High-speed rotary valve and fluid high-speed transmission system
By designing a high-speed rotating valve with a multi-stage structure and adopting a rectangular valve port to reduce hydraulic impact, the problem of increasing eccentric pressure torque in the prior art is solved, and a more stable valve core start-up and operation is achieved.
Patent Information
- Application Number
- CN202421371123.1
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-06-14
- Publication Date
- 2025-02-18
- Estimated Expiration
- 2034-06-14
AI Technical Summary
The valve port size of the existing valve core is large, resulting in an increase in the additional torque of the eccentric pressure, causing an increase in the starting torque or a pulsating impact of the rotation torque, which can easily damage the components.
Design a high-speed rotating valve, whose valve body adopts a multi-stage structure, the valve core adopts a rectangular valve opening, and the rectangular valve opening is set as a flow hole to reduce hydraulic impact on the pressure side, thereby reducing rotational instability .
By reducing the moment of inertia of the valve core and reducing hydraulic impact, the start and operation stability of the valve core is improved, and is suitable for high pressure differential occasions.
Smart Images
Figure CN222502243U_ABST
Abstract
Description
Technical Field
[0001] The utility model belongs to the technical field of high-speed rotary valves, and in particular relates to a high-speed rotary valve and a high-speed fluid transmission system. Background Art
[0002] The existing valve core has a large circumferential opening of the valve port, and the sealing width without an opening also needs to be large. The axial diameter of the valve core needs to be large, and its own rotational inertia is relatively large, making it difficult to start or stop. This increases the requirements for the servo motor, and a high-inertia servo motor is required, which increases both the volume and power.
[0003] Since the valve core has a large diameter and a large radius, when it is about to be opened or closed, the force area on the high-pressure side also increases with the increase of the radius. Therefore, the additional torque of the eccentric pressure on the valve core increases, thereby increasing the starting torque or the pulsating impact of the rotational torque, which can easily damage components. Utility Model Content
[0004] The utility model provides a high-speed rotary valve and a high-speed fluid transmission system to solve the problem that the existing valve core and valve port are large in size, the additional torque of the eccentric pressure on the valve core increases, resulting in an increase in the starting torque or an increase in the pulsating impact of the rotating torque, causing easy damage to components.
[0005] The technical solution adopted by the utility model is:
[0006] A high-speed rotary valve, comprising a valve body and a valve core; the valve body has a first flow channel; the first flow channel has a first contraction section, a first convergence section, a second convergence section and a first diffusion section along the flow direction; an accommodating cavity for rotatably connecting the valve core is formed between the first convergence section and the second convergence section;
[0007] The valve core has rectangular valve openings on both sides along the fluid flow direction, forming a second flow channel of the valve core; the first flow channel and the second flow channel have a first working state that is interconnected and a second working state that is disconnected from each other, and the valve core is driven to rotate relative to the first converging section so that the first working state and the second working state are continuously switched with the rotation of the valve core.
[0008] The first contraction section has a first port for oil input that is away from the first convergence section along the fluid flow direction, and a second port that is connected to the rectangular opening of the first convergence section; the first contraction section has a trumpet-shaped structure in a projection perpendicular to the fluid flow direction, and the diameter gradually decreases from the first port side to the second port side.
[0009] The first converging section is a rectangular pipe having first rectangular openings on both sides along the fluid flow direction, the first rectangular opening of the first converging section on the side facing the valve core can be connected to the valve port of the valve core, and the first rectangular opening of the first converging section on the side facing the first contraction section can be connected to the first port of the first contraction section.
[0010] The second converging section is a rectangular pipe having second rectangular openings on both sides along the fluid flow direction; the second rectangular opening of the second converging section on the side facing the valve core can be connected to the valve port of the valve core, and the second rectangular opening of the second converging section on the side facing the first diffusion section can be connected to the first diffusion section.
[0011] The first diffusion section has a first rectangular opening along the fluid flow direction, which is connected to the second rectangular opening of the second converging section on the side facing the first diffusion section, and a second circular opening away from the second converging section for oil output; the first diffusion section gradually increases in size from the first opening side to the second opening side.
[0012] In the first working state, the first converging section, the second converging section and the first diffuser section constitute a Laval nozzle; or at least a portion of the first contraction section and the first converging section, the second converging section and the first diffuser section constitute a Laval nozzle.
[0013] The accommodating cavity is a cylindrical structure with a rectangular opening along the fluid flow direction, and the axis of the accommodating cavity is perpendicular to the fluid flow direction.
[0014] The first converging section and the second converging section are symmetrically distributed on two sides of the accommodating cavity along the fluid flow direction.
[0015] The valve opening of the valve core has a width of 4 mm and a length of 12 mm; the diameter of the second opening of the first diffusion section is not less than 12 mm.
[0016] A tangential slope between the first port and the second port of the first contraction section is greater than 3.375 times a density of liquid upstream of a throttling hole.
[0017] The present application also relates to a high-speed fluid transmission system of a high-speed rotary valve, comprising a pump source, a high-speed rotary valve at the pump source end, an arterial pipeline, a venous pipeline, an oil replenishment pipeline, a load A-port independent control valve block, a load B-port independent control valve block, a vacuum pump, a pressurized oil tank and a hydraulic actuator; the load A-port independent control valve block comprises a high-speed rotary valve A1, a high-speed rotary valve A2 and a high-speed rotary valve A3 connected in parallel to a first output end; the load B-port independent control valve block comprises a high-speed rotary valve B1, a high-speed rotary valve B2 and a high-speed rotary valve B3 connected in parallel to a second output end; the first output end is connected to the A port of the hydraulic actuator, and the second output end is connected to the B port of the actuator;
[0018] The pump source is connected to the high-speed rotary valve at the pump source end; the high-speed rotary valve at the pump source end is respectively connected to the high-speed rotary valve A1 of the load A port independent control valve block and the high-speed rotary valve B1 of the load B port independent control valve block through an arterial pipeline; the vacuum pump is respectively connected to the high-speed rotary valve A2 of the load A port independent control valve block and the high-speed rotary valve B2 of the load B port independent control valve block through a venous pipeline; the pressurized oil tank is respectively connected to the high-speed rotary valve A3 of the load A port independent control valve block and the high-speed rotary valve B3 of the load B port independent control valve block through the oil replenishment pipeline.
[0019] Due to the adoption of the above technical solution, the beneficial effects achieved by the utility model are as follows:
[0020] 1. The valve body of a high-speed rotary valve of the present application adopts a multi-section structure, wherein the first converging section and the second converging section adopt rectangular openings and are connected to the rectangular valve port of the valve core. By setting the rectangular valve port as a flow hole, it is not only easy to process, but also can reduce the rotational instability caused by the hydraulic shock on the pressure side, and has a wider applicability, especially in applications with high pressure difference.
[0021] 2. A high-speed rotary valve of the present application can make the valve core and the shaft diameter of the servo motor equivalent to Φ8. The valve core and the servo motor are connected by a shaft sleeve, and the valve core opening adopts an axial rectangular hole to ensure that the length L is long enough. Such a setting can not only increase the flow area and reduce leakage, but also reduce the rotational inertia of the valve core. BRIEF DESCRIPTION OF THE DRAWINGS
[0022] The drawings described herein are used to provide a further understanding of the present invention and constitute a part of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation on the present invention. In the drawings:
[0023] Figure 1 This is a schematic diagram of the internal structure of a valve body of a high-speed rotary valve in one embodiment of the utility model;
[0024] Figure 2 It is a structural schematic diagram of a valve core of a high-speed rotary valve in one embodiment of the utility model;
[0025] Figure 3 A structural principle diagram of a high-speed fluid transmission system of a high-speed rotary valve according to an embodiment of the present application;
[0026] In the figure,
[0027] 1 valve body, 2 valve core, 3 valve port, 4 first contraction section, 5 first convergence section, 6 accommodating chamber, 7 second convergence section, 8 first diffusion section, 9 pump source, 10 pump source end high-speed rotary valve, 11 load A port independent control valve block, 12 load B port independent control valve block, 13 arterial pipeline, 14 venous pipeline, 15 oil replenishment pipeline, 16 pressurized oil tank, 17 vacuum pump, 18 oil cylinder, 19 piston rod, 20 oil cylinder A port, 21 oil cylinder B port, 22 high-speed rotary valve A1, 23 high-speed rotary valve A2, 24 high-speed rotary valve A3, 25 high-speed rotary valve B1, 26 high-speed rotary valve B2, 27 high-speed rotary valve B3, 28 pressure pulsation sensor, 29 displacement sensor, 30 signal acquisition and controller. DETAILED DESCRIPTION
[0028] In order to more clearly illustrate the overall concept of the present application, a detailed description is given below in an illustrative manner in conjunction with the accompanying drawings.
[0029] In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present application is not limited to the specific embodiments disclosed below.
[0030] In addition, in the description of the present application, it should be understood that the terms "top", "bottom", "inside", "outside", "axial", "radial", "circumferential", etc., indicating orientations or positional relationships are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.
[0031] In this application, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection, an electrical connection, or a communication; it can be a direct connection, or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.
[0032] In the present application, unless otherwise clearly specified and limited, the first feature "above" or "below" the second feature may be that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. In the description of this specification, the description with reference to the terms "implementation method", "example", "one embodiment", "example" or "specific example" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in an appropriate manner in any one or more embodiments or examples.
[0033] Example 1
[0034] The present application relates to a high-speed rotary valve, such as Figure 1-2 As shown, it includes a valve body 1 and a valve core 2; the valve body 1 has a first flow channel; the first flow channel has a first contraction section 4, a first convergence section 5, a second convergence section 7 and a first diffusion section 8 along the flow direction; a receiving chamber 6 for rotatably connecting the valve core 2 is formed between the first convergence section 5 and the second convergence section 7; the valve core 2 has rectangular valve ports 3 on both sides along the fluid flow direction, forming a second flow channel of the valve core 2; the first flow channel and the second flow channel have a first working state that is interconnected and a second working state that is disconnected from each other, and the valve core 2 is driven to rotate or swing relative to the first convergence section 5, so that the first working state and the second working state are continuously switched with the rotation or swing of the valve core 2.
[0035] The circumferential opening of the valve port 3 of the traditional valve core 2 is large, and the sealing width without opening also needs to be large. The shaft diameter of the valve core 2 needs to be large, and its own rotational inertia is relatively large, which is not easy to start or stop, resulting in increased requirements for the servo motor. It must be a high-inertia servo motor, and the volume and power will increase. Since the valve core 2 has a large diameter and a large radius, when it is about to be opened or closed, the force area on the high-pressure side also increases with the increase of the radius. Therefore, the additional torque of the eccentric pressure on the valve core 2 increases, thereby causing an increase in the starting torque or a pulsating impact of the torque, which is easy to damage components.
[0036] The present application designs a slender structure of the valve core 2, and adopts an easily processed rectangular strip opening as the valve port 3, so as to reduce the rotation instability problem caused by the hydraulic impact on the pressure side, and is applied to high pressure difference occasions. In order to reduce leakage, the diameter D of the valve core 2 should not be too large, and the gap between the valve sleeve and the valve core 2 should not be too large, but the length L can be increased, so the valve core 2 is equal to the shaft diameter Φ8 of the servo motor, and the valve core 2 and the servo motor are connected by a shaft sleeve. The opening of the valve core 2 adopts an axial rectangular hole to ensure that the length L is long enough, so that not only the flow area can be increased and leakage can be reduced, but also the rotational inertia of the valve core 2 can be reduced.
[0037] The fluid first passes through the first contraction section 4, at which time the fluid is compressed and enters the first convergence section 5, and is output to the second convergence section 7 through the first convergence section 5 through the rectangular valve port 3 of the valve core 2, and the fluid is discretized from the second convergence section 7 through the first diffusion section 8, so that the fluid forms a high-pressure jet.
[0038] As a preferred embodiment, Figure 1 As shown, the first contraction section 4 has a first port for oil input away from the first convergence section 5 along the fluid flow direction, and a second port connected to the rectangular opening of the first convergence section 5; the first contraction section 4 has a trumpet-shaped structure in the projection perpendicular to the fluid flow direction, and the diameter gradually decreases from the first port side to the second port side.
[0039] The diameter of the first port of the first contraction section 4 is larger than that of the second port of the first contraction section 4. The first port serves as the input end of the fluid. The volume of the fluid is continuously compressed in the first contraction section 4 through the first port with a larger diameter, and then enters the second port. The first port is circular in shape, and the second port is rectangular in shape. The projection of the first contraction section 4 on the cross section is a trumpet-shaped structure, so that the first contraction section 4 forms a hyperbolic compression form, further realizing that during the flow of the fluid, the density of the fluid is gradually compressed and the pressure increases.
[0040] As a preferred embodiment, the first converging section 5 is a rectangular pipe having first rectangular openings on both sides along the fluid flow direction, the first rectangular opening of the first converging section 5 on the side facing the valve core 2 can be connected to the valve port 3 of the valve core 2, and the first rectangular opening of the first converging section 5 on the side facing the first contraction section 4 can be connected to the first port of the first contraction section 4.
[0041] It should be noted that the size and shape of the first rectangular opening are adapted to the shape and size of the second port of the first contraction section 4, so that the fluid can smoothly pass through the second port and the first rectangular opening of the first convergence section 5 facing the first contraction section 4 to enter the first convergence section 5, and then enter the valve port 3 through the first rectangular opening of the first convergence section 5 facing the accommodating chamber 6.
[0042] As a preferred embodiment, the second converging section 7 is a rectangular pipe having second rectangular openings on both sides along the fluid flow direction; the second rectangular opening of the second converging section 7 on the side facing the valve core 2 can be connected to the valve port 3 of the valve core 2, and the second rectangular opening of the second converging section 7 on the side facing the first diffusion section 8 can be connected to the first diffusion section 8.
[0043] It should be noted that the second converging section 7 has the same structure as the first converging section 5, and the second converging section 7 and the first converging section 5 are symmetrically distributed on both sides of the accommodating chamber 6. The second rectangular opening of the second converging section 7 facing the valve core 2 is used to communicate with the valve core 2 so that the fluid passing through the valve port 3 can smoothly enter the second rectangular opening. The size of the valve port 3 of the valve core 2 can be smaller than the size of the first rectangular opening or the second rectangular opening; the second rectangular opening of the second converging section 7 facing the first diffusion section 8 is adapted to the shape and size of the first opening of the first diffusion section 8, so that the fluid can smoothly enter the first diffusion section 8 through the second converging section 7.
[0044] As a preferred embodiment, the first diffusion section 8 has a first rectangular opening along the fluid flow direction, which is connected to the second rectangular opening of the second converging section 7 on the side facing the first diffusion section 8, and a second circular opening away from the second converging section 7 for oil output; the first diffusion section 8 gradually increases in size from the first opening side to the second opening side.
[0045] The first diffuser 8 is a conical structure as a whole, and the size of the first opening to the second opening gradually increases, the purpose is to achieve the density opening of the fluid entering from the first opening and outputting the liquid through the second opening, the cross-sectional area of the fluid increases, and it flows out in a radial high-pressure jet. The first opening of the first diffuser 8 is rectangular, the second opening of the first diffuser 8 is circular, and the inner wall surface of the first diffuser 8 is smoothly transitioned from the first opening to the second opening. Moreover, the second opening is designed to be circular to facilitate connection with the downstream arterial pipeline 13.
[0046] As a preferred embodiment, in the first working state, the first converging section 5, the second converging section 7 and the first diffuser section 8 constitute a Laval nozzle; or at least a portion of the first contraction section 4 and the first converging section 5, the second converging section 7 and the first diffuser section 8 constitute a Laval nozzle.
[0047] It should be noted that the present application does not impose any specific restrictions on the composition of the Laval tube, and any of the following embodiments may be adopted:
[0048] Embodiment 1: The first converging section 5, the second converging section 7 and the first diverging section 8 constitute a Laval nozzle.
[0049] Embodiment 2: At least a portion of the first contraction section 4, the first convergence section 5, the second convergence section 7 and the first diffusion section 8 form a Laval nozzle.
[0050] In actual production applications, the technical solutions disclosed in the above two embodiments can be selected according to the requirements of the actual application scenario and the size restrictions of the valve body 1 and the valve core 2, and the structure in the solution can be adaptively adjusted.
[0051] As a preferred embodiment, the accommodating chamber 6 is a cylindrical structure with a rectangular opening along the fluid flow direction, and the axis of the accommodating chamber 6 is perpendicular to the fluid flow direction.
[0052] The accommodating chamber 6 is used to accommodate the valve core 2, and the valve core 2 is a cylindrical structure. The valve core 2 needs to rotate or swing in the accommodating chamber 6. Therefore, the accommodating chamber 6 is designed as a cylindrical structure, and because the fluid of the first converging section 5 needs to flow into the second converging section 7 through the valve port 3, the accommodating chamber 6 needs to have corresponding openings corresponding to the first converging section 5 and the second converging section 7. The shape of the opening is rectangular. The accommodating chamber 6 is coaxially arranged with the valve core 2 and its axial direction is perpendicular to the flow direction of the fluid.
[0053] One end of the valve core 2 is connected to the driving member, and the rotation or swing of the valve core 2 is achieved through the driving action of the driving member. The present application does not specifically limit the type and mechanism of the driving member. As a preferred embodiment of the present application, the driving member can preferentially select a servo motor. Compared with other ordinary motors, the servo motor has a fast response speed, high precision, stable operation, strong adaptability, and strong overload resistance.
[0054] As a preferred implementation, the first converging section 5 and the second converging section 7 are symmetrically distributed on both sides of the accommodating cavity 6 along the fluid flow direction.
[0055] In order to keep the fluid in and out of the valve port 3 in a relatively stable state, the first converging section 5 and the second converging section 7 on both sides of the accommodating chamber 6 are designed to have the same structure, so that the fluid entering the first converging section 5 passes through the valve port 3 and the second converging section 7 to maintain a stable flow rate.
[0056] As a preferred implementation, the valve port 3 of the valve core 2 has a width of 4 mm and a length of 12 mm; and the diameter of the second opening of the first diffusion section 8 is not less than 12 mm.
[0057] Specifically, preferably, in order to ensure that the servo motor adopts low inertia, the valve core 2 should also be made into a slender structure like the rotating shaft of the low inertia servo motor. Then, according to the above valve core 2 diameter and the above low inertia servo motor diameter Φ8, L≈8mm can be obtained, and according to L=X≈2δ≈0.67d, the throttle hole diameter of the circular hole can be obtained as d=8 / 0.67=11.9mm. For a circular hole, the opening is large and the shaft diameter is easy to become larger. Therefore, the opening of the low inertia valve core 2 should adopt a long hole, and its hydraulic diameter should be equivalent to the d of the circular hole. For the long hole a*b, the hydraulic equivalent diameter d=4R=4A / (a+b)=4a*b / (a+b)=11.9mm, and the gap a=4mm, then the length b=11.9mm / 4 / (1-11.9 / 4 / 4)=11.6≈12mm, so the valve port 3 is designed to be 12mm in length and 4mm in width. The valve core 2 designed in this application can be used to discretize the high-pressure oil being transported, can drive the natural frequency between the output end and the receiving end, and can increase the transmission speed of the discrete flow.
[0058] The tangential slope between the first port and the second port of the first contraction section 4 is greater than 3.375 times the density of the liquid upstream of the throttling hole.
[0059] A hyperbolic compression form is formed between the first port and the second port of the first contraction section 4, so that the density of the fluid is compressed during the flow of the fluid, and the density of the fluid is released when it is output from the first diffusion section 8. By making the tangential slope between the first port and the second port greater than 3.375 times the density of the liquid upstream of the throttle hole, it is possible to ensure that the compression rate of the fluid density upstream of the valve core 2 is greater than 3.375 times the density of the fluid downstream, so that the requirement of sending out can be met.
[0060] Example 2
[0061] The present application also relates to a high-speed fluid transmission system of a high-speed rotary valve, such as Figure 3 As shown, it includes a pump source 9, a high-speed rotary valve 10 at the pump source end, an arterial pipeline 13, a venous pipeline 14, an oil replenishment pipeline 15, a load A port independent control valve block, a load B port independent control valve block, a vacuum pump 17, a pressurized oil tank 16 and a hydraulic actuator; the load A port independent control valve block includes a high-speed rotary valve A122, a high-speed rotary valve A223 and a high-speed rotary valve A324 connected in parallel to the first output end; the load B port independent control valve block includes a high-speed rotary valve B125, a high-speed rotary valve B226 and a high-speed rotary valve B327 connected in parallel to the second output end; the first output end is connected to the A port of the hydraulic actuator, and the second output end is connected to the B port of the actuator;
[0062] The pump source 9 is connected to the high-speed rotary valve 10 at the pump source end; the high-speed rotary valve 10 at the pump source end is respectively connected to the high-speed rotary valve A122 of the load A port independent control valve block and the high-speed rotary valve B125 of the load B port independent control valve block through the arterial pipeline 13; the vacuum pump 17 is respectively connected to the high-speed rotary valve A223 of the load A port independent control valve block and the high-speed rotary valve B226 of the load B port independent control valve block through the venous pipeline 14; the pressurized oil tank 16 is respectively connected to the high-speed rotary valve A324 of the load A port independent control valve block 11 and the high-speed rotary valve B327 of the load B port independent control valve block through the oil replenishment pipeline 15.
[0063] It is worth noting that the actuator preferably uses a cylinder, and a hydraulic pump can also be used, without any specific limitation here.
[0064] High-speed rotary valve A223 and high-speed rotary valve B226 are used to connect the venous pipeline 14, and vacuumize the oil cylinder 18 through the venous pipeline 14; high-speed rotary valve A324 and high-speed rotary valve B327 are used to connect with the oil replenishment pipeline 15, and the oil replenishment pipeline 15 is used to prepare before the piston rod 19 is extended or retracted to prevent vacuum negative pressure in the oil cylinder 18, and high-speed rotary valve A122 and high-speed rotary valve B125 are used to connect with the arterial pipeline 13; wherein high-speed rotary valve A122 , high-speed rotary valve A223 and high-speed rotary valve A324 are commonly connected to the first output end, and connected to the cylinder A port 20 through the first output end, high-speed rotary valve B125, high-speed rotary valve B226 and high-speed rotary valve B327 are commonly connected to the second output end, and connected to the cylinder B port 21 through the second output end, oil is input through the cylinder A port 20, and the cylinder B port 21 releases oil to achieve retraction of the piston rod 19, and pressure is released through the cylinder A port 20, and pressure is increased at the cylinder B port 21 to achieve extension of the piston rod 19.
[0065] As a preferred embodiment, the high-speed fluid transmission system also includes a signal acquisition and controller 30, a pressure pulsation sensor 28 and a displacement sensor 29; wherein the signal acquisition and controller 30 is connected to the arterial pipeline 13, the displacement sensor 29 and the pressure pulsation sensor 28, for collecting signals and controlling the pipeline, wherein the pressure pulsation sensor 28 is connected to the arterial pipeline 13, the displacement sensor 29 is connected to the piston rod 19 for detecting the displacement of the piston rod 19, and the pressure pulsation sensor 28 is respectively connected to the connecting ends of the arterial pipeline 13 and the high-speed rotary valve A122 and the high-speed rotary valve B125.
[0066] The working principle of the fluid high-speed transmission system is as follows:
[0067] Before the piston rod 19 can extend, it needs to be prepared: first, the valve 10H is rotated at a high speed at the pump source end. h The natural frequency ω0 of the oil in the arterial pipeline 13 is increased to a base pressure of 20 MPa in the arterial pipeline 13. At the same time, since the cylinder B port 21 may be the vacuum negative pressure in the venous pipeline 14, it is necessary to first replenish oil to the load B port independent control valve block, and open the high-speed rotary valve B327 to replenish oil to the load B port independent control valve block through the high-speed rotary valve B327; in order to overcome the back pressure of the cylinder A port 20, open the high-speed rotary valve B327 and at the same time open the high-speed rotary valve A223 of the load A port independent control valve block, so that the high-speed rotary valve A223 is connected to the vacuum negative pressure in the venous pipeline 14 to achieve pressure relief, and use the negative pressure to assist the piston rod 19 to prepare for the next extension action;
[0068] When the piston rod 19 is extended: the high-speed rotary valve A223 is opened, the high-speed rotary valve B125 is opened, and the oil enters the cylinder B port 21 through the arterial pipeline 13 and the high-speed rotary valve B125 from the high-speed rotary valve 10 at the pump source end. When the base pressure of the arterial pipeline 13 rises to 20MPa (the controller collects sensor data), the high-speed rotary valve B125 is opened. The rotation frequency ω of the high-speed rotary valve B125 is calculated based on the displacement of the piston rod 19 and historical data to obtain the oil volume in the cylinder B port 21 pipeline and the oil cylinder 18, the current pressure and other data, and the natural frequency ω of the oil in the arterial pipeline 13 0， According to a certain boost step size (for example, 0.5MPA), the frequency ω B1 At the same time, the pump source end high-speed rotary valve 10 connected to the pump source 9 is rotated at a frequency of ω B1 The phase error is adjusted according to the sensor data and the controller algorithm. At the same time, the back pressure of the cylinder A port 20 is still maintained to open the high-speed rotary valve A223, connecting the vacuum negative pressure in the venous tube to relieve pressure, and the negative pressure can assist the extension of the piston rod 19.
[0069] When preparing for retraction before the piston rod 19 is retracted: first, at the pump source end, the valve 10H is rotated at a high speed. h The natural frequency ω0 of the oil in the arterial pipeline 13 is increased to a base pressure of 20 MPa in the arterial pipeline 13. At the same time, since the cylinder A port 20 may be the vacuum negative pressure in the venous pipeline 14, it is necessary to first replenish oil to the load A port independent control valve block, and open the high-speed rotary valve A324 to replenish oil to the load A port independent control valve block 11 through the high-speed rotary valve A324; in order to overcome the back pressure of the cylinder B port 21, the high-speed rotary valve A324 is opened while the high-speed rotary valve B226 of the load B port independent control valve block is opened, so that the high-speed rotary valve B226 is connected to the vacuum negative pressure in the venous pipeline 14 to achieve pressure relief, and the negative pressure is used to assist the piston rod 19 to prepare for the next retraction action;
[0070] When the piston rod 19 retracts: the high-speed rotary valve B226 opens, the high-speed rotary valve A122 opens, and the oil enters the cylinder A port 20 through the arterial pipeline 13 and the high-speed rotary valve A122 from the high-speed rotary valve 10 at the pump source end. When the base pressure of the arterial pipeline 13 rises to 20MPa (the controller collects sensor data), the high-speed rotary valve A122 is opened. The rotation frequency ω of the high-speed rotary valve A122 is calculated based on the displacement of the piston rod 19 and historical data to obtain the oil volume in the cylinder A port 20 pipeline and the cylinder 18, the current pressure and other data, and based on the natural frequency ω of the oil in the arterial pipeline 13 0， According to a certain boost step size (for example, 0.5MPA), the frequency ω B1 At the same time, the pump source end high-speed rotary valve 10 connected to the pump source 9 is rotated at a frequency of ω B1The phase error is adjusted according to the sensor data and the controller algorithm. At the same time, the back pressure of the cylinder B port 21 is still maintained to open the high-speed rotary valve B226, connecting the vacuum negative pressure in the venous tube to relieve pressure, and the negative pressure can assist the extension of the piston rod 19.
Claims
1. A high-speed rotary valve, characterized in that: It comprises a valve body and a valve core; the valve body has a first flow channel; the first flow channel has a first contraction section, a first convergence section, a second convergence section and a first diffusion section along the flow direction; an accommodating cavity for rotatably connecting the valve core is formed between the first convergence section and the second convergence section; The valve core has rectangular valve openings on both sides along the fluid flow direction, forming a second flow channel of the valve core; the first flow channel and the second flow channel have a first working state that is interconnected and a second working state that is disconnected from each other, and the valve core is driven to rotate relative to the first converging section so that the first working state and the second working state are continuously switched with the rotation of the valve core.
2. A high-speed rotary valve as claimed in claim 1, characterized in that: The first contraction section has a first port for oil input that is away from the first convergence section along the fluid flow direction, and a second port that is connected to the rectangular opening of the first convergence section; the first contraction section has a trumpet-shaped structure in a projection perpendicular to the fluid flow direction, and the diameter gradually decreases from the first port side to the second port side.
3. A high-speed rotary valve as claimed in claim 2, characterized in that: The first converging section is a rectangular pipe having first rectangular openings on both sides along the fluid flow direction, the first rectangular opening of the first converging section on the side facing the valve core can be connected to the valve port of the valve core, and the first rectangular opening of the first converging section on the side facing the first contraction section can be connected to the first port of the first contraction section.
4. A high-speed rotary valve as claimed in claim 3, characterized in that: The second converging section is a rectangular pipe having second rectangular openings on both sides along the fluid flow direction; the second rectangular opening of the second converging section on the side facing the valve core can be connected to the valve port of the valve core, and the second rectangular opening of the second converging section on the side facing the first diffusion section can be connected to the first diffusion section.
5. A high-speed rotary valve as claimed in claim 4, characterized in that: The first diffusion section has a first rectangular opening along the fluid flow direction, which is connected to the second rectangular opening of the second converging section on the side facing the first diffusion section, and a second circular opening away from the second converging section for oil output; the first diffusion section gradually increases in size from the first opening side to the second opening side.
6. A high-speed rotary valve as claimed in claim 1, characterized in that: In the first working state, the first converging section, the second converging section and the first diffuser section constitute a Laval nozzle; or at least a portion of the first contraction section and the first converging section, the second converging section and the first diffuser section constitute a Laval nozzle.
7. A high-speed rotary valve as claimed in claim 1, characterized in that: The accommodating cavity is a cylindrical structure with a rectangular opening along the fluid flow direction, and the axis of the accommodating cavity is perpendicular to the fluid flow direction.
8. A high-speed rotary valve as claimed in claim 1, characterized in that: The first converging section and the second converging section are symmetrically distributed on two sides of the accommodating cavity along the fluid flow direction.
9. A high-speed rotary valve as claimed in claim 5, characterized in that: The valve opening of the valve core has a width of 4 mm and a length of 12 mm; the diameter of the second opening of the first diffusion section is not less than 12 mm.
10. A high-speed fluid transmission system based on a high-speed rotary valve according to any one of claims 1 to 9, characterized in that: It includes a pump source, a high-speed rotary valve at the pump source end, an arterial pipeline, a venous pipeline, an oil replenishment pipeline, a load A port independent control valve block, a load B port independent control valve block, a vacuum pump, a pressurized oil tank and a hydraulic actuator; the load A port independent control valve block includes a high-speed rotary valve A1, a high-speed rotary valve A2 and a high-speed rotary valve A3 connected in parallel to the first output end; the load B port independent control valve block includes a high-speed rotary valve B1, a high-speed rotary valve B2 and a high-speed rotary valve B3 connected in parallel to the second output end; the first output end is connected to the A port of the hydraulic actuator, and the second output end is connected to the B port of the actuator; The pump source is connected to the high-speed rotary valve at the pump source end; the high-speed rotary valve at the pump source end is respectively connected to the high-speed rotary valve A1 of the load A port independent control valve block and the high-speed rotary valve B1 of the load B port independent control valve block through an arterial pipeline; the vacuum pump is respectively connected to the high-speed rotary valve A2 of the load A port independent control valve block and the high-speed rotary valve B2 of the load B port independent control valve block through a venous pipeline; the pressurized oil tank is respectively connected to the high-speed rotary valve A3 of the load A port independent control valve block and the high-speed rotary valve B3 of the load B port independent control valve block through the oil replenishment pipeline.