when the valve sleeve 13 and the valve core 12 are in complete contact, the larger the contact area, the greater the friction, which will hinder the movement of the valve core 12, resulting in longer working time and even wear on the contact surface. Therefore, by opening a through groove 131 on the valve sleeve 13, a guide groove 121 on the valve core 12, and even a pressure equalization groove 132 on the inner wall of the valve sleeve 13, the oil flow can be guided and leakage can be prevented. At the same time, by controlling the size of multiple grooves, the contact area can be further reduced, so that the friction between the valve core 12 and the valve sleeve 13 is reduced to a suitable operating range.

[0087] It should be noted that the gap between the valve core 12 and the valve sleeve 13 should not be too large. An increased gap will increase oil leakage, and when the gap between the valve core 12 and the valve sleeve 13 is too large, it will reduce the space utilization rate, thereby increasing the overall size of the servo valve.

[0088] Specifically, in the specific embodiments of this utility model, the range of the gap is not explicitly limited, and is based on the actual required size.

[0089] Preferably, in a specific embodiment of this utility model, the gap between the valve core 12 and the valve sleeve 13 is in the range of 1 μm to 8 μm.

[0090] In an embodiment of this utility model, a limiting structure 112 is provided on the valve body 11 to limit the rotation angle of the valve core 12.

[0091] It should be noted that the limiting structure 112 is set on the valve body 11, giving the valve core 12 a range of rotation space. However, when the valve core 12 rotates beyond this range, it will hinder the rotation of the valve core 12, so that the maximum rotation angle of the valve core 12 is fixed. If the maximum rotation angle is exceeded, it will be blocked and thus stop rotating.

[0092] In an embodiment of this utility model, the high-response servo valve 1 further includes a servo motor 15 that drives the valve core 12 to move. The servo motor 15 includes a rotor 151 disposed inside. The rotor 151 is integrally connected to the valve core 12. The rotor 151 is a regular polygonal structure or a circular structure, wherein the number of sides of the regular polygon is 2N+2, and N≥1.

[0093] It should be noted that the valve core 12 and rotor 151 of a conventional rotary direct drive servo valve are detachably connected and require an additional mating structure to achieve the connection for further transmission.

[0094] The present invention integrates the valve core 12 and the rotor 151, which reduces the number of overall parts and improves the response speed of the servo valve.

[0095] Furthermore, the rotor 151 can be configured as a regular polygonal structure with an even number of sides, or the rotor 151 can be configured as a circular structure. When this type of structure is fixed, the opposite sides can be subjected to symmetrical forces, making the fixation more stable and thus improving the response speed.

[0096] In an embodiment of this utility model, the connection end of the valve core 12 and the rotor 151 and / or the rotor 151 is hollow. The end face of the opposite end of the rotor 151 is provided with a connection groove 1511. The inner wall of the connection groove 1511 is provided with a plurality of processing grooves 1512, which are used to further connect and fix the valve core 12 and the rotor 151 to other structures through the processing grooves 1512 after the valve core 12 and the rotor 151 are connected.

[0097] Optionally, other components, such as small components like magnets, can also be installed in the connecting slot 1511 to improve space utilization.

[0098] Specifically, the component is arranged symmetrically in the connecting groove 1511 to ensure that the axial torque of the rotor 151 is balanced during operation.

[0099] It should be noted that the connection end between the valve core 12 and the rotor 151 is hollow, and / or the rotor 151 is hollow, which helps to reduce the overall weight of the valve core 12 and the rotor 151 and thus reduce the moment of inertia, so as to obtain a higher response speed.

[0100] The rotor 151 has a connecting groove 1511 and a machining groove 1512 on its opposite end face. The machining groove 1512 can be further filled with adhesive or added with fixing structure after the rotor 151 is fixed, so that the connection is more stable and the response speed is further improved.

[0101] Specifically, when other small-volume components are installed in the connecting groove 1511, the components are fixed by filling the machining groove 1512 with adhesive or adding a fixing structure to prevent loosening and imbalance during operation.

[0102] Please combine Figure 1-5 , Figure 7 , Figures 10-12 In an embodiment of this utility model, at least one set of guide grooves 121 are provided around the valve core 12, and at least one of the guide grooves 121 spans two adjacent through grooves 131 in the same set to guide the liquid passage.

[0103] It should be noted that, since the oil supply port and / or oil return port of the liquid flow channel 111 in the same layer are opened on the valve sleeve 13 of the same group of through grooves 131, the number of through grooves 131 in the same group is greater than or equal to the sum of the number of oil supply ports and the number of oil return ports of the liquid flow channel 111 in the corresponding layer of the group of through grooves 131.

[0104] Specifically, the liquid flow channel 111 includes a control port for controlling the flow direction of the oil, and the control port spans two adjacent sets of through slots 131 to facilitate the liquid passage.

[0105] More specifically, the control port connects to two different sets of through channels 131, through which oil entering from one set of oil supply ports is guided to the other set of oil return ports, and then returns to the oil circulation through the liquid flow channel 111.

[0106] In the embodiments of this utility model, the oil supply ports of the same level liquid flow channel 111 are arranged radially symmetrically around the valve sleeve 13, the oil return ports of the same level liquid flow channel 111 are arranged radially symmetrically around the valve sleeve 13, and the control ports of the same level liquid flow channel 111 are arranged radially symmetrically around the valve sleeve 13.

[0107] In the embodiments of this utility model, the dimensions of the guide grooves 121 in the same group are consistent and they are radially evenly distributed on the valve core 12. There is an angular offset between two adjacent groups of guide grooves 121, and the offset angle range is 0°-90°.

[0108] It should be noted that after the oil flows out from the outlet end of the liquid flow channel 111, it enters the through groove 131 of the valve sleeve 13, and flows to the guide groove 121 corresponding to the valve core 12 after being squeezed, and then flows out of the valve sleeve 13 through the guide groove 121 connecting the two adjacent through grooves 131.

[0109] Optionally, in one embodiment of the present invention, the number of adjacent groups of guide grooves 121 is the same, and the size and shape of adjacent groups of guide grooves 121 are the same.

[0110] Alternatively, in another embodiment of the present invention, at least one of the number, size and shape of two adjacent sets of guide grooves 121 is different.

[0111] It should be noted that the number, size, and shape of the guide grooves 121 will affect the final size of the valve core 12, thereby indirectly affecting the overall structural size of the servo valve.

[0112] Understandably, by limiting the number, size, shape, and angular offset of the guide channels 121, the arrangement of the guide channels 121 can be controlled, making the arrangement of the guide channels 121 more compact, thereby reducing the volume of the valve core 12.

[0113] In an embodiment of this utility model, the opening of the guide groove 121 is a plane, and the plane is concave relative to the outer surface of the valve core 12 at that location.

[0114] It should be noted that the groove opening plane of the guide groove 121 is concave relative to the outer surface of the valve core 12, which can further reduce the contact area between the valve core 12 and the valve sleeve 13. In addition, the groove opening of the guide groove 121 is set in a planar form, which is convenient for processing, can improve processing efficiency, and at the same time control the mating dimensions between the guide groove 121 and the valve sleeve 13.

[0115] The technical solution of this utility model sets up layered liquid flow channels 111, and then acts on the valve core 12 through the through grooves 131 opened on the valve sleeve 13. This makes the force of the oil acting on the valve core 12 evenly distributed, instead of acting uniformly in a very small area of ​​the valve core 12. Moreover, the oil supply ports of the same layer of liquid flow channels 111 are symmetrically arranged on the valve sleeve 13, so that the forces acting on the valve sleeve 13 and even the same area of ​​the valve core 12 in different directions cancel each other out, reducing the axial torque on the valve core 12. Specifically, the setting of the inner wall spacing of the through grooves 111 on the valve sleeve 13 gradually decreasing from the side closer to the valve body 11 to the side closer to the valve core 12 reduces or even completely eliminates the oil vortex on the outer wall of the valve sleeve 13 when the oil flows through the through grooves 111, thereby reducing the energy loss of the valve body 11. At the same time, the oil pressure flowing through the valve core 12 is consistent, making the force on the valve core 12 more balanced, further canceling the axial torque on the valve core 12 and promoting the response speed of the servo valve.

[0116] Specifically, the guide groove 121 connects the two adjacent levels of the through groove 131 to form an oil circulation loop. When the oil enters through the through groove 131 on the valve sleeve 13, it acts on the valve core 12 and is discharged from the valve core 12 through the guide groove 121 on the valve core 12 from the adjacent level through groove 131. When oil leakage occurs in the valve body 11, the leaked oil is stored in the pressure equalization tank 132 to reduce the possibility of external leakage.

[0117] Define two interconnected liquid flow channels 111 as the first and second layers from bottom to top. The first layer is the oil inlet channel, and the second layer is the oil outlet channel.

[0118] In one embodiment, an oil supply port, a control port, and an oil return port are provided on the same layer of liquid flow channel 111, wherein the three are arranged at intervals, and the oil supply port, oil return port, and control port of all layers are independent of each other and the same type of oil port is interconnected.

[0119] Specifically, when the relative position of the valve core 12 and the valve sleeve 13 is zero, all the oil flowing out of the oil supply circuit acts directly on the valve core 12, and the guide groove 121 is not connected to the same group of through grooves 131, so there is no oil flow at this time.

[0120] When the valve core 12 rotates clockwise or counterclockwise relative to the valve sleeve 13 by a certain angle, the guide groove 121 and the through groove 131 are connected to the oil supply port and control port of the same level liquid flow channel 111, forming an oil circuit. The control port leads the oil out of the valve sleeve 13 and into the liquid flow channel 111 of other levels, while the oil of other levels is introduced into the valve core 12 of this level through the control port, guided by the guide groove 121 to the return port, and enters the oil circulation.

[0121] It can be seen that the larger the rotation angle of the valve core 12 relative to the valve sleeve 13, the greater the liquid flow rate. When the rotation angle of the valve core 12 relative to the valve sleeve 13 is the largest, the liquid flow rate reaches its maximum value.

[0122] In one embodiment, only an oil supply port and a control port are provided on the same layer of liquid flow channel 111, or only an oil return port and a control port are provided on the same layer of liquid flow channel 111. The oil supply port and the control port are arranged alternately, the oil return port and the control port are arranged alternately, and the two layers of liquid flow channels 111 with only an oil supply port and a control port and only an oil return port and a control port are connected through the control port.

[0123] Specifically, when the relative position of the valve core 12 and the valve sleeve 13 is zero, all the oil flowing out of the oil supply circuit acts directly on the valve core 12, and the guide groove 121 is not connected to the same group of through grooves 131, so there is no oil flow at this time.

[0124] Rotate the valve core 12 so that the guide groove 121 and the through groove 131 connect the oil supply port, control port and return port of multiple levels. The oil forms an oil circulation between at least two levels. At this time, the oil supply port and the return port are set in two different levels, one for oil supply and one for oil return to ensure smooth flow of oil circuit and sufficient liquid flow.

[0125] When the valve core 12 rotates clockwise relative to the valve sleeve 13 by a certain angle, the oil supply port of the valve core 12 in the first layer is connected to the control port 2, and the oil flowing out of the oil supply port is guided to the control port 2. After entering the liquid flow channel 111 through the control port 2, it flows to the control port 2 in the second layer, which is connected to it. After passing through the through groove 131 and the guide groove 121 in the second layer, it finally flows out of the valve sleeve 13 through the return oil port in the second layer.

[0126] When the valve core 12 rotates counterclockwise relative to the valve sleeve 13 by a certain angle, the oil supply port of the valve core 12 in the first layer is connected to the control port 1, and the oil flowing out of the oil supply port is guided to the control port 1. After entering the liquid flow channel 111 through the control port 1, it flows to the control port 1 in the second layer, which is connected to it. After passing through the through groove 131 and the guide groove 121 in the second layer, it finally flows out of the valve sleeve 13 through the return oil port in the second layer.

[0127] It can be seen that the larger the rotation angle of the valve core 12 relative to the valve sleeve 13, the greater the liquid flow rate. When the rotation angle of the valve core 12 relative to the valve sleeve 13 is the largest, the liquid flow rate reaches its maximum value.

[0128] It should be noted that when the overall structure of the servo valve is small, it usually only needs to circulate across two adjacent layers, and there will be no situation where it crosses multiple liquid flow channels 111. However, if there are design requirements that require increasing the volume of the servo valve, or if it is necessary to cross multiple liquid flow channels 111 at the same time, the connection of liquids in multiple liquid flow channels 111 can be achieved by changing the number of connected liquid flow channels 111. Correspondingly, the size of the liquid flow channel 111 will also be adjusted to ensure sufficient flow capacity. There is no absolute limitation here.

[0129] It should be understood that the terms "one embodiment" or "one example" throughout the specification mean that a specific feature, structure, or characteristic related to the embodiment is included in at least one embodiment of the present invention. Therefore, "in one embodiment" or "in one example" appearing throughout the specification do not necessarily refer to the same embodiment. Furthermore, these specific features, structures, or characteristics can be combined in any suitable manner in one or more embodiments. Those skilled in the art should also recognize that the embodiments described in the specification are optional embodiments, and the actions and modules involved are not necessarily essential to the present invention.

[0130] In various embodiments of this utility model, it should be understood that the sequence number of each process does not necessarily imply the order of execution. The execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of this utility model embodiment.

[0131] The flowcharts and block diagrams in the accompanying drawings illustrate the architecture, functionality, and operation of possible implementations of systems, methods, and computer program products according to various embodiments of this application. In this regard, each block in a flowchart or block diagram may represent a module, segment, or portion of code containing one or more executable instructions for implementing a specified logical function. It should also be noted that in some alternative implementations, the functions indicated in the blocks may occur in a different order than those indicated in the drawings. For example, two consecutively indicated blocks may actually be executed substantially in parallel, or they may sometimes be executed in reverse order, depending on the functions involved. It is particularly important to note that each block in a block diagram and / or flowchart, and combinations of blocks in block diagrams and / or flowcharts, can be implemented using a dedicated hardware-based system that performs the specified function or operation, or using a combination of dedicated hardware and computer instructions.

[0132] The above description is merely an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformations made based on the technical concept of the present utility model and the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. A high-response servo valve, characterized in that: The high-response servo valve includes a valve body, a valve core disposed within the valve body, and a valve sleeve surrounding the valve core and disposed within the valve body. The valve body has a liquid flow channel for oil circulation, the liquid flow channel is arranged in layers, and the liquid flow channel has a symmetrically arranged oil supply port and / or oil return port at the end near the valve sleeve. The valve sleeve has at least two sets of through grooves that connect the inner and outer walls. The through grooves guide the oil in the oil supply port to the inside of the valve sleeve and guide the oil in the valve sleeve to the oil return port. The distance between the inner walls of the through grooves gradually decreases from the side near the valve body to the side near the valve core.

2. The high-response servo valve as described in claim 1, characterized in that: The through grooves are evenly arranged around the valve sleeve, and the plane of each group of through grooves is perpendicular to the axial extension line of the valve sleeve. The distance between two adjacent groups of through grooves is 0.5 mm-50 mm.

3. The high-response servo valve as described in claim 1, characterized in that: The dimensions of the same set of through slots are the same, and there is an angular offset between adjacent sets of through slots, which ranges from 0° to 90°.

4. The high-response servo valve as described in claim 1, characterized in that: The number of adjacent sets of through slots is the same, and their size and shape are identical.

5. The high-response servo valve as described in claim 1, characterized in that: The number, size, and shape of any two adjacent sets of through slots are different.

6. The high-response servo valve as described in claim 1, characterized in that: The included angle formed by the through groove relative to the inner wall extension surfaces on both sides ranges from 0° to 60°.

7. The high-response servo valve as described in claim 1, characterized in that: The valve sleeve slides with the valve core, and the inner wall and outer surface of the valve sleeve are provided with pressure equalization grooves between two adjacent sets of through grooves, and / or the inner wall and outer surface of the valve sleeve are provided with pressure equalization grooves between each set of through grooves.

8. The high-response servo valve as described in claim 7, characterized in that: The gap between the valve core and the valve sleeve is 0µm-25µm.

9. The high-response servo valve as described in claim 1, characterized in that: The oil supply port and / or oil return port of the liquid flow channel in the same layer correspond to the same group of through slots opened on the valve sleeve. The number of through slots in the same group is greater than or equal to the sum of the number of oil supply ports and the number of oil return ports of the liquid flow channel in the corresponding layer of the group of through slots.

10. The high-response servo valve as described in claim 9, characterized in that: The liquid flow channel includes a control port for controlling the flow direction of the oil. The oil supply ports of the same level liquid flow channel are radially symmetrically arranged around the valve sleeve. The oil return ports of the same level liquid flow channel are radially symmetrically arranged around the valve sleeve. The control ports of the same level liquid flow channel are radially symmetrically arranged around the valve sleeve.

11. The high-response servo valve as described in claim 9, characterized in that: Oil supply port, control port and return port are set on the same liquid flow channel. The three are set at intervals. The oil supply port, return port and control port of all levels are independent of each other and the same type of oil port is interconnected.

12. The high-response servo valve as described in claim 9, characterized in that: Only an oil supply port and a control port are provided on the same layer of liquid flow channel, or only an oil return port and a control port are provided on the same layer of liquid flow channel. The oil supply port and the control port are set alternately, and the oil return port and the control port are set alternately. The two layers of liquid flow channels with only an oil supply port and a control port and the two layers with only an oil return port and a control port are connected through the control port.

13. The high-response servo valve as described in claim 1, characterized in that: At least one set of guide grooves are arranged around the valve core. The guide grooves in the same set are the same size and are evenly distributed radially on the valve core. There is an angular offset between adjacent sets of guide grooves, and the offset angle ranges from 0° to 90°.

14. The high-response servo valve as described in claim 13, characterized in that: The number of adjacent groups of guide channels is the same, and the size and shape of adjacent groups of guide channels are the same.

15. The high-response servo valve as described in claim 13, characterized in that: The number, size, and shape of any two adjacent sets of guide channels are different.

16. The high-response servo valve as described in claim 13, characterized in that: The opening of the guide groove is a plane, and the plane is concave relative to the outer surface of the valve core at that location.

17. The high-response servo valve as described in claim 1, characterized in that: The valve sleeve and valve body are respectively provided with a positioning component for use in defining the corresponding position of the through groove on the valve sleeve and the oil supply port of the liquid flow channel.

18. The high-response servo valve as described in claim 1, characterized in that: The valve body is provided with a limiting structure that restricts the rotation angle of the valve core.

19. The high-response servo valve as described in claim 1, characterized in that: The high-response servo valve also includes a servo motor that drives the valve core to move. The servo motor includes an internal rotor that is either a regular polygon or a circular structure, wherein the number of sides of the regular polygon is 2N+2, and N≥1.

20. The high-response servo valve as described in claim 18, characterized in that: The valve core and the rotor are connected at the connection end and / or the rotor is hollow. The end face of the opposite end of the rotor is provided with a connection groove. The inner wall of the connection groove is provided with multiple machining grooves, which are used to further connect and fix the valve core and the rotor to other structures through the machining grooves.

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