A magnetic armature assembly, solenoid valve, air suspension system, and vehicle

Abstract

This application relates to a magneto-armature assembly, a solenoid valve, an air suspension system, and a vehicle, including a moving iron core and a stop member. The moving iron core is configured to switch between a first state and a second state under the action of magnetic force. The stop member is directly connected to the moving iron core and is configured to move under the drive of the moving iron core to close or open the solenoid valve. When the moving iron core is in the first state, the solenoid valve is open; when the moving iron core is in the second state, the solenoid valve is closed. By directly connecting the moving iron core and the stop member, the coaxiality between the moving iron core and the stop member is improved, thereby reducing the possibility of jamming during movement. This, in turn, helps to improve the response speed of the solenoid valve, enabling it to achieve a faster opening and closing response under the action of a drive signal.

Description

Technical Field

[0001] This application relates to the field of electromagnetic operating valves, and more particularly to a magneto-armature assembly, a solenoid valve, an air suspension system, and a vehicle. Background Technology

[0002] An air suspension system is a technology that regulates vehicle suspension performance by adjusting the inflation and deflation of compressed air within air springs. This system typically includes air springs, an air compressor, an air tank, a control unit, and several control valve components. Among these, the solenoid valve, as a key component controlling airflow, regulates the internal air pressure of the air springs during system operation, thereby affecting the suspension stiffness and vehicle height adjustment.

[0003] However, in the existing technology, the solenoid valves used in air suspension systems are prone to unsmooth opening and closing during use, resulting in insufficient response speed. Utility Model Content

[0004] This application provides a magneto-armature assembly, a solenoid valve, an air suspension system, and a vehicle, which improves the response speed of the solenoid valve during use, thereby at least partially solving the above-mentioned technical problems.

[0005] To achieve the above objectives, according to a first aspect of this application, a magnetoarmature assembly is provided, comprising:

[0006] The moving iron core is configured to switch between a first state and a second state under the action of magnetic force; and

[0007] The stop element is directly connected to the moving iron core and is configured to move under the drive of the moving iron core to close or open the solenoid valve.

[0008] When the moving iron core is in the first state, the solenoid valve is open; when the moving iron core is in the second state, the solenoid valve is closed.

[0009] In some embodiments, the stop element is connected to the end of the moving iron core facing the stop element.

[0010] In some embodiments, the stop member is fixedly connected to the moving iron core.

[0011] In some embodiments, the stop member and the moving iron core are connected by interference fit and / or welding.

[0012] In some embodiments, in the moving direction of the stop member, at least one of the stop member and the moving iron core has a first pressure-bearing surface and a second pressure-bearing surface, wherein the force directions of the first pressure-bearing surface and the second pressure-bearing surface are their respective normal directions, and the fluid pressure acting on the first pressure-bearing surface and the second pressure-bearing surface are opposite in direction.

[0013] In some embodiments, the magnetoarmature assembly further includes a valve housing, wherein at least one of the moving iron core and the stop element is movably disposed in the valve housing to allow the moving iron core to switch between the first state and the second state.

[0014] In some embodiments, the valve housing has a first opening and a second opening;

[0015] When the moving iron core is in the first state, the first opening is connected to the second opening;

[0016] When the moving iron core is in the second state, the stop member closes the communication channel between the first opening and the second opening to block the connection between the first opening and the second opening.

[0017] In some embodiments, a balance chamber is formed between the side of the stop member opposite to the first opening and the valve housing, and the balance chamber is configured to communicate with a pressure source;

[0018] The first pressure-bearing surface is the end face of at least one of the stop member and the moving iron core that faces away from the first opening;

[0019] The second pressure-bearing surface is the end face of at least one of the stop member and the moving iron core facing the first opening.

[0020] In some embodiments, the stop element slides and seals against the valve housing, and the moving iron core is located in the balance chamber;

[0021] The first pressure-bearing surface is the end face of the stop member and the moving iron core that is away from the first opening;

[0022] The second pressure-bearing surface is the end face of the stop member and the moving iron core facing the first opening.

[0023] In some embodiments, the stop member is provided with a first through hole, which is used to connect the first opening with the balance chamber so that the pressure at the first opening forms a pressure source for the balance chamber.

[0024] In some embodiments, the moving iron core is provided with a second through hole that communicates with the first through hole.

[0025] In some embodiments, the area difference between the first pressure-bearing surface and the second pressure-bearing surface is equal to zero;

[0026] Alternatively, the area difference between the first pressure-bearing surface and the second pressure-bearing surface is greater than zero;

[0027] Alternatively, the area difference between the first pressure-bearing surface and the second pressure-bearing surface is less than zero.

[0028] In some embodiments, a first sealing portion is provided around the first opening, and the stop member includes a second sealing portion, wherein:

[0029] When the moving iron core is in the second state, the first sealing part and the second sealing part are sealed together, and the first through hole is connected to the first opening;

[0030] And / or, when the moving iron core is in the first state, the first sealing part and the second sealing part are separated, and the first opening and the first through hole are both connected to the second opening.

[0031] In some embodiments, a seal is provided between the stop element and the valve housing of the magneto-armature assembly.

[0032] In some embodiments, the seal is a sliding Glyd ring.

[0033] In some embodiments, the magnetoarmature assembly further includes an elastic element disposed between the moving iron core and the valve housing of the magnetoarmature assembly, so as to reset the moving iron core to the first state or the second state after the magnetic force is released.

[0034] In some embodiments, the valve housing includes a stationary iron core, and the elastic element is disposed between the moving iron core and the stationary iron core to allow the moving iron core to elastically reset. The moving iron core is configured to move in a direction close to or away from the stationary iron core under the action of magnetic force to switch between the first state and the second state.

[0035] In some embodiments, at least one of the moving iron core and the valve housing of the magneto-armature assembly is provided with a buffer member, which is used to buffer the moving iron core when it moves relative to the valve housing.

[0036] In some embodiments, the valve housing further includes a valve seat, with a first opening and a second opening of the valve housing located on the valve seat, and the valve seat and the stationary iron core of the valve housing engaging in a circumferential upper limit fit between the valve and the solenoid valve.

[0037] And / or, the valve housing further includes an iron core cover, the stationary iron core of the valve housing being fixedly connected to the iron core cover.

[0038] According to a second aspect of this application, a solenoid valve is provided, including the magneto-armature assembly described above.

[0039] In some embodiments, the solenoid valve further includes a coil assembly and a connector assembly;

[0040] The coil assembly is disposed on the outer periphery of the moving iron core and / or the stationary iron core of the magneto-armature assembly. A limiting structure is provided between the coil assembly and the plug-in assembly. The plug-in assembly and the coil assembly are engaged in a circumferential upper limit cooperation in the solenoid valve through the limiting structure.

[0041] In some embodiments, the solenoid valve further includes a housing, and at least one of the coil assembly and the plug assembly engages with the housing in a circumferentially upper limit of the solenoid valve.

[0042] In some embodiments, the housing is provided with an opening, and at least a portion of the limiting structure is located within the opening, such that the limiting structure and the housing engage in a circumferentially limiting fit with the solenoid valve.

[0043] In some embodiments, the housing is at least partially made of metal, and the pins of the coil assembly pass through the limiting structure to connect to the outside.

[0044] In some embodiments, the housing is provided with a limiting platform, and the stationary iron core abuts against the limiting platform to limit the position of the stationary iron core relative to the housing.

[0045] In some embodiments, the valve housing of the magnetoarmature assembly is provided with a stepped surface, and the coil assembly includes an abutment portion disposed near the center of the coil assembly and used to contact the stepped surface.

[0046] In some embodiments, the valve housing of the magneto-armature assembly is engaged with the coil assembly at the circumferential limit of the solenoid valve.

[0047] According to a third aspect of this application, an air suspension system is also provided, including the magneto-armature assembly described in the above-described technical solutions, or the solenoid valve described in the above-described technical solutions.

[0048] According to a fourth aspect of this application, a vehicle is also provided, including the magneto-armature assembly described in the above-described technical solutions, or the solenoid valve described in the above-described technical solutions, or the air suspension system described in the above-described technical solutions.

[0049] In the magnetoarmature assembly of this application embodiment, the moving iron core and the stop member are directly connected, thereby eliminating the need for intermediate components to connect the moving iron core and the stop member, which helps to reduce the complexity of the structural configuration. With this structure, the moving iron core and the stop member can reciprocate together along the same axis. Compared to a structural scheme that connects indirectly through intermediate components, this direct connection method can improve the coaxiality between the moving iron core and the stop member to a certain extent.

[0050] Improving coaxiality helps reduce the relative deviation between the moving iron core and the stop element during movement, thereby reducing the possibility of jamming during their movement. Because the movement of the moving iron core and the stop element is smoother, it helps improve their response speed, resulting in a faster opening and closing response of the solenoid valve under the action of the drive signal, and an overall improved response characteristic.

[0051] Other features and advantages of this application will be described in detail in the following detailed description section. Attached Figure Description

[0052] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0053] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings, wherein the same reference numerals in the following description denote the same parts.

[0054] Figure 1 This is a schematic diagram of the structure of the magnetoarmature assembly provided in an exemplary embodiment of this disclosure;

[0055] Figure 2 This is a cross-sectional view of the moving iron core in the magneto-armature assembly provided in the exemplary embodiments of this disclosure when it is in the first state;

[0056] Figure 3 This is a cross-sectional view of the moving iron core in the magneto-armature assembly provided in the exemplary embodiments of this disclosure when it is in the second state;

[0057] Figure 4 This is a cross-sectional view of the coil assembly and the plug-in assembly provided in an exemplary embodiment of this disclosure;

[0058] Figure 5 This is a schematic diagram of the structure of the coil assembly and the plug-in assembly provided in the exemplary embodiments of this disclosure;

[0059] Figure 6 This is a schematic diagram of the structure of the outer casing provided in an exemplary embodiment of this disclosure;

[0060] Figure 7 This is a cross-sectional view of the housing provided in an exemplary embodiment of this disclosure;

[0061] Figure 8 This is a schematic diagram of the structure of the solenoid valve provided in an exemplary embodiment of this disclosure;

[0062] Figure 9This is a cross-sectional view of the solenoid valve provided in the exemplary embodiment of this disclosure when the moving iron core is in the first state;

[0063] Figure 10 This is a cross-sectional view of the moving iron core in the solenoid valve provided in the exemplary embodiment of this disclosure when it is in the second state.

[0064] Explanation of reference numerals in the attached figures:

[0065] 10. Solenoid valve; 11. Coil assembly; 11a. Limiting structure; 11b. Abutment part; 12. Plug-in assembly; 13. Housing; 13a. Opening; 13b. Limiting platform; 100. Moving iron core; 110. Second through hole; 120. Buffer; 200. Stop element; 210. First pressure-bearing surface; 220. Second pressure-bearing surface; 230. First through hole; 240. Second sealing part; 250. Sealing element; 300. Valve body; 310. First opening; 320. Second opening; 321. First sealing part; 330. Balance chamber; 340. Stationary iron core; 341. Stepped surface; 350. Valve seat; 360. Iron core cover; 400. Elastic element. Detailed Implementation

[0066] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the protection scope of this application.

[0067] According to the first aspect of this application, referring to Figures 1 to 3 This disclosure provides a magnetoarmature assembly applied to a solenoid valve 10. Exemplarily, the solenoid valve 10 includes a coil assembly 11, which generates a magnetic field when energized to drive the components in the magnetoarmature assembly to move, thereby placing the solenoid valve 10 in a closed or open state.

[0068] The magnetoarmature assembly includes a moving iron core 100 and a stop / go element 200. The moving iron core 100 can move under the influence of a magnetic field, thereby switching its state. The moving iron core 100 has a first state and a second state. In the energized state, the electromagnetic coil generates a magnetic field, which exerts an attractive force on the moving iron core 100, causing it to move towards a magnetic component (e.g., a stationary iron core 340), thus switching between the first and second states.

[0069] It can be understood that the moving iron core 100, by forming a closed magnetic circuit with the stationary iron core 340, is attracted to a position close to the stationary iron core 340 under the action of magnetic force, thereby completing the switch from the first state to the second state. Correspondingly, under the conditions of power failure or weakening of magnetic force, the moving iron core 100 can return to the first state under the action of the elastic element 400 or other external forces. Through the above structure, the motion state of the moving iron core 100 can be controlled to switch according to the on / off state of the electromagnetic coil, thereby realizing the drive control of the stop element 200.

[0070] It should be noted that the moving iron core 100 is usually made of soft magnetic material so as to form an effective magnetic flux path under the action of electromagnetic force and have a high magnetic response speed.

[0071] In some embodiments, refer to Figure 1 , Figure 2 The stop-go component 200 is directly connected to the moving iron core 100, meaning that the stop-go component 200 and the moving iron core 100 can achieve an integrated or tightly fitted connection structure without the need for intermediate connecting parts. This connection method can be of various structural forms such as mechanical fixed connection, interference fit, and welding connection, thereby enabling the stop-go component 200 and the moving iron core 100 to achieve direct contact and rigid transmission in structure.

[0072] When the moving iron core 100 moves axially under magnetic drive, the stop member 200 moves synchronously under the drive of the moving iron core 100, thereby enabling the stop member 200 to open and close, thus opening or closing the solenoid valve 10. It can be understood that the design of the stop member 200 directly connecting to the moving iron core 100 eliminates the intermediate structures (such as connecting rods, plug-in parts, etc.) used in traditional solutions to connect the two, thereby reducing the number of components in the magnetoarms assembly. This structural simplification not only helps reduce the complexity of assembly and processing but also helps reduce assembly errors between the stop member 200 and the moving iron core 100, improving the coaxiality of the moving iron core 100 and the stop member 200.

[0073] The improvement of coaxiality has a positive impact on the dynamic performance of the solenoid valve 10. It helps to reduce the risk of jamming caused by eccentricity or tilting of the stop element 200 during movement, thereby making the opening and closing action of the solenoid valve 10 smoother and the response faster, which in turn helps to improve the response speed and stability of the solenoid valve 10.

[0074] In some embodiments, refer to Figure 2 , Figure 3When the moving iron core 100 is in the first state, the solenoid valve 10 is open. When the moving iron core 100 is in the second state, the solenoid valve 10 is closed. It can be understood that when the moving iron core 100 switches from the first state to the second state, or from the second state to the first state, under the action of magnetic force, the stop-flow component 200, as a structural component directly connected to the moving iron core 100, will move synchronously with the moving iron core 100, thereby opening or closing the solenoid valve 10. This structural method can avoid the response delay caused by multi-stage transmission, and helps to improve the response performance and control accuracy of the solenoid valve 10.

[0075] For example, to achieve automatic reset of the moving iron core 100 after the magnetic force is removed, an elastic element 400 can be connected to the moving iron core 100. The elastic element 400 can provide a restoring force after the moving iron core 100 loses its magnetic force, so as to drive the moving iron core 100 to a first state or a second state. The elastic element 400 can be a helical spring, a wave spring, or other components with rebound characteristics, and the specific structural form can be selected according to the application scenario.

[0076] It is understandable that in some application scenarios, to adapt to specific control logic or improve system reliability, the reset of the moving iron core 100 can also be achieved through manual operation. Furthermore, it can be combined with other electromagnetic control modules to guide the moving iron core 100 to reset via additional magnetic force. Since the methods for resetting the moving iron core 100 vary across different applications, this embodiment does not impose specific limitations. The reset method of the moving iron core 100 can be flexibly configured as needed to meet the response requirements and stability requirements of different solenoid valve 10 systems.

[0077] In some embodiments, refer to Figure 2 , Figure 3 The stop element 200 is connected to the end of the moving iron core 100 facing the stop element 200. This design allows for a corresponding reduction in the effective length of the stop element 200, thereby reducing the difficulty of precision control during manufacturing. The shorter structural dimensions not only reduce the likelihood of deflection or misalignment during processing but also improve positioning accuracy during assembly. Furthermore, shortening the length of the stop element 200 also enhances its rigidity and stability during movement.

[0078] In some embodiments, the stop member 200 is fixedly connected to the moving iron core 100. Exemplarily, the stop member 200 and the moving iron core 100 can be connected as a single unit by welding, interference fit, threaded connection, or other mechanical fastening methods. Using a fixed connection helps improve the assembly stability between the two, ensuring consistent movement during actual operation and preventing structural loosening caused by relative sliding or clearance fit.

[0079] With a fixed connection, the stop element 200 can move axially along with the moving iron core 100 more reliably, thus helping to maintain consistent response during the opening and closing of the solenoid valve 10. Simultaneously, the fixed connection structure also improves the coaxiality between the stop element 200 and the moving iron core 100, thereby reducing frictional resistance or motion jamming caused by axial misalignment to a certain extent, and enhancing the operational reliability and smooth operation of the magneto-armature assembly.

[0080] It is understood that the coaxiality mentioned in this embodiment refers to the fact that during the switching process between the first and second states, the moving iron core 100 moves basically along its own axis, while the movement trajectory of the stop member 200 must also remain on this axis. Maintaining the coaxiality of the moving iron core 100 and the stop member 200 helps reduce relative offset and radial oscillation, thereby reducing friction and wear between components, promoting smoother and more stable coordinated movement of the two, and thus improving the response speed and service life of the magnetoarmature assembly.

[0081] In some embodiments, the stop element 200 and the moving iron core 100 are connected by interference fit and / or welding. Interference fit enables a firm connection between the stop element 200 and the moving iron core 100 through mechanical fastening, which helps improve the fitting accuracy and structural stability between the two. Welding, on the other hand, forms an integrated structure through the metallurgical bonding of materials, further enhancing the strength and durability of the connection. The above connection methods can be used individually or in combination to meet the requirements of connection strength and processing technology in different application scenarios.

[0082] In some embodiments, refer to Figure 2 , Figure 3 In the moving direction of the stop member 200, at least one of the stop member 200 and the moving iron core 100 has a first pressure-bearing surface 210 and a second pressure-bearing surface 220. The force directions of the first pressure-bearing surface 210 and the second pressure-bearing surface 220 are their respective normal directions, and the fluid pressures acting on the first pressure-bearing surface 210 and the second pressure-bearing surface 220 are in opposite directions. Specifically, the direction of the fluid pressure on the first pressure-bearing surface 210 is opposite to the direction of the fluid pressure on the second pressure-bearing surface 220. This design causes the pressures between the first pressure-bearing surface 210 and the second pressure-bearing surface 220 to counteract or cancel each other out, thereby effectively reducing the magnetic force required to drive the moving iron core 100 to move.

[0083] It is understood that the first pressure-bearing surface 210 and the second pressure-bearing surface 220 mentioned in this application can refer to the actual physical surface of the stop member 200 and / or the moving iron core 100, or it can refer to the projected surface of the stop member 200 and / or the moving iron core 100 along the fluid pressure direction. When the surface of the stop member 200 and / or the moving iron core 100 has curvature changes, uneven structures, or other irregular shapes, for ease of description and analysis, the projected surface of the stop member 200 and / or the moving iron core 100 in the fluid pressure direction can be regarded as the first pressure-bearing surface 210 and the second pressure-bearing surface 220.

[0084] Specifically, the first pressure-bearing surface 210 and the second pressure-bearing surface 220 are respectively subjected to fluid pressure, and the directions of the forces are opposite. Since the pressures on the two pressure-bearing surfaces are mutually antagonistic, a resultant force is formed. The magnitude and direction of this resultant force depend on the area difference between the two surfaces, thereby determining the direction and extent of movement of the moving iron core 100.

[0085] When the surface areas of the two pressurized parts are equal, the forces exerted by the fluid pressures cancel each other out, and the moving iron core 100 remains stationary or in equilibrium. In this case, only a small external force is needed to move the moving iron core 100.

[0086] If there is a difference in the surface area of ​​the two pressurized surfaces, the larger pressurized surface will bear greater fluid pressure, thereby generating a driving force that propels the moving iron core 100 to move in a predetermined direction. At this time, the fluid pressure can assist the movement of the moving iron core 100 or help maintain the moving iron core 100 at a certain predetermined position.

[0087] By rationally designing and adjusting the area difference between the first pressure-bearing surface 210 and the second pressure-bearing surface 220, the response speed and stability of the moving iron core 100 can be precisely controlled. An appropriate area difference can improve the response speed of the moving iron core 100 and reduce inertial hysteresis.

[0088] Therefore, the design of the area difference between the first pressure-bearing surface 210 and the second pressure-bearing surface 220 helps to optimize the performance of the solenoid valve 10, achieving more precise control and higher stability. It can be understood that in this embodiment, the first pressure-bearing surface 210 and the second pressure-bearing surface 220 are subjected to the same fluid pressure as an example.

[0089] It can be understood that in the direction of movement of the moving iron core 100, the stop member 200 and / or the moving iron core 100 having a first pressure-bearing surface 210 and a second pressure-bearing surface 220 means that one of the first pressure-bearing surface 210 and the second pressure-bearing surface 220 is located on the upstream side in the direction of movement of the moving iron core 100, and the other surface is located on the downstream side.

[0090] In some embodiments, refer to Figure 2 , Figure 3The magnetoarmature assembly also includes a valve housing 300, with at least one of the moving iron core 100 and the stop element 200 movably disposed within the valve housing 300 to allow the moving iron core 100 to switch between a first state and a second state. As a structural support, the valve housing 300 provides a relatively fixed mounting base for the moving iron core 100 and the stop element 200, ensuring clear guidance and constraint on the movement path of the moving iron core 100 when switching between the first and second states, thus contributing to stable axial movement. By incorporating the valve housing 300, not only is the coaxiality of the moving iron core 100 and the stop element 200 improved during movement, but problems such as misalignment and jamming that may be caused by gaps or structural deviations between components are also mitigated, thereby enhancing the overall operational reliability and service life of the magnetoarmature assembly.

[0091] In some examples, the moving iron core 100 is slidably connected to the valve housing 300, and the stop element 200 is connected to the moving iron core 100, but the stop element 200 does not directly contact the valve housing 300. In some examples, the stop element 200 is slidably connected to the valve housing 300, and the moving iron core 100 is connected to the stop element 200, but there is no direct contact between the moving iron core 100 and the valve housing 300. In some examples, both the moving iron core 100 and the stop element 200 are slidably connected to the valve housing 300. These various slid connection methods all contribute to achieving reliable guidance and efficient drive of the moving iron core 100 within the valve housing 300, further ensuring the controllability and consistency of the movement of the magnetoarmature assembly during opening and closing.

[0092] In some embodiments, refer to Figure 2 , Figure 3 The valve body 300 has a first opening 310 and a second opening 320. When the moving iron core 100 is in the first state, the first opening 310 and the second opening 320 are connected. When the moving iron core 100 is in the second state, the stop member 200 closes the communication channel between the first opening 310 and the second opening 320, thereby blocking the flow between the first opening 310 and the second opening 320. When the moving iron core 100 is in the first state, a communication channel is formed between the first opening 310 and the second opening 320, allowing the medium to flow. When the moving iron core 100 is in the second state, the stop member 200 moves to a predetermined position under the drive of the moving iron core 100 and closes the communication channel, thereby blocking the flow path between the first opening 310 and the second opening 320. Through the above structural arrangement, the solenoid valve 10 can switch the medium flow state under different working states. This control method has the characteristics of compact structure and sensitive response, which helps to improve the system's adjustment accuracy and response speed.

[0093] For example, the pipeline to be controlled can be connected to the first opening 310 and the second opening 320, and the on / off state of the moving iron core 100 can be used to control the pipeline. For example, the first opening 310 can be connected to one pipeline, and the second opening 320 can be connected to another pipeline. By switching the state of the moving iron core 100, the connection between these two pipelines can be controlled, thereby regulating the flow state of the fluid.

[0094] In this embodiment, the "connecting channel" refers to the channel connecting the first opening 310 and the second opening 320. When the first opening 310 and the second opening 320 are in a connected state, it indicates that a fluid communication channel exists between them. By controlling the on / off state of this channel, the first opening 310 and the second opening 320 can be connected or disconnected, thereby achieving the purpose of regulating the fluid flow. This embodiment does not limit the specific structure and path of the connecting channel; it can be configured as a straight, curved, or branched channel according to actual application requirements.

[0095] In some embodiments, refer to Figure 2 , Figure 3 The moving iron core 100 can slide along its axial direction. The moving iron core 100 and the stop member 200 are disposed inside the valve housing 300 and can reciprocate within the valve housing 300. Both the moving iron core 100 and the stop member 200 are provided with a first pressure-bearing surface 210 and a second pressure-bearing surface 220, which are respectively arranged at opposite ends of the sliding direction of the moving iron core 100 and the stop member 200. Specifically, the first pressure-bearing surface 210 can be understood as being located on one side (e.g., the upstream side) of the sliding direction, and the second pressure-bearing surface 220 as being located on the opposite side (e.g., the downstream side). The aforementioned "upstream side" and "downstream side" are relative to the sliding path of the moving iron core 100 and the stop member 200. For example, the first end face of the moving iron core 100 is the first pressure-bearing surface 210, and the second pressure-bearing surface 220 of the moving iron core 100 is the second pressure-bearing surface 220. The first end face of the stop member 200 is the first pressure-bearing surface 210, and the second end face of the stop member 200 is the second pressure-bearing surface 220.

[0096] In some embodiments, the stop member 200 and the moving iron core 100 are piston structures that slide axially along the valve housing 300. Both the stop member 200 and the moving iron core 100 are cylindrical in shape. The first pressure-bearing surface 210 of the moving iron core 100 and the stop member 200 is the end face facing away from the first opening 310, and the second pressure-bearing surface 220 is the end face facing the first opening 310. In this state, high-pressure fluid enters through the first opening 310 and acts on the two pressure-bearing surfaces of the stop member 200 and the moving iron core 100. By switching the moving iron core 100 between the first state and the second state, it is possible to control whether the high-pressure fluid at the first opening 310 can pass through the second opening 320. When the moving iron core 100 is in the first state, the first opening 310 and the second opening 320 are connected, allowing high-pressure fluid to flow. When the moving iron core 100 is in the second state, it drives the stop member 200 to close the communication channel between the first opening 310 and the second opening 320, thereby blocking the flow of fluid. This design can effectively control the flow direction and on / off state of the fluid, achieving precise fluid regulation.

[0097] In some embodiments, the end faces of the stop member 200 and the moving iron core 100 facing or away from the first opening 310 are curved, such as including chamfers, steps, or arc-shaped transition surfaces. Due to the presence of these curved shapes, the fluid pressure on the stop member 200 and the moving iron core 100 may exhibit local variations. In this case, to simplify pressure calculations and structural descriptions, the first pressure-bearing surface 210 and the second pressure-bearing surface 220 defined in this application actually refer to the effective projection surfaces of the moving iron core 100 and the stop member 200 along the direction of fluid pressure. Specifically, the first pressure-bearing surface 210 and the second pressure-bearing surface 220 are the areas after projecting the shapes of the moving iron core 100 and the stop member 200 along the direction of fluid pressure. These projected areas serve as the basis for determining the magnitude and direction of the fluid pressure actually acting on the moving iron core 100 and the stop member 200.

[0098] Furthermore, the area difference between the first pressure-bearing surface 210 and the second pressure-bearing surface 220 can be used to achieve different functional requirements. For example, when the area of ​​the first pressure-bearing surface 210 is smaller than the area of ​​the second pressure-bearing surface 220, it can, to some extent, facilitate the movement of the moving iron core 100 and the stop member 200 away from the high-pressure side under the action of fluid pressure, thereby helping the solenoid valve 10 to open; conversely, when the area of ​​the first pressure-bearing surface 210 is larger than the area of ​​the second pressure-bearing surface 220, it can, to some extent, facilitate the moving iron core 100 to maintain the second state, so that the solenoid valve 10 is closed, improving the reliability of the seal.

[0099] In practical applications, the first pressure-bearing surface 210 and the second pressure-bearing surface 220 can be selected according to the specific structural design of the moving iron core 100 and the stop member 200. For example, they can be planar surfaces, slightly curved surfaces, surfaces with grooves or reinforcing ribs, or composite curved surfaces with local variations. As long as the force projection area can be clearly defined in the direction of fluid pressure, these surfaces can be used as the first pressure-bearing surface 210 or the second pressure-bearing surface 220 as defined in this application.

[0100] In some embodiments, refer to Figure 2 , Figure 3 The stop member 200 forms a balance chamber 330 with the valve housing 300 on the side opposite to the first opening 310, and the balance chamber 330 is configured to connect to a pressure source; the first pressure-bearing surface 210 is opposite to the end face of the stop member 200 and the moving iron core 100; the second pressure-bearing surface 220 is opposite to the end face of the stop member 200 and the moving iron core 100 facing the first opening 310. Specifically, the first pressure-bearing surface 210 is the end face of the stop member 200 and / or the moving iron core 100 opposite to the first opening 310, while the second pressure-bearing surface 220 is the end face of the stop member 200 and / or the moving iron core 100 facing the first opening 310.

[0101] With this design, the pressure within the balance chamber 330 can act on the first pressure-bearing surface 210 and the second pressure-bearing surface 220. The fluid pressure acting on the first pressure-bearing surface 210 and the fluid pressure acting on the second pressure-bearing surface 220 are mutually antagonistic, thus forming a balancing force. This structure helps reduce the displacement of the moving iron core 100 and the stop element 200 under fluid pressure, enabling them to switch states stably with a smaller external driving force, which is beneficial to improving the stability of the solenoid valve 10.

[0102] It is understood that the pressure source can be externally connected, and preferably the pressure source has the same pressure as the fluid connected to the first opening 310. For example, the balance chamber 330 can be connected to an air compressor, which supplies gas to the balance chamber 330 at the same pressure as the side of the first opening 310.

[0103] In some embodiments, refer to Figure 2 , Figure 3 The balance chamber 330 can be connected to the first opening 310 side, so that the pressure in the balance chamber 330 will be consistent with the pressure of the fluid at the first opening 310, thereby ensuring that the first pressure surface 210 and the second pressure surface 220 are subjected to the same pressure source.

[0104] This design helps to balance the moving iron core 100 and the stop element 200 in the direction of force, reducing the offset or unstable movement of the moving iron core 100 and the stop element 200 caused by uneven pressure. By making the first pressure-bearing surface 210 and the second pressure-bearing surface 220 work under the same pressure source, the requirement for external driving force can be effectively reduced, the stability of the solenoid valve 10 can be maintained, and the accuracy of the response of the moving iron core 100 and the stop element 200 can be improved.

[0105] In some embodiments, the stop member 200 slides and seals against the valve housing 300, and the moving iron core 100 is located in the balance chamber 330. The first pressure-bearing surface 210 is the end face of the stop member 200 and the moving iron core 100 facing away from the first opening 310; the second pressure-bearing surface 220 is the end face of the stop member 200 and the moving iron core 100 facing the first opening 310. With this design, the moving iron core 100 not only participates in motion control as an actuating component, but also has a pressure-bearing surface corresponding to the stop member 200 in its structure, so that the entire magnetoarmature assembly includes multiple first pressure-bearing surfaces 210 and multiple second pressure-bearing surfaces 220.

[0106] Based on this, the areas of the multiple pressure-bearing surfaces can be adjusted differentially according to the application scenario, thereby regulating the direction and magnitude of the resultant force between the moving iron core 100 and the stop member 200 under pressure, making it more suitable for the response requirements under specific working conditions. For example, by appropriately increasing the total area of ​​the second pressure-bearing surface 220, an effective differential pressure is formed compared to the total area of ​​the first pressure-bearing surface 210, which is beneficial for achieving rapid reset or stable switching of the moving iron core 100 when the magnetic force is released or reversed. This structural configuration is beneficial for improving the response accuracy and operational reliability of the magneto-armature assembly, meeting the usage requirements of various fluid control scenarios.

[0107] In some embodiments, refer to Figure 2 , Figure 3 The stop-flow component 200 is provided with a first through hole 230, which connects the first opening 310 to the balance chamber 330, so that the pressure at the first opening 310 becomes the pressure source of the balance chamber 330. By providing the first through hole 230 on the stop-flow component 200, effective control of the pressure in the balance chamber 330 can be achieved without adding additional pipelines or external connection structures, so that the fluid pressure in the balance chamber 330 is basically the same as the pressure at the first opening 310.

[0108] This structural design, to a certain extent, helps to balance the force state of the moving iron core 100 and the stop member 200 during the switching process between the first and second states. Especially when the stop member 200 slides with the valve housing 300, it can reduce the resistance caused by the pressure difference, thus making it easier for the moving iron core 100 and the stop member 200 to switch positions under magnetic drive. In addition, the size and shape of the first through hole 230 can be optimized according to specific application scenarios to adjust the pressure response speed and stability within the balance cavity 330, thereby improving the dynamic response performance and control accuracy of the magneto-armature assembly.

[0109] In some embodiments, the moving iron core 100 is provided with a second through hole 110 communicating with the first through hole 230. This allows the pressure transmitted through the first through hole 230 to be rapidly distributed to the area surrounding the moving iron core 100. This design helps to reduce the response delay that may occur in the moving iron core 100 during the pressure transmission process, thereby improving the response speed of the moving iron core 100 to a certain extent.

[0110] By setting the second through hole 110, the pressure around the moving iron core 100 can reach the expected value more evenly and promptly, which is beneficial to maintaining the smooth movement of the moving iron core 100 under magnetic drive. In addition, the specific position, number and size of the second through hole 110 can be adjusted according to the actual working conditions to optimize the pressure transmission efficiency and hydrodynamic performance, and further promote the sensitivity and stability of the overall opening and closing response of the solenoid valve 10.

[0111] In some embodiments, the area difference between the first pressure-bearing surface 210 and the second pressure-bearing surface 220 is zero. In this case, the fluid pressure on the first pressure-bearing surface 210 and the second pressure-bearing surface 220 is the same. This means that when driving the moving iron core 100 and the stop member 200 to move, the pressure effects of the two pressure-bearing surfaces cancel each other out or balance each other, so that no additional driving force is generated.

[0112] Specifically, when the areas of the first pressure-bearing surface 210 and the second pressure-bearing surface 220 are equal, the moving iron core 100 and the stop member 200 will not experience additional pushing or resistance under pressure. The force required to drive the moving iron core 100 and the stop member 200 comes only from the friction between the moving iron core 100 and the stop member 200 and the valve body 300, as well as other external forces. Therefore, the process of driving the moving iron core 100 and the stop member 200 becomes smoother, reducing additional forces and avoiding interference from pressure on the movement of the moving iron core 100 and the stop member 200. Thus, during the driving process, the pressure on the first opening 310 side no longer significantly affects the driving force of the moving iron core 100 and the stop member 200, thereby helping to improve the movement accuracy and stability of the moving iron core 100 and the stop member 200.

[0113] The advantage of this design is that it effectively reduces the force required to drive the moving iron core 100 and the stop element 200, thereby reducing the current demand in the coil assembly 11. Since electromagnetic force is proportional to current, reducing the current helps reduce system energy consumption, achieving energy savings. Furthermore, reducing the driving force also improves the response speed of the moving iron core 100 and the stop element 200, avoiding delays or hysteresis caused by large forces, thus improving the overall performance and efficiency of the system.

[0114] In some embodiments, the area difference between the first pressure-bearing surface 210 and the second pressure-bearing surface 220 is greater than zero. This means that the areas of the fluid pressure acting on the first pressure-bearing surface 210 and the second pressure-bearing surface 220 are different, resulting in unequal pressure forces acting on them, generating a driving force that pushes the moving iron core 100 and the stop member 200 toward the second pressure-bearing surface 220.

[0115] Specifically, when the area of ​​the first pressure-bearing surface 210 is larger than the area of ​​the second pressure-bearing surface 220, the fluid pressure on the first pressure-bearing surface 210 is greater. Since the first pressure-bearing surface 210 is located at one end of the moving iron core 100 and the stop member 200, while the second pressure-bearing surface 220 is located at the other end, this pressure difference causes the moving iron core 100 and the stop member 200 to exert a force towards the second pressure-bearing surface 220. When the moving iron core 100 is in the second state, the fluid pressure helps the stop member 200 maintain the state of blocking the first opening 310 and the second opening 320, further enhancing the sealing effect.

[0116] Through this design, the stop element 200 can stably maintain the blocking state of the first opening 310 and the second opening 320 under the action of external force, thereby avoiding the risk of accidental opening and effectively improving the sealing performance. This pressure difference design not only improves the sealing performance of the solenoid valve 10, but also increases the stability of the moving iron core 100 and the stop element 200 during dynamic switching, ensuring the reliability and control accuracy of the system during operation.

[0117] In some embodiments, the area difference between the first pressure-bearing surface 210 and the second pressure-bearing surface 220 is less than zero. This means that the areas of the fluid pressure acting on the first pressure-bearing surface 210 and the second pressure-bearing surface 220 are different, and the area of ​​the first pressure-bearing surface 210 is smaller than the area of ​​the second pressure-bearing surface 220, which in turn results in unequal pressure forces acting on them, generating a driving force that pushes the moving iron core 100 and the stop member 200 toward the first pressure-bearing surface 210.

[0118] Specifically, when the area of ​​the first pressure-bearing surface 210 is smaller than the area of ​​the second pressure-bearing surface 220, the fluid pressure on the second pressure-bearing surface 220 is greater. Since the first pressure-bearing surface 210 is located at one end of the moving iron core 100 and the stop member 200, and the second pressure-bearing surface 220 is located at the other end of the moving iron core 100 and the stop member 200, this pressure difference will cause the moving iron core 100 and the stop member 200 to exert a force towards the first pressure-bearing surface 210. When the moving iron core 100 is in the second state, this pressure difference helps to open the solenoid valve 10, maintaining the connection between the first opening 310 and the second opening 320.

[0119] The advantage of this design is that it can utilize the fluid pressure to push the moving iron core 100 and the stop element 200, making it easier for the solenoid valve 10 to open. By adjusting the area difference between the first pressure surface 210 and the second pressure surface 220, the performance and response speed of the solenoid valve 10 can also be optimized according to specific working conditions.

[0120] In some embodiments, refer to Figure 2 , Figure 3 A first sealing portion 321 is provided around the first opening 310, and the stop member 200 includes a second sealing portion 240. When the moving iron core 100 is in the second state, the first sealing portion 321 and the second sealing portion 240 are sealed together, and the first through hole 230 communicates with the first opening 310. Specifically, when the moving iron core 100 is in the second state, the first sealing portion 321 and the second sealing portion 240 form a sealing fit, blocking the fluid communication between the first opening 310 and the second opening 320. At the same time, the first through hole 230 remains in communication with the first opening 310. This structural design is beneficial for realizing the closed state of the solenoid valve 10.

[0121] In some embodiments, when the moving iron core 100 is in the first state, the first sealing part 321 and the second sealing part 240 are separated, and both the first opening 310 and the first through hole 230 are in communication with the second opening 320. In this state, fluid can form a smooth flow channel through the first opening 310, the first through hole 230, and the second opening 320, which is beneficial for the flow of the medium when the solenoid valve 10 is open. The above structural design is beneficial for realizing the reliable opening and closing function of the solenoid valve 10 through the cooperation and separation of the sealing parts, and the reasonable arrangement of the sealing parts helps to reduce the risk of leakage and improve the working stability of the solenoid valve 10.

[0122] In some embodiments, a seal 250 is provided between the stop member 200 and the valve housing 300 of the magnetoarms assembly. This seal 250 helps to achieve a sealing effect on the balance chamber 330, reducing the risk of leakage caused by the gap between the stop member 200 and the valve housing 300 after fluid enters the balance chamber 330 through the first through hole 230. By properly configuring the seal 250, the sealing performance of the solenoid valve 10 in the closed state can be effectively improved while maintaining the response speed of the solenoid valve 10, thereby helping to mitigate the impact of media leakage and improving the reliability and stability of the overall system.

[0123] In some embodiments, the seal 250 is preferably an elastic sealing ring, such as one made of fluororubber or polyurethane. This type of sealing ring possesses good elasticity and chemical corrosion resistance, can accommodate minor relative movements between the stop element 200 and the valve body 300, and effectively resists erosion and wear of the sealing surface by the medium. Furthermore, the sealing ring's structural design typically includes a lip or O-shaped cross-section, which helps to further enhance the sealing effect under pressure, preventing media leakage from the sealing surface. By rationally selecting the material and structural dimensions of the sealing ring, sealing performance and sliding resistance can be balanced to a certain extent, avoiding excessive obstruction to the movement of the moving iron core 100 and the stop element 200, thereby helping to maintain the rapid response performance of the solenoid valve 10. Simultaneously, this sealing ring can maintain a stable sealing state under a certain range of temperature and pressure changes, improving the adaptability and service life of the solenoid valve 10 under complex operating conditions.

[0124] In some embodiments, the seal 250 is a sliding Glyd ring. The sliding Glyd ring maintains good sealing performance during the relative sliding between the stop element 200 and the valve body 300. This seal has a certain degree of elasticity and wear resistance, adapting to the reciprocating motion of the stop element 200 and reducing the decrease in sealing performance caused by friction. Furthermore, the sliding Glyd ring helps to mitigate changes in the sealing gap caused by mechanical vibration or temperature variations, thereby maintaining a relatively stable sealing state under dynamic operating conditions. By using a sliding Glyd ring, while ensuring the response speed of the solenoid valve 10, it is beneficial to improve the durability and reliability of the seal, reduce maintenance frequency, and extend the service life of the solenoid valve 10.

[0125] In some embodiments, refer to Figure 2 , Figure 3The magnetoarmature assembly also includes an elastic element 400, which is disposed between the moving iron core 100 and the valve housing 300 of the magnetoarmature assembly to reset the moving iron core 100 to a first or second state after the magnetic force is released. The elastic element 400 can be a spring, elastic ring, or elastic washer, and the elastic material can be steel, alloy material, or a polymer material with good elasticity. This design improves the reset stability of the moving iron core 100, reduces reliance on external reset devices, thereby simplifying the structure of the solenoid valve 10 and reducing manufacturing costs.

[0126] When the magnetic force disappears, the elastic element 400 can overcome the frictional resistance between the moving iron core 100 and the stop element 200 to a certain extent, ensuring that the moving iron core 100 moves in a predetermined direction, which facilitates the reliable opening or closing of the solenoid valve 10. In addition, by rationally designing the stiffness and preload state of the elastic element 400, the reset action of the moving iron core 100 can be made smoother, avoiding overshoot or oscillation, thereby helping to extend the overall service life of the solenoid valve 10 and improve its operational reliability.

[0127] By incorporating the elastic element 400, the solenoid valve 10 can quickly and effectively reset when power is cut off or the magnetic force disappears, reducing the risk of leakage that may occur when the solenoid valve 10 is not in operation and promoting the stability and safety of the overall system performance. The elastic element 400 structure is not limited to a specific form and can be flexibly adjusted according to specific application requirements, exhibiting a certain degree of applicability and scalability.

[0128] In some embodiments, refer to Figure 2 , Figure 3 The valve housing 300 includes a stationary iron core 340, and an elastic element 400 is disposed between a moving iron core 100 and the stationary iron core 340 to allow the moving iron core 100 to elastically reset. The moving iron core 100 is configured to move in a direction approaching or away from the stationary iron core 340 under the action of magnetic force to switch between a first state and a second state. Specifically, the moving iron core 100 is configured to move in a direction approaching or away from the stationary iron core 340 under the action of magnetic force to achieve the switching between the first state and the second state.

[0129] This structural design allows the moving iron core 100 to overcome the reaction force of the elastic element 400 and move towards the stationary iron core 340 when energized and generating magnetic force, switching to the corresponding working state. When the magnetic force is removed, the elastic element 400 drives the moving iron core 100 to return to its initial state to a certain extent, which helps improve the sensitivity and response speed of the solenoid valve 10. The elastic element 400 can also buffer the movement of the moving iron core 100 to a certain extent, reducing impact force, which helps reduce component wear and extend the service life of the solenoid valve 10.

[0130] Furthermore, the relative positional relationship between the stationary iron core 340 and the moving iron core 100 helps to clarify the direction of the magnetic force, thereby ensuring a relatively stable movement trajectory of the moving iron core 100 and facilitating reliable opening and closing of the solenoid valve 10. The material and shape of the elastic element 400 can be optimized according to actual working conditions to adapt to different working environments and performance requirements.

[0131] In some embodiments, refer to Figure 2 , Figure 3 At least one of the moving iron core 100 and the valve housing 300 of the magneto-armature assembly is provided with a buffer 120, which is used to buffer the moving iron core 100 when it moves relative to the valve housing 300. The buffer 120 is used to provide a buffering effect when the moving iron core 100 moves relative to the valve housing 300, thereby slowing down the movement speed of the moving iron core 100 and mitigating the impact force between the moving iron core 100 and the valve housing 300.

[0132] This buffer design helps reduce mechanical shock during operation, decrease component wear, and improve the durability and reliability of the components. Simultaneously, the buffer 120 can reduce vibration and noise that may be caused by the high-speed impact of the moving iron core 100 on the valve housing 300, optimizing the operational stability and user experience of the solenoid valve 10. The buffer 120 can take the form of an elastic washer, rubber ring, spring buffer structure, or other suitable elastic material components, and can be selected and arranged according to actual needs.

[0133] In some embodiments, refer to Figure 2 , Figure 3 The valve housing 300 also includes a valve seat 350. The first opening 310 and the second opening 320 of the valve housing 300 are located on the valve seat 350. The valve seat 350 and the stationary iron core 340 of the valve housing 300 are in a circumferential limiting fit with each other. This circumferential limiting fit design is beneficial to improving the overall structural stability of the solenoid valve 10.

[0134] During the installation and operation of the solenoid valve 10, it often needs to be connected to other devices or pipelines and may be subjected to external forces in the circumferential direction. The circumferential limiting fit between the valve seat 350 and the stationary iron core 340 can effectively prevent relative rotation or sliding between the valve seat 350 and the stationary iron core 340, thereby avoiding internal structural misalignment or loosening and reducing sealing failure or functional abnormality caused by component position displacement.

[0135] Furthermore, the limiting fit facilitates the accurate positioning of the valve seat 350, maintaining a stable fluid passage layout and contributing to the normal opening and closing functions of the solenoid valve 10. This structural design enhances the mechanical strength and vibration resistance of the solenoid valve 10 while ensuring a compact assembly, thereby helping to extend its service life and improve overall reliability.

[0136] The limiting and fitting structure can adopt the matching of slot and boss, the matching of slot and insert, or other mechanical limiting methods. The appropriate shape and size can be selected according to the specific design requirements to take into account both assembly convenience and structural stability.

[0137] In some embodiments, refer to Figure 2 , Figure 3 The valve housing 300 also includes a core cover 360, and the stationary core 340 of the valve housing 300 is fixedly connected to the core cover 360. This fixed connection method can ensure the positioning stability of the stationary core 340 and prevent it from undergoing relative displacement during the operation of the solenoid valve 10, thereby helping to maintain the integrity of the internal magnetic circuit and the stability of the performance of the solenoid valve 10.

[0138] The iron core cover 360 not only provides mechanical protection for the stationary iron core 340, but also prevents impurities from entering the magnetic circuit area, reducing interference with the magnetic field and improving the operational reliability of the solenoid valve 10. Furthermore, the iron core cover 360 simplifies the overall structural design of the valve housing 300, facilitating assembly and maintenance, while also enhancing the durability and service life of the solenoid valve 10.

[0139] In some embodiments, refer to Figure 2 , Figure 3 The iron core cover 360 and the stationary iron core 340 serve as at least part of the sidewalls of the balance chamber 330. The two are fixedly connected to form an integral structure, which helps to ensure the structural stability and sealing performance of the balance chamber 330. This fixed connection not only enhances the mechanical strength of the balance chamber 330, but also helps to reduce the risk of leakage caused by the relative movement of components, thereby improving the sealing effect and overall performance stability of the solenoid valve 10.

[0140] The connection between the iron core cover 360 and the stationary iron core 340 can be achieved using various techniques, including but not limited to welding, interference fit, adhesive bonding, bolting, or brazing. Welding provides a strong and well-sealed connection, suitable for applications requiring high sealing performance. Interference fits utilize dimensional fit to generate strong mechanical clamping force, suitable for compact designs that are easy to assemble. Adhesive bonding offers a certain degree of sealing performance and is simple to perform. Bolting is suitable for structural designs requiring easy disassembly and maintenance. Brazing combines strong connection and sealing performance, suitable for applications with specific material and process requirements. Based on the actual structure and manufacturing process requirements, the above connection methods can be rationally selected or combined to achieve the best results.

[0141] According to the second aspect of this disclosure, referring to Figures 4 to 10 A solenoid valve 10 is provided, including the magnetoarmature assembly described in the above embodiments. This solenoid valve 10 possesses all the beneficial effects of the aforementioned magnetoarmature assembly, which will not be elaborated further herein.

[0142] In some embodiments, refer to Figure 4 , Figure 5 The solenoid valve 10 also includes a coil assembly 11 and a plug-in assembly 12. The coil assembly 11 is disposed on the outer periphery of the moving iron core 100 and / or the stationary iron core 340 of the magneto-armature assembly. A limiting structure 11a is provided between the coil assembly 11 and the plug-in assembly 12, and the plug-in assembly 12 and the coil assembly 11 are engaged in a circumferentially limiting engagement through the limiting structure 11a. This limiting structure 11a is used to achieve a limiting engagement between the coil assembly 11 and the plug-in assembly 12 in the circumferential direction of the solenoid valve 10, thereby ensuring that the two maintain a stable relative position during installation and operation, and preventing relative rotation or misalignment caused by vibration or external force.

[0143] The specific form of the limiting structure 11a can include a boss and groove fit, a keyway fit, a snap-fit ​​structure, or other mechanical limiting methods, designed according to the specific structure and installation requirements of the solenoid valve 10. By setting the limiting structure 11a, not only can the assembly accuracy between the coil assembly 11 and the plug-in assembly 12 be improved, but the overall structural stability and reliability of the solenoid valve 10 can also be effectively guaranteed, which is beneficial to extending the service life of the solenoid valve 10 and improving its performance.

[0144] The coil assembly 11 is disposed on the outer periphery of the moving iron core 100 and / or the stationary iron core 340 of the magnetoarmature assembly. When energized, it generates a magnetic field, causing the moving iron core 100 to move closer to the stationary iron core 340, thereby switching the moving iron core 100 between a first state and a second state, closing the solenoid valve 10. When the coil assembly 11 is de-energized, the magnetic field disappears, and under the action of the elastic element 400, the moving iron core 100 is driven to move away from the stationary iron core 340, thus opening the solenoid valve 10. This structural design facilitates reliable control and rapid response of the solenoid valve 10, improving system stability and efficiency.

[0145] In some embodiments, refer to Figure 7 , Figure 9 The solenoid valve 10 also includes a housing 13, and at least one of the coil assembly 11 and the plug assembly 12 is engaged with the housing 13 in a circumferentially limiting manner. By providing the housing 13, the solenoid valve 10 can be mechanically protected against external impacts or impurities, thereby improving its durability and service life. Simultaneously, the coil assembly 11 and the plug assembly 12, through their circumferential limiting engagement with the housing 13, can effectively prevent relative rotation or displacement during the operation of the solenoid valve 10, which helps maintain the stability and reliability of the internal structure and ensures the normal operation of the solenoid valve 10.

[0146] In some embodiments, refer to Figure 6 , Figure 9 The outer casing 13 is provided with an opening 13a, and at least a portion of the limiting structure 11a is located within the opening 13a (in conjunction with...). Figure 5 This design allows the limiting structure 11a to engage with the housing 13 in the circumferential direction of the solenoid valve 10. The limiting structure 11a not only maintains a circumferential limiting engagement between the plug-in assembly 12 and the coil assembly 11, but also achieves circumferential limiting between the plug-in assembly 12 and / or the coil assembly 11 and the housing 13, thus effectively limiting multiple components with a single structure. This design makes the limiting structure 11a more concise and compact, simplifying the overall structure of the solenoid valve 10 and improving assembly efficiency and stability.

[0147] In some embodiments, the housing 13 is at least partially made of metal, and the pins of the coil assembly 11 pass through the limiting structure 11a to connect to the outside. Exemplarily, the limiting structure 11a is made of an insulating material, such as a raised structure of insulating material, to prevent electrical continuity between the coil pins and the metal housing 13, thereby effectively ensuring circuit stability. By integrating the limiting and insulation functions into the same structure, the structure is simplified and compacted, while improving the overall reliability of the solenoid valve 10.

[0148] In some embodiments, refer to Figure 8 , Figure 9The outer casing 13 is provided with a limiting platform 13b, and the stationary iron core 340 abuts against the limiting platform 13b to limit the position of the stationary iron core 340 relative to the outer casing 13. The limiting platform 13b effectively positions the stationary iron core 340 during the assembly of the solenoid valve 10, preventing axial displacement during operation, thus helping to ensure the structural stability and operational reliability of the magnetoarmature assembly. At the same time, this structure is simple, occupies little space, and is easy to integrate into a compact solenoid valve 10 device.

[0149] In some embodiments, refer to Figure 9 , Figure 10 The valve housing 300 of the magnetoarmature assembly is provided with a stepped surface 341, and the coil assembly 11 includes an abutment portion 11b (connected). Figure 5 The contact portion 11b is located near the center of the coil assembly 11 and is used to contact the stepped surface 341. During the winding process, the skeleton of the coil assembly 11 may undergo structural deformation due to the winding tension of the copper wire. Especially in the outer edge area of ​​the skeleton, due to the concentrated force, warping or instability is prone to occur, resulting in a decrease in the overall flatness of the bottom surface of the coil assembly 11. This may lead to problems such as unstable assembly, misalignment or uneven gap between the assembly and the valve body 300.

[0150] Because the inner side of the coil assembly 11 skeleton, i.e., the position near the center hole, experiences less stress during the winding process, its structural deformation is relatively small. Therefore, abutment portion 11b can be provided at this position to abut against the stepped surface 341 of the valve housing 300, thereby forming a stable positioning support. This structural design helps improve assembly stability, avoids changes in assembly clearance caused by warping of the skeleton edge, and effectively ensures the installation accuracy and operational reliability of the coil assembly 11 in the solenoid valve 10.

[0151] The contact portion 11b can be an outwardly protruding structure, such as a rib, ridge, or annular step formed on the inner edge of the coil assembly 11. Alternatively, a distributed multi-point contact structure can be used to accommodate different manufacturing errors. For example, the coil assembly 11 has an annular structure, with the contact portion 11b projected axially near the central hole, forming an axial positioning and support relationship with the stepped surface 341 of the valve housing 300. This structure allows for precise positioning and stable support of the coil assembly 11 without significantly increasing the overall structural complexity, thereby improving the structural stability and service life of the entire solenoid valve 10 assembly.

[0152] In some embodiments, refer to Figure 9 , Figure 10The valve housing 300 of the magneto-armature assembly and the coil assembly 11 are positioned in the upper circumferential direction of the solenoid valve 10. This arrangement allows for circumferential positioning of the coil assembly 11 during the assembly of the solenoid valve 10, thereby preventing the coil assembly 11 from rotating or misaligning during use and ensuring a stable fit between it and the valve housing 300. This is beneficial for maintaining electromagnetic performance and structural stability.

[0153] For example, the coil assembly 11 has a protruding structure, and the corresponding position in the valve housing 300 has a groove adapted to the protruding structure; or conversely, the coil assembly 11 has a groove, and the valve housing 300 has a protruding structure that mates with it. Through this structural cooperation, when the coil assembly 11 is assembled into the valve housing 300, it can be limited in the circumferential direction of the solenoid valve 10, thereby achieving an anti-rotation positioning function.

[0154] According to a third aspect of this disclosure, an air suspension system is provided, including the magneto-armature assembly of the above embodiments or the solenoid valve 10 of the above embodiments. This air suspension system has all the beneficial effects of the aforementioned magneto-armature assembly or solenoid valve 10, which will not be elaborated further herein.

[0155] According to a fourth aspect of this disclosure, a vehicle is provided, including the magnetoarmature assembly, the solenoid valve 10, or the air suspension system described in the above embodiments. This vehicle possesses all the beneficial effects of the aforementioned magnetoarmature assembly, solenoid valve 10, or air suspension system, which will not be elaborated further herein.

[0156] The vehicle may be a gasoline-powered vehicle, a plug-in hybrid electric vehicle, or a new energy vehicle, etc., and this disclosure does not make any specific restrictions.

[0157] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0158] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0159] The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0160] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. A magnetoarmature assembly, characterized in that, include: The moving iron core is configured to switch between a first state and a second state under the action of magnetic force; and The stop element is directly connected to the moving iron core and is configured to move under the drive of the moving iron core to close or open the solenoid valve. When the moving iron core is in the first state, the solenoid valve is open; when the moving iron core is in the second state, the solenoid valve is closed.

2. The magnetoarmature assembly according to claim 1, characterized in that, The stop-flow element is connected to the end of the moving iron core facing the stop-flow element.

3. The magnetoarmature assembly according to claim 1, characterized in that, The stop-flow component is fixedly connected to the moving iron core.

4. The magnetoarmature assembly according to claim 1, characterized in that, The stop element and the moving iron core are connected by interference fit and / or welding.

5. The magnetoarmature assembly according to any one of claims 1-4, characterized in that, In the moving direction of the stop member, at least one of the stop member and the moving iron core has a first pressure-bearing surface and a second pressure-bearing surface, the force direction of the first pressure-bearing surface and the second pressure-bearing surface is the normal direction of their respective directions, and the fluid pressure acting on the first pressure-bearing surface and the second pressure-bearing surface is opposite in direction.

6. The magnetoarmature assembly according to claim 5, characterized in that, The magneto-armature assembly further includes a valve housing, and at least one of the moving iron core and the stop member is movably disposed in the valve housing so that the moving iron core switches between the first state and the second state.

7. The magnetoarmature assembly according to claim 6, characterized in that, The valve housing has a first opening and a second opening; When the moving iron core is in the first state, the first opening is connected to the second opening; When the moving iron core is in the second state, the stop member closes the communication channel between the first opening and the second opening to block the connection between the first opening and the second opening.

8. The magnetoarmature assembly according to claim 7, characterized in that, The stop-flow component forms a balance chamber with the valve housing on the side opposite to the first opening, and the balance chamber is configured to communicate with a pressure source. The first pressure-bearing surface is the end face of at least one of the stop member and the moving iron core that faces away from the first opening; The second pressure-bearing surface is the end face of at least one of the stop member and the moving iron core facing the first opening.

9. The magnetoarmature assembly according to claim 8, characterized in that, The stop-flow element slides and seals with the valve housing, and the moving iron core is located in the balance chamber; The first pressure-bearing surface is the end face of the stop member and the moving iron core that is away from the first opening; The second pressure-bearing surface is the end face of the stop member and the moving iron core facing the first opening.

10. The magnetoarmature assembly according to claim 8, characterized in that, The stop-through component is provided with a first through hole, which is used to connect the first opening with the balance chamber so that the pressure at the first opening forms a pressure source for the balance chamber.

11. The magnetoarmature assembly according to claim 10, characterized in that, The moving iron core is provided with a second through hole that communicates with the first through hole.

12. The magnetoarmature assembly according to claim 6, characterized in that, The area difference between the first pressure-bearing surface and the second pressure-bearing surface is equal to zero; Alternatively, the area difference between the first pressure-bearing surface and the second pressure-bearing surface is greater than zero; Alternatively, the area difference between the first pressure-bearing surface and the second pressure-bearing surface is less than zero.

13. The magnetoarmature assembly according to claim 10, characterized in that, A first sealing portion is provided around the first opening, and the stop member includes a second sealing portion, wherein: When the moving iron core is in the second state, the first sealing part and the second sealing part are sealed together, and the first through hole is connected to the first opening; And / or, when the moving iron core is in the first state, the first sealing part and the second sealing part are separated, and the first opening and the first through hole are both connected to the second opening.

14. The magnetoarmature assembly according to any one of claims 1-4, characterized in that, A seal is provided between the stop-flow element and the valve housing of the magneto-armature assembly.

15. The magnetoarmature assembly according to claim 14, characterized in that, The sealing element is a sliding Glycol seal.

16. The magnetoarmature assembly according to any one of claims 1-4, characterized in that, The magneto-armature assembly further includes an elastic element disposed between the moving iron core and the valve housing of the magneto-armature assembly, so as to reset the moving iron core to the first state or the second state after the magnetic force is released.

17. The magnetoarmature assembly according to claim 16, characterized in that, The valve housing includes a stationary iron core, and the elastic element is disposed between the moving iron core and the stationary iron core to allow the moving iron core to elastically reset. The moving iron core is configured to move in a direction close to or away from the stationary iron core under the action of magnetic force to switch between the first state and the second state.

18. The magnetoarmature assembly according to any one of claims 1-4, characterized in that, At least one of the moving iron core and the valve housing of the magneto-armature assembly is provided with a buffer member, which is used to buffer the moving iron core when it moves relative to the valve housing.

19. The magnetoarmature assembly according to claim 6, characterized in that, The valve housing also includes a valve seat, and the first opening and the second opening of the valve housing are located on the valve seat. The valve seat and the stationary iron core of the valve housing are in a circumferential upper limit fit between the valve and the solenoid valve. And / or, the valve housing further includes an iron core cover, the stationary iron core of the valve housing being fixedly connected to the iron core cover.

20. A solenoid valve, characterized in that, Includes the magnetoelectric armature assembly as described in any one of claims 1-19.

21. The solenoid valve according to claim 20, characterized in that, The solenoid valve also includes a coil assembly and a connector assembly; The coil assembly is disposed on the outer periphery of the moving iron core and / or the stationary iron core of the magneto-armature assembly. A limiting structure is provided between the coil assembly and the plug-in assembly. The plug-in assembly and the coil assembly are engaged in a circumferential upper limit cooperation in the solenoid valve through the limiting structure.

22. The solenoid valve according to claim 21, characterized in that, The solenoid valve further includes a housing, and at least one of the coil assembly and the plug assembly engages with the housing in a circumferential upper limit of the solenoid valve.

23. The solenoid valve according to claim 22, characterized in that, The housing has an opening, and at least a portion of the limiting structure is located within the opening, so that the limiting structure and the housing engage in a circumferential upper limit fit with the solenoid valve.

24. The solenoid valve according to claim 23, characterized in that, The outer casing is at least partially made of metal, and the pins of the coil assembly pass through the limiting structure to connect to the outside.

25. The solenoid valve according to any one of claims 22-24, characterized in that, The outer casing is provided with a limiting platform, and the stationary iron core abuts against the limiting platform to limit the position of the stationary iron core relative to the outer casing.

26. The solenoid valve according to any one of claims 21-24, characterized in that, The valve housing of the magneto-armature assembly has a stepped surface, and the coil assembly includes an abutment portion located near the center of the coil assembly and used to contact the stepped surface.

27. The solenoid valve according to any one of claims 21-24, characterized in that, The valve housing of the magneto-armature assembly and the coil assembly are in a circumferential upper limit fit with the solenoid valve.

28. An air suspension system, characterized in that, It includes the magnetoarmature assembly as described in any one of claims 1-19, or the solenoid valve as described in any one of claims 20-27.

29. A vehicle, characterized in that, It includes the magneto-armature assembly according to any one of claims 1-19, or the solenoid valve according to any one of claims 20-27, or the air suspension system according to claim 28.

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