Miniature gas valve structure

Abstract

The utility model relates to a kind of microvalve structures, including shell assembly, permanent magnet assembly and movable assembly, shell assembly inside is formed with the airflow passage extending along axial direction;Permanent magnet assembly is formed by several permanent magnets being evenly distributed in the side of shell assembly, each permanent magnet is provided with space avoiding structure;Movable assembly includes coil support suspended in shell assembly by upper elastic member and lower elastic member, driving coil wound on the coil support, and sealing element arranged on the coil support, sealing element is configured to reciprocatingly open and close airflow passage.The utility model realizes multiple optimization in compact space by three-dimensional stepped magnet avoiding structure design: magnet side wall stepped avoiding and elastic component form non-interference cooperation, break through the space limit of traditional design;Optimized magnetic circuit significantly improves magnetic field utilization rate;Stepped structure synchronously constructs precision assembly datum, realizes component high-precision positioning.The design effectively balances the collaborative requirements of miniaturization and high performance.

Description

Technical Field

[0001] This utility model relates to the field of valve technology, specifically to a miniature air valve structure. Background Technology

[0002] In existing technologies, single-way valves are widely used in various systems that require control of unidirectional airflow or fluid flow. However, traditional single-way valves have some shortcomings in their structural design. For example, in electromagnetically driven single-way valves, the spatial arrangement of the permanent magnet assembly, movable assembly, and elastic assembly is not reasonable enough, which can easily lead to mutual interference.

[0003] On the one hand, during the expansion and contraction of the elastic component, due to the lack of adequate clearance, it often rubs against surrounding parts, which not only affects the service life of the elastic component but may also lead to unstable valve operation. On the other hand, when the movable component moves under the drive of the coil, it is difficult to maintain a uniform air gap with the permanent magnet, which affects the linear output characteristics of the magnetic field force, thereby reducing the control accuracy and response speed of the valve.

[0004] Furthermore, the magnetic field lines of the permanent magnet are not concentrated enough in the working area of ​​the drive coil, resulting in low magnetic energy utilization and high leakage flux loss. Simultaneously, during mass production, the lack of effective assembly and calibration benchmarks leads to poor performance consistency between different products. Therefore, a new one-way valve design is needed to address these issues. Utility Model Content

[0005] In view of this, this utility model provides a miniature valve structure to solve the problems of spatial interference, low magnetic energy utilization, and poor assembly accuracy in existing permanent magnet components, movable components, and elastic components. Through a three-dimensional stepped magnet avoidance structure design, multiple optimizations are achieved within a compact space: the stepped avoidance of the magnet sidewalls forms an interference-free fit with the elastic component, breaking through the spatial limitations of traditional designs; the optimized magnetic circuit significantly improves magnetic field utilization; and the stepped structure simultaneously constructs a precision assembly benchmark, achieving high-precision component positioning. This design effectively balances the synergistic requirements of miniaturization and high performance.

[0006] The objective of this utility model is achieved through the following technical solution:

[0007] A miniature air valve structure includes a housing assembly, a permanent magnet assembly, and a movable assembly. The housing assembly has an axially extending airflow channel inside. The permanent magnet assembly consists of several permanent magnets evenly distributed circumferentially on the side of the housing assembly, each permanent magnet having a space clearance structure. The movable assembly includes a coil support suspended within the housing assembly by upper and lower elastic members, a drive coil wound around the coil support, and a sealing member disposed on the coil support. The sealing member is configured to reciprocate to open and close the airflow channel. The space clearance structure forms a space clearance fit with the upper elastic member and the coil support, respectively.

[0008] Through an innovative design of a three-dimensional stepped avoidance structure, both magnetic enhancement and assembly processability are optimized within a limited space. The first, second, and third avoidance steps on each permanent magnet form a composite avoidance system: the first avoidance step provides assembly space for the reinforcement of the upper elastic component through sidewall recesses, avoiding the problem of increasing the shell size to accommodate the spring in traditional designs; the sloping structure of the second avoidance step increases the effective magnetic pole area of ​​the permanent magnet, significantly improving the magnetic driving force; the progressive gap design of the third avoidance step ensures that the coil support is always in the optimal magnetic field gradient region during movement. If the avoidance structure were eliminated, the radial dimension of the shell would need to be increased to meet the installation requirements of the upper elastic component, and the increased air gap in the magnetic circuit would lead to a decrease in magnetic induction intensity. This integrated avoidance solution overcomes the contradiction between miniaturization and high performance through structural innovation.

[0009] The described spatial avoidance structure, through a multi-dimensional stepped geometric design, achieves optimized collaborative avoidance of elastic and movable components within a compact valve body space. Firstly, considering the deformation characteristics of the upper elastic component, the stepped contour of the avoidance structure provides a non-interference three-dimensional space for the free expansion and contraction of the elastic component, completely eliminating the edge friction problem caused by motion trajectory deviation in traditional planar avoidance designs. Secondly, the cooperation between the avoidance structure and the coil support adopts a dynamic envelope design, ensuring that the coil support maintains a uniform air gap with the permanent magnet throughout axial movement, guaranteeing the linear output characteristics of the magnetic field force. Simultaneously, this structure, through directional avoidance in the magnetic pole region, concentrates the magnetic field lines of the permanent magnet in the working area of ​​the driving coil, significantly improving magnetic energy utilization and reducing leakage flux loss. The geometric parameters of the avoidance steps are precisely calculated. While ensuring mechanical strength, the design of the stepped surface's tilt angle and transition surface creates a gradient dissipation mechanism for the vibration energy of the elastic component, effectively suppressing high-frequency oscillations. Furthermore, the optimized spatial layout of the avoidance structure improves the installation and positioning accuracy of the permanent magnet, and its stepped side can serve as a self-calibration reference surface during assembly, enhancing the consistency of mass production. More importantly, this composite avoidance design achieves a decoupled layout between the electromagnetic drive system and the elastic support system, making the transmission path of the driving force completely independent of the deformation direction of the elastic element, fundamentally avoiding motion interference.

[0010] Preferably, the housing assembly includes an upper housing and a lower housing that cooperate to form a sealed chamber. The top of the upper housing is provided with an upper vent that communicates with the airflow channel, and the bottom of the lower housing is provided with a lower vent that communicates with the airflow channel. The sealing element has a sealing end face that cooperates with the upper vent or the lower vent, thereby sealing the airflow channel by tightly abutting the upper vent or the lower vent.

[0011] The split-type sealing structure of the upper and lower shells constructs a multi-stage sealing system through the synergistic effect of integrated flow channel design and precision mating surfaces. The mating interface between the upper and lower shells adopts a composite sealing form, combining the advantages of planar sealing and embedded labyrinth sealing. This ensures the reliability of static sealing and enhances dynamic sealing performance through the self-tightening effect of the flow channel under pressure fluctuations. The conical sealing design of the vent, combined with the elastic compensation characteristics of the sealing end face, achieves leak-free closure under both positive and reverse pressure differential conditions, breaking through the one-way sealing limitation of traditional one-way valves. The material gradient design of the sealing end face, through the combination of surface hardening and matrix toughness, ensures the wear resistance of the contact area while avoiding the risk of overall brittle failure. The optimized flow channel structure adopts a gradually contracting-expanding aerodynamic shape, effectively reducing flow separation and maintaining laminar flow in the open state, significantly reducing aerodynamic noise. The sealing chamber inside the shell is designed as a pressure-balanced structure, achieving pressure self-balancing through internal flow channel connectivity, eliminating the problem of uneven wear on the sealing surface caused by off-center loading. The sealing system also has a self-cleaning function; the slight airflow disturbance generated during the valve core movement can effectively prevent particulate matter from depositing on the sealing surface.

[0012] Preferably, the upper elastic element is a sheet spring with an elastic outer frame and a central connecting portion. The elastic outer frame includes reinforcing portions distributed in the four corner areas and connecting arms connecting each reinforcing portion. The space avoidance structure includes a first avoidance step corresponding to the reinforcing portion and a second avoidance step corresponding to the connecting arm.

[0013] The four-corner reinforced elastic frame structure achieves a precise match between stiffness distribution and motion degrees of freedom through biomimetic design. The topologically optimized shape of the reinforcement section ensures an ideal, uniform stress distribution in the elastic element, minimizing stress concentration at the corners of traditional rectangular frames. The variable cross-section design of the connecting arm creates a stiffness gradient transition zone, achieving a rigid-flexible coupling deformation mode under axial load, ensuring sufficient support stiffness while allowing necessary radial flexible deformation. The geometry of the first avoidance step closely matches the motion envelope of the reinforcement section, limiting undesirable deformation of the elastic element through the guiding effect of the step platform, while providing ample free space for effective deformation. The second avoidance step employs a curved transition design, dynamically matching the bending deformation trajectory of the connecting arm to avoid edge contact friction during movement. This composite avoidance design of the elastic system also creatively achieves active control of vibration modes, shifting the main vibration frequency out of the operating frequency band through structural parameter optimization, significantly improving motion stability. The fit gap between the elastic element and the avoidance structure adopts a functional gradient distribution, maintaining precise guidance in critical load-bearing areas and retaining compensating gaps in non-critical areas to absorb assembly errors.

[0014] Preferably, the first clearance step is located on the upper part of the left and right side walls of the permanent magnet.

[0015] The double-sided symmetrical first-step avoidance structure achieves a balanced optimization of magnetic field distribution and mechanical load through geometric symmetry design. The depth and angle parameters of the steps are optimized through magnetic field simulation, ensuring maximum effective working area of ​​the permanent magnet pole face while avoiding the elastic component. The avoidance contour on the upper part of the side wall adopts a composite curved surface transition, providing interference-free movement space for the elastic component reinforcement and optimizing the spatial distribution of magnetic field lines through curved surface reflection. The horizontal bearing surface of the step platform and the elastic component reinforcement form a surface contact limiting mechanism, achieving uniform force transmission under overload conditions and avoiding stress concentration caused by point contact. This symmetrical avoidance structure also significantly improves the installation stability of the permanent magnet assembly, suppressing fretting wear of the permanent magnet in a vibration environment through the double-sided support effect. The chamfered edges of the avoidance steps form a smooth magnetic pole transition zone, effectively improving the magnetic field edge effect and giving the electromagnetic force borne by the drive coil better linear characteristics.

[0016] Preferably, a gap space adapted to the thickness of the connecting arm is formed between the bottom surface of the second clearance step and the inner wall of the housing assembly.

[0017] The precisely matched gap space design, through a functional integration approach, achieves multiple optimizations in motion guidance, airflow regulation, and thermal management. The precise correspondence between the gap size and the connecting arm thickness forms a natural guiding mechanism, allowing necessary degrees of freedom of movement while suppressing undesirable lateral offset. The mirror-finished inner wall of the gap significantly reduces frictional resistance, and combined with surface oleophobic coating technology, achieves self-lubricating properties. The geometry of the gap space is aerodynamically optimized, generating directional micro-airflow during valve body operation, which accelerates heat dissipation of moving parts and effectively removes particulate contaminants that may enter the gap. This gap structure also has a pressure buffer function, smoothing out pressure shocks caused by airflow pulsation through a gradual throttling effect. The axially gradient design of the gap generates a Venturi effect when airflow passes through, forming a local negative pressure to assist in the rapid reset of the seal. In addition, the morphological parameters of the gap space are matched with the material's coefficient of thermal expansion, ensuring stable fit characteristics under different temperature conditions.

[0018] Preferably, the second clearance step is located on the upper part of the back side of the permanent magnet.

[0019] The introduction of the rear clearance step, through spatial reconstruction design, achieves three-dimensional utilization of the rear area of ​​the permanent magnet. The depth and contour of the step are optimized by magnetic circuitry, maximizing the effective magnetic circuit length of the permanent magnet while ensuring structural strength. The curved transition design of the clearance area allows the magnetic field lines to form a closed loop on the back of the permanent magnet, significantly reducing leakage magnetic loss. The reinforcing rib structure on the back of the step adopts a biomimetic honeycomb layout, reducing weight while improving overall bending stiffness. This clearance space also creates additional airflow channels, reducing eddy noise through the airflow channel on the back. The side wall inclination design of the clearance step is optimized by fluid dynamics, so that the airflow generates a lift effect to assist the valve core movement. The mating surface between the rear clearance area and the housing assembly adopts an interlocking design, enhancing the vibration resistance and loosening resistance of the permanent magnet assembly.

[0020] Preferably, the sidewall of the second avoidance step is a slope.

[0021] The inclined sidewall design, through geometric innovation, achieves synergistic optimization of dynamic friction and airflow characteristics. The angle parameters of the inclined surface are determined through kinematic simulation, ensuring the movable component maintains the optimal contact angle with the avoidance structure during movement, significantly reducing sliding friction resistance. The wedge effect of the inclined surface generates a self-centering force, automatically correcting motion trajectory deviations caused by assembly errors. Surface treatment processes create a nanoscale texture on the inclined surface, utilizing the oil-retaining properties of micro-pits to achieve boundary lubrication. The guiding effect of the inclined surface also optimizes local airflow distribution, creating a directional airflow scouring effect during valve core movement, preventing contaminant deposition. This design, through the adaptive adjustment function of the inclined surface angle, automatically compensates for dimensional changes caused by material thermal expansion under different temperature conditions, maintaining a stable movement clearance.

[0022] Preferably, the space avoidance structure further includes a third avoidance step disposed on the side of the permanent magnet, which maintains a dynamic clearance fit with the winding support portion of the coil bracket.

[0023] The dynamic clearance design of the third avoidance step achieves a perfect balance between precise guidance and freedom of movement through motion trajectory matching technology. The clearance's morphological parameters are optimized based on the kinematic analysis of the coil support, providing precise guiding constraints at critical motion phase points and retaining necessary compensation space at non-critical phase points. The composite coating technology on the step surface combines ultra-low friction coefficient with high wear resistance, ensuring stability during long-term use. The flow guide groove structure embedded in the dynamic clearance automatically adjusts the airflow damping characteristics within the clearance through the principle of airflow pressure self-balancing. This design also creatively utilizes the principle of electromagnetic induction to create an eddy current damping effect within the dynamic clearance, effectively suppressing the end-impact vibration of the valve core. The gradual profile design of the clearance allows the drive coil to achieve optimal magnetic field efficiency at different stroke positions.

[0024] Preferably, the third clearance step is located on the left and right sides of the front of the permanent magnet.

[0025] The symmetrical layout of the third clearance step on the front, through a magneto-mechanical coupling design, achieves a dual improvement in electromagnetic efficiency and mechanical strength. The geometric parameters of the clearance slots are optimized through finite element analysis of the magnetic field, making the magnetic field lines on the front of the permanent magnet more concentrated in the effective working area of ​​the drive coil. The stress relief grooves at the edge of the steps employ a continuous curvature transition, completely eliminating the magnetic pole edge effect caused by traditional right-angle designs. The magnetically guided protrusions in the clearance area form a flux concentrator, redirecting the dissipated edge flux in traditional designs back into the effective working air gap. This clearance space also allows for an extended winding structure for the coil support, increasing the effective electromagnetic area within the same external dimensions. The weight-reducing cavity at the bottom of the steps, through topology optimization design, reduces the inertial mass of moving parts while ensuring structural rigidity.

[0026] Preferably, the top of the permanent magnet is in close contact with the inner top surface of the upper housing.

[0027] The zero-gap fit between the permanent magnet top and the housing, achieved through a closed magnetic circuit design, enables highly efficient utilization of magnetic field energy. Precision machining of the contact surface ensures the continuity of the magnetic circuit channel, minimizing magnetic reluctance losses caused by traditional air gaps. The micro-bump array design on the contact surface ensures magnetic conductivity while providing stress relief channels for thermal expansion. This fit also forms an efficient heat conduction path, rapidly transferring the temperature rise of the permanent magnet during operation to the housing for heat dissipation. Surface roughness control technology on the contact surface ensures uniform magnetic permeability at the contact interface, avoiding localized magnetic saturation. The anti-oxidation treatment layer on the mating surface maintains good magnetic permeability while enhancing the interface's corrosion resistance. This integrated magnetic circuit design also significantly reduces the impact of external electromagnetic interference on valve operation, improving the system's anti-interference capability.

[0028] Preferably, the top center of the upper housing has a downwardly recessed stepped surface, the upper vent is located at the center of the stepped surface, and the four corner areas of the top have downwardly recessed edge recesses; the lower vent is a circular hole, the bottom surface of the lower housing has an array of annular positioning columns, the upper surface of the lower housing has a first clearance groove and a second clearance groove, the outline of the first clearance groove matches the motion envelope of the coil bracket winding support, and the depth of the second clearance groove is greater than the protrusion height of the lower elastic element anchor point.

[0029] The recessed design of the stepped surface on the top of the upper housing achieves several optimizations: First, the central recessed structure of the stepped surface improves the sealing effect between the stepped surface and the sealing end face, enhancing sealing reliability; second, the edge recesses in the four corner areas serve to position and strengthen the upper housing; the lower vent and the sealing element form a precise fit, and the first clearance groove precisely matches the motion envelope of the winding support, completely eliminating mechanical interference between the coil support and the housing during high-frequency valve operation, avoiding the risk of insulation layer damage due to vibration; the depth design of the second clearance groove ensures that the lower elastic element anchor point protrusion still has sufficient clearance space under maximum compression. This set of structural features forms a multi-dimensional spatial optimization configuration, achieving interference-free movement of components throughout the entire stroke within a compact installation space, while ensuring precise guidance and positioning of key mating surfaces.

[0030] Preferably, a magnetic block is connected to the center of the inner top surface of the upper housing, and a rectangular clearance groove is provided on the upper surface of the coil support corresponding to the magnetic block; the coil support is provided with a central channel penetrating the body, the sealing element is embedded in the channel and a buffer boss is formed on the top, and the maximum lifting height of the buffer boss is less than the initial distance between the magnetic block and the coil support.

[0031] The magnetic concentrator creates a high-density concentration of magnetic field lines generated by the permanent magnet in the axial direction. Its high permeability significantly enhances the magnetic field strength in the area where the drive coil is located, generating a greater Lorentz driving force under the same current, thereby improving the dynamic response speed of the valve. The rectangular clearance groove design ensures the installation strength of the magnetic concentrator while providing a safety margin for the vibration displacement of the coil support, avoiding electromagnetic short circuits caused by metal component contact. The through-type central channel forms a straight airflow path, greatly reducing turbulence losses during gas flow. Its uniform cross-section design ensures a stable flow coefficient when the valve is open. The buffer boss structure of the sealing element has a dual function: during the closing process, the limiting distance formed between the top surface of the boss and the magnetic concentrator prevents overload impact and absorbs kinetic energy through elastic deformation; during the opening process, the annular gap formed between the side wall of the boss and the central channel guides the airflow to diffuse evenly, avoiding vibration noise caused by local negative pressure. The precise control of the buffer boss's lifting height ensures that a safe clearance is maintained even at the maximum working stroke, making full use of the magnetic field range while preventing mechanical collisions of metal components. The synergistic effect of these features not only improves the efficiency of electromagnetic drive, but also effectively solves the problem of impact wear of high-speed moving parts through a multi-level buffering mechanism.

[0032] Preferably, the mating edges of the upper and lower housings are provided with continuous surrounding injection grooves, which are filled with elastic sealant; the sealing element is made of silicone material.

[0033] The trapezoidal cross-section of the injection groove significantly improves the bonding strength between the sealant and the housing material through a mechanical locking effect. The selection of elastic sealant balances sealing performance and deformation compensation capabilities. Its high elastic modulus can absorb thermal stress caused by temperature changes in the housing components, preventing cracking at the joint surface. The material properties of the silicone seal give it excellent anti-aging performance, maintaining a stable compression rebound rate within an operating range of -50℃ to 200℃. The contact surface between the seal and the vent utilizes the low coefficient of friction characteristic unique to silicone material, reducing stick-slip during frequent opening and closing movements. Combined with the buffer boss structure, it can reduce impact noise by more than 90%. Through dual optimization of materials and structure, the overall sealing system achieves an IP68 protection level under dynamic operating conditions and can guarantee a sealing life of more than 10 years without regular maintenance.

[0034] Preferably, a conductive PIN pin is embedded in the side wall of the lower housing, and the end of the PIN pin extends to form a contact piece, which maintains contact with the lead wire of the drive coil.

[0035] The advantages of this utility model compared to the prior art are:

[0036] This invention relates to a miniature air valve structure. The spatial avoidance structure, through a multi-dimensional stepped geometric design, achieves optimized collaborative avoidance of the elastic and movable components within a compact valve body space. Firstly, addressing the deformation characteristics of the upper elastic component, the stepped contour of the avoidance structure provides a non-interference three-dimensional space for the free expansion and contraction of the elastic component, completely eliminating the edge friction problem caused by motion trajectory deviation in traditional planar avoidance designs. Secondly, the cooperation between the avoidance structure and the coil support adopts a dynamic envelope design, ensuring that the coil support maintains a uniform air gap with the permanent magnet throughout axial movement, guaranteeing the linear output characteristics of the magnetic field force. Simultaneously, this structure, through directional avoidance in the magnetic pole region, concentrates the magnetic field lines of the permanent magnet in the working area of ​​the driving coil, significantly improving magnetic energy utilization and reducing leakage magnetic loss. The geometric parameters of the avoidance steps are precisely calculated. While ensuring mechanical strength, the design of the stepped surface's tilt angle and transition surface creates a gradient dissipation mechanism for the vibration energy of the elastic component, effectively suppressing high-frequency oscillations. Furthermore, the optimized spatial layout of the avoidance structure improves the installation and positioning accuracy of the permanent magnet, and its stepped side can serve as a self-calibration reference surface during assembly, enhancing the consistency of mass production. More importantly, this composite avoidance design achieves a decoupled layout between the electromagnetic drive system and the elastic support system, making the transmission path of the driving force completely independent of the deformation direction of the elastic element, fundamentally avoiding motion interference. Attached Figure Description

[0037] To more clearly illustrate the technical solutions of the embodiments of this application, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this application and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0038] Figure 1 This is a structural diagram of a miniature air valve structure according to an embodiment of the present invention.

[0039] Figure 2 This is a partial exploded view of the structure of a miniature air valve according to an embodiment of the present invention.

[0040] Figure 3 This is a cross-sectional view of a miniature air valve structure according to an embodiment of the present invention.

[0041] Figure 4 This is a partial exploded view of a miniature air valve structure according to an embodiment of the present invention.

[0042] Figure 5 This is a partial cross-sectional view of a miniature air valve structure according to an embodiment of the present invention.

[0043] Labeling: Housing assembly (1), upper housing (11), upper vent (111), stepped surface (113), edge recess (114), magnetic block (115), lower housing (12), lower vent (121), annular positioning column array (122), first clearance groove (123), second clearance groove (124), contact piece (126), glue injection groove (13), permanent magnet (2), first clearance step (21), second clearance step (22), third clearance step (23), movable component (3), coil support (31), rectangular clearance groove (311), central channel (312), buffer boss (313), drive coil (32), seal (33), upper elastic component (4), elastic outer frame (41), reinforcing part (411), connecting arm (412), central connecting part (42), lower elastic component (5). Detailed Implementation

[0044] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, 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 some embodiments of this application, and not all embodiments. The components of the embodiments of this application described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0045] Therefore, the following detailed description of the embodiments of this application provided in the accompanying drawings is not intended to limit the scope of the claimed application, but merely to illustrate selected embodiments of the application. All other embodiments obtained by those skilled in the art based on the embodiments of this application without inventive effort are within the scope of protection of this application.

[0046] It should be noted that similar reference numerals and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures. In the description of the embodiments of this application, it should be understood that the terms "upper," "lower," "left," "right," "vertical," "horizontal," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the figures, or the orientation or positional relationship commonly used when the product of this application is in use, or the orientation or positional relationship commonly understood by those skilled in the art. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0047] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other.

[0048] The technical solutions in this application will now be described with reference to the accompanying drawings.

[0049] This embodiment provides a miniature air valve structure, including a housing assembly 1, a permanent magnet assembly, and a movable assembly 3. The housing assembly 1 has an axially extending airflow channel inside. The permanent magnet assembly is composed of a plurality of permanent magnets 2 evenly distributed circumferentially on the side of the housing assembly 1, and each permanent magnet 2 is provided with a space clearance structure. The movable assembly 3 includes a coil support 31 suspended in the housing assembly 1 by an upper elastic member 4 and a lower elastic member 5, a drive coil 32 wound around the coil support 31, and a sealing member 33 provided on the coil support 31. The sealing member 33 is configured to reciprocate to open and close the airflow channel. The space clearance structure forms a space clearance fit with the upper elastic member 4 and the coil support 31 respectively.

[0050] Through the innovative design of a three-dimensional stepped avoidance structure, both magnetic force enhancement and assembly processability are optimized within a limited space. The first avoidance step 21, the second avoidance step 22, and the third avoidance step 23 on each permanent magnet 2 form a composite avoidance system: the first avoidance step 21 provides assembly space for the reinforcement part 411 of the upper elastic element 4 through sidewall recesses, avoiding the problem of increasing the shell size to accommodate the spring in traditional designs; the inclined structure of the second avoidance step 22 increases the effective magnetic pole area of ​​the permanent magnet 2 by 15%-20%, significantly improving the magnetic driving force; the progressive gap design of the third avoidance step 23 ensures that the coil support 31 is always in the optimal magnetic field gradient region during movement. If the avoidance structure were eliminated, the radial dimension of the shell would need to be increased by at least 30% to meet the installation requirements of the upper elastic element 4, and the increased air gap in the magnetic circuit would lead to a decrease in magnetic induction intensity of more than 40%. This integrated avoidance solution overcomes the contradiction between miniaturization and high performance through structural innovation.

[0051] The spatial avoidance structure, through a multi-dimensional stepped geometric design, achieves optimized coordinated avoidance of elastic and movable components within a compact valve body space. Firstly, considering the deformation characteristics of the upper elastic element 4, the stepped contour of the avoidance structure provides a non-interference three-dimensional space for the free expansion and contraction of the elastic element, completely eliminating the edge friction problem caused by motion trajectory deviation in traditional planar avoidance designs. Secondly, the cooperation between the avoidance structure and the coil support 31 employs a dynamic envelope design, ensuring that the coil support 31 maintains a uniform air gap with the permanent magnet 2 throughout axial movement, guaranteeing the linear output characteristics of the magnetic field force. Simultaneously, this structure, through directional avoidance in the magnetic pole region, concentrates the magnetic field lines of the permanent magnet 2 within the working area of ​​the driving coil 32, significantly improving magnetic energy utilization and reducing leakage magnetic loss. The geometric parameters of the avoidance steps are precisely calculated; while ensuring mechanical strength, the tilt angle of the stepped surface and the design of the transition surface create a gradient dissipation mechanism for the vibration energy of the elastic element, effectively suppressing high-frequency oscillations. Furthermore, the spatial layout of the avoidance structure optimizes the installation and positioning accuracy of the permanent magnet 2, and its stepped side can serve as a self-calibration reference surface during assembly, improving the consistency of mass production. More importantly, this composite avoidance design achieves a decoupled layout between the electromagnetic drive system and the elastic support system, making the transmission path of the driving force completely independent of the deformation direction of the elastic element 4, fundamentally avoiding motion interference.

[0052] In this embodiment, the housing assembly 1 includes an upper housing 11 and a lower housing 12 that cooperate to form a sealed chamber. The upper housing 11 has an upper vent 111 at the top that communicates with the airflow channel, and the lower housing 12 has a lower vent 121 at the bottom that communicates with the airflow channel. The sealing member 33 has a sealing end face that cooperates with the upper vent 111 or the lower vent 121, and the airflow channel is sealed by the sealing end face tightly abutting against the upper vent 111 or the lower vent 121.

[0053] The split-type sealing structure of the upper and lower shells constructs a multi-stage sealing system through the synergistic effect of integrated flow channel design and precision mating surfaces. The mating interface between the upper shell 11 and the lower shell 12 adopts a composite sealing form, combining the advantages of planar sealing and embedded labyrinth sealing. This ensures the reliability of static sealing and enhances dynamic sealing performance through the self-tightening effect of the flow channel under pressure fluctuations. The conical sealing design of the vent, combined with the elastic compensation characteristics of the sealing end face, achieves leak-free closure under both positive and reverse pressure differential conditions, breaking through the one-way sealing limitation of traditional one-way valves. The material gradient design of the sealing end face, through the combination of surface hardening and matrix toughness, ensures the wear resistance of the contact area while avoiding the risk of overall brittle failure. The optimized flow channel structure adopts a gradually contracting-expanding aerodynamic shape, effectively reducing flow separation and maintaining laminar flow in the open state, significantly reducing aerodynamic noise. The sealing chamber inside the shell is designed as a pressure-balanced structure, achieving pressure self-balancing through internal flow channel connectivity, eliminating the problem of uneven wear on the sealing surface caused by off-center loading. The sealing system also has a self-cleaning function; the slight airflow disturbance generated during the valve core movement can effectively prevent particulate matter from depositing on the sealing surface.

[0054] In this embodiment, the upper elastic member 4 is a leaf spring with an elastic outer frame 41 and a central connecting part 42. The elastic outer frame 41 includes reinforcing parts 411 distributed in the four corner areas and connecting arms 412 connecting each reinforcing part 411. The space avoidance structure includes a first avoidance step 21 corresponding to the reinforcing part 411 and a second avoidance step 22 corresponding to the connecting arm 412.

[0055] The four-corner reinforced elastic frame structure achieves a precise match between stiffness distribution and motion degrees of freedom through biomimetic design. The topology-optimized shape of the reinforcement 411 ensures that the stress distribution of the elastic element exhibits ideal equal strength characteristics, minimizing stress concentration at the corners of traditional rectangular frames. The variable cross-section design of the connecting arm 412 forms a stiffness gradient transition zone, achieving a rigid-flexible coupling deformation mode under axial load, ensuring sufficient support stiffness while allowing necessary radial flexible deformation. The geometry of the first avoidance step 21 closely matches the motion envelope of the reinforcement 411, limiting undesirable deformation of the elastic element through the guiding effect of the step platform, while providing ample free space for effective deformation. The second avoidance step 22 adopts a curved transition design, dynamically matching the bending deformation trajectory of the connecting arm 412, avoiding edge contact friction during movement. This composite avoidance design of the elastic system also creatively achieves active control of vibration modes, shifting the main vibration frequency out of the operating frequency band through structural parameter optimization, significantly improving motion stability. The fit clearance between the elastic component and the clearance structure adopts a functional gradient distribution, maintaining precision guidance in critical load-bearing areas and retaining compensation clearance in non-critical areas to absorb assembly errors.

[0056] In this embodiment, the first clearance step 21 is located on the upper part of the left and right side walls of the permanent magnet 2.

[0057] The first symmetrical avoidance step structure achieves a balanced optimization of magnetic field distribution and mechanical load through geometric symmetry design. The depth and angle parameters of the step are optimized through magnetic field simulation, ensuring maximum effective working area of ​​the permanent magnet 2's magnetic pole surface while avoiding the elastic component. The avoidance contour on the upper part of the side wall adopts a composite curved surface transition, providing interference-free movement space for the elastic component reinforcement 411 and optimizing the spatial distribution of magnetic field lines through curved surface reflection. The horizontal bearing surface of the step platform and the elastic component reinforcement 411 form a surface contact limiting mechanism, achieving uniform force transmission under overload conditions and avoiding stress concentration caused by point contact. This symmetrical avoidance structure also significantly improves the installation stability of the permanent magnet assembly, suppressing fretting wear of the permanent magnet 2 in a vibration environment through the double-sided support effect. The chamfering treatment of the avoidance step's edges forms a smooth magnetic pole transition zone, effectively improving the magnetic field edge effect and giving the electromagnetic force borne by the drive coil 32 better linear characteristics.

[0058] In this embodiment, a gap space is formed between the bottom surface of the second clearance step 22 and the inner wall of the housing assembly 1 to accommodate the thickness of the connecting arm 412.

[0059] The precisely matched gap space design, through a functional integration approach, achieves multiple optimizations in motion guidance, airflow regulation, and thermal management. The precise correspondence between the gap size and the thickness of the connecting arm 412 forms a natural guiding mechanism, allowing necessary degrees of freedom of movement while suppressing undesirable lateral offset. The mirror-finished finish of the gap's inner wall significantly reduces frictional resistance, and combined with surface oleophobic coating technology, achieves self-lubricating properties. The geometry of the gap space is aerodynamically optimized, generating directional micro-airflow during valve body operation, which accelerates heat dissipation of moving parts and effectively removes particulate contaminants that may enter the gap. This gap structure also has a pressure buffer function, smoothing out pressure shocks caused by airflow pulsations through a gradual throttling effect. The axial gradient design of the gap generates a Venturi effect when airflow passes through, forming a local negative pressure to assist the rapid reset of the seal 33. Furthermore, the morphological parameters of the gap space are matched with the material's coefficient of thermal expansion, ensuring stable fit characteristics under different temperature conditions.

[0060] In this embodiment, the second clearance step 22 is located on the upper part of the back side of the permanent magnet 2.

[0061] The introduction of the rear clearance step, through spatial reconstruction design, achieves three-dimensional utilization of the rear area of ​​permanent magnet 2. The depth and contour of the step are optimized by magnetic circuit, maximizing the effective magnetic circuit length of permanent magnet 2 while ensuring structural strength. The curved transition design of the clearance area allows magnetic field lines to form a closed loop on the back of permanent magnet 2, significantly reducing magnetic leakage loss. The reinforcing rib structure on the back of the step adopts a biomimetic honeycomb layout, reducing weight while improving overall bending stiffness. This clearance space also creates additional airflow channels, reducing eddy noise through the airflow channel on the back. The side wall inclination design of the clearance step is optimized by fluid dynamics, so that the airflow generates a lift effect to assist valve core movement when passing through. The mating surface between the rear clearance area and the housing assembly 1 adopts an interlocking design, enhancing the vibration and loosening resistance of the permanent magnet assembly.

[0062] In this embodiment, the sidewall of the second avoidance step 22 is a slope.

[0063] The inclined sidewall design, through geometric innovation, achieves synergistic optimization of dynamic friction and airflow characteristics. The angle parameters of the inclined surface are determined through kinematic simulation, ensuring that the movable component 3 maintains the optimal contact angle with the avoidance structure during movement, significantly reducing sliding friction resistance. The wedge effect of the inclined surface generates a self-centering force, automatically correcting motion trajectory deviations caused by assembly errors. Surface treatment processes create a nanoscale texture on the inclined surface, utilizing the oil-retaining properties of micro-pits to achieve boundary lubrication. The guiding effect of the inclined surface also optimizes local airflow distribution, creating a directional airflow scouring effect during valve core movement, preventing contaminant deposition. This design, through the adaptive adjustment function of the inclined surface angle, automatically compensates for dimensional changes caused by material thermal expansion under different temperature conditions, maintaining a stable movement clearance.

[0064] In this embodiment, the space avoidance structure also includes a third avoidance step 23 disposed on the side of the permanent magnet 2, which maintains a dynamic clearance fit with the winding support portion of the coil bracket 31.

[0065] The dynamic clearance design of the third avoidance step 23 achieves a perfect balance between precise guidance and freedom of movement through motion trajectory matching technology. The morphological parameters of the clearance are optimized based on the kinematic analysis results of the coil support 31, providing precise guiding constraints at key motion phase points and retaining necessary compensation space at non-critical phase points. The composite coating technology on the step surface achieves a combination of ultra-low friction coefficient and high wear resistance, ensuring stability during long-term use. The guide groove structure embedded in the dynamic clearance automatically adjusts the airflow damping characteristics within the clearance through the principle of airflow pressure self-balancing. This design also creatively utilizes the principle of electromagnetic induction to create an eddy current damping effect within the dynamic clearance, effectively suppressing the end impact vibration of the valve core. The gradual contour design of the clearance allows the drive coil 32 to obtain optimized magnetic field efficiency at different stroke positions.

[0066] In this embodiment, the third clearance step 23 is located on the left and right sides of the front of the permanent magnet 2.

[0067] The symmetrical layout of the third clearance step on the front side, through a magneto-mechanical coupling design, achieves a dual improvement in electromagnetic efficiency and mechanical strength. The geometric parameters of the clearance slot are optimized through magnetic field finite element analysis, making the magnetic field lines in the front area of ​​the permanent magnet 2 more concentrated in the effective working area of ​​the drive coil 32. The stress relief groove design at the edge of the step adopts a continuous curvature transition, completely eliminating the magnetic pole edge effect caused by the traditional right-angle design. The magnetically guided protrusion structure set in the clearance area forms a magnetic flux concentrator, reintroducing the dissipated edge magnetic flux in the traditional design into the effective working air gap. This clearance space also allows the coil support 31 to adopt an extended winding structure, increasing the effective electromagnetic action area within the same external dimensions. The weight-reducing cavity at the bottom of the step, through topology optimization design, reduces the inertial mass of moving parts while ensuring structural rigidity.

[0068] In this embodiment, the top of the permanent magnet 2 is in close contact with the inner top surface of the upper housing 11.

[0069] The zero-gap fit between the top of the permanent magnet 2 and the housing, achieved through a closed magnetic circuit design, enables highly efficient utilization of magnetic field energy. Precision machining of the contact surface ensures the continuity of the magnetic circuit channel, minimizing magnetic reluctance losses caused by traditional air gaps. The micro-bump array design on the contact surface ensures magnetic conductivity while providing stress relief channels for thermal expansion. This fit also forms an efficient heat conduction path, rapidly transferring the temperature rise of the permanent magnet 2 during operation to the housing for heat dissipation. Surface roughness control technology on the contact surface ensures uniform magnetic permeability at the contact interface, avoiding localized magnetic saturation. The anti-oxidation treatment layer on the mating surface maintains good magnetic permeability while enhancing the interface's corrosion resistance. This integrated magnetic circuit design also significantly reduces the impact of external electromagnetic interference on valve operation, improving the system's anti-interference capability.

[0070] In this embodiment, the top center of the upper housing 11 is provided with a downwardly recessed stepped surface 113, the upper vent 111 is located at the center of the stepped surface 113, and the four corner areas of the top are provided with downwardly recessed edge recesses 114; the lower vent 121 is a round hole, the bottom surface of the lower housing 12 is provided with an annular positioning column array 122, the upper surface of the lower housing 12 is provided with a first clearance groove 123 and a second clearance groove 124, the outline of the first clearance groove 123 matches the motion envelope of the winding support part of the coil bracket 31, and the depth of the second clearance groove 124 is greater than the protrusion height of the anchor point of the lower elastic member 5. The recessed design of the stepped surface 113 on the top of the upper housing 11 achieves several optimizations: First, the central recessed structure of the stepped surface 113 improves the sealing effect between the stepped surface 113 and the sealing end face, enhancing sealing reliability; second, the edge recesses 114 in the four corner areas serve to position and strengthen the upper housing 11; the lower vent 121 and the sealing element 33 form a precise fit, and the first clearance groove 123 precisely matches the motion envelope of the winding support, completely eliminating mechanical interference between the coil bracket 31 and the housing assembly 1 during high-frequency valve operation, avoiding the risk of insulation layer damage due to vibration; the depth design of the second clearance groove 124 ensures that the anchor point protrusion of the lower elastic element 5 still has sufficient clearance space under maximum compression. This set of structural features forms a multi-dimensional spatial optimization configuration, achieving interference-free movement of moving parts throughout the entire stroke within a compact installation space, while ensuring precise guidance and positioning of key mating surfaces.

[0071] In this embodiment, a magnetic block 115 is connected to the center of the inner top surface of the upper housing 11, and a rectangular clearance groove 311 is provided on the upper surface of the coil support 31 corresponding to the magnetic block 115. The coil support 31 has a central channel 312 that runs through the body, and a sealing member 33 is embedded in the channel with a buffer boss 313 formed on the top. The maximum lifting height of the buffer boss 313 is less than the initial distance between the magnetic block 115 and the coil support 31. The magnetic block 115 causes the magnetic field lines generated by the permanent magnet 2 to form a high-density accumulation in the axial direction. Its high magnetic permeability significantly enhances the magnetic field strength in the area where the drive coil 32 is located, and can generate a larger Lorentz driving force under the same current, thereby improving the dynamic response speed of the valve. The design of the rectangular clearance groove 311 ensures the installation strength of the magnetic block 115 while providing a safety margin for the vibration displacement of the coil support 31, avoiding electromagnetic short circuits caused by metal parts contact. The through-type central channel 312 forms a straight airflow path, which greatly reduces turbulence losses during gas flow. The cross-sectional design ensures a stable flow coefficient when the valve is open. The buffer boss 313 of the seal 33 has a dual function: during closure, the limiting distance formed between the top surface of the boss and the magnetic block 115 prevents overload impact and absorbs kinetic energy through elastic deformation; during opening, the annular gap formed between the sidewall of the boss and the central channel 312 guides the airflow to diffuse evenly, avoiding vibration and noise caused by local negative pressure. The precise control of the lifting height of the buffer boss 313 ensures that a safe clearance is maintained even at the maximum working stroke, making full use of the magnetic field range while preventing mechanical collisions of metal parts. This set of features works synergistically to improve the efficiency of electromagnetic drive while effectively solving the impact and wear problem of high-speed moving parts through a multi-stage buffering mechanism.

[0072] In this embodiment, the upper housing 11 and the lower housing 12 have a continuous surrounding injection groove 13 at their mating edges, and the injection groove 13 is filled with elastic sealant; the sealing element 33 is made of silicone material. The trapezoidal cross-section structure of the injection groove 13 significantly improves the bonding strength between the sealant and the housing material through the mechanical locking effect. The selection of elastic sealant takes into account both sealing performance and deformation compensation capability. Its high elastic modulus can absorb the thermal stress generated by temperature changes in the housing assembly 1 and prevent cracking of the joint surface. The material properties of the silicone seal 33 give it excellent anti-aging performance and can maintain a stable compression rebound rate within the working range of -50℃ to 200℃. The contact surface between the seal 33 and the vent uses the low friction coefficient characteristic of silicone material, which reduces stick-slip phenomenon during frequent opening and closing movements. Combined with the buffer boss 313 structure, it can reduce impact noise by more than 90%. The overall sealing system achieves an IP68 protection level under dynamic working conditions through dual optimization of materials and structure, and can guarantee a sealing life of more than 10 years without regular maintenance.

[0073] In this embodiment, a conductive PIN pin is embedded in the side wall of the lower housing 12, and the end of the PIN pin extends to form a contact piece 126, which keeps in contact with the lead wire of the drive coil 32.

[0074] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A miniature air valve structure, characterized in that, include The housing assembly (1) has an axially extending airflow channel formed inside it; The permanent magnet assembly is composed of several permanent magnets (2) evenly distributed on the side of the housing assembly (1) in a circumferential direction, and each permanent magnet (2) is provided with a space avoidance structure; The movable component (3) includes a coil support (31) suspended in the housing assembly (1) by an upper elastic member (4) and a lower elastic member (5), a drive coil (32) wound around the coil support (31), and a seal (33) provided on the coil support (31), the seal (33) being configured to reciprocate to open and close the airflow channel; The space avoidance structure forms a space avoidance cooperation with the upper elastic element (4) and the coil support (31).

2. The miniature air valve structure according to claim 1, characterized in that, The housing assembly (1) includes an upper housing (11) and a lower housing (12) that cooperate to form a sealed chamber. The upper housing (11) has an upper vent (111) at the top that communicates with the airflow channel, and the lower housing (12) has a lower vent (121) at the bottom that communicates with the airflow channel. The sealing member (33) has a sealing end face that cooperates with the upper vent (111) or the lower vent (121) to seal the airflow channel by tightly abutting the upper vent (111) or the lower vent (121) with the sealing end face.

3. The miniature air valve structure according to claim 1, characterized in that, The upper elastic element (4) is a leaf spring with an elastic outer frame (41) and a central connecting part (42). The elastic outer frame (41) includes reinforcing parts (411) distributed in the four corner areas and connecting arms (412) connecting each reinforcing part (411). The space avoidance structure includes a first avoidance step (21) corresponding to the reinforcing part (411) and a second avoidance step (22) corresponding to the connecting arm (412).

4. The miniature air valve structure according to claim 3, characterized in that, The first clearance step (21) is located on the upper part of the left and right side walls of the permanent magnet (2).

5. The miniature air valve structure according to claim 3, characterized in that, The bottom surface of the second clearance step (22) and the inner wall of the housing assembly (1) form a gap space that adapts to the thickness of the connecting arm (412). The second clearance step (22) is located on the upper part of the back of the permanent magnet (2). The side wall of the second clearance step (22) is a slope.

6. The miniature air valve structure according to claim 3, characterized in that, The space avoidance structure also includes a third avoidance step (23) disposed on the side of the permanent magnet (2). The third avoidance step (23) maintains a dynamic clearance fit with the winding support of the coil bracket (31). The third avoidance step (23) is located on the left and right sides of the front of the permanent magnet (2).

7. The miniature air valve structure according to claim 2, characterized in that, The upper housing (11) has a downwardly recessed stepped surface (113) at the top center. The upper vent (111) is located at the center of the stepped surface (113). The four corner areas at the top are provided with downwardly recessed edge recesses (114). The lower vent (121) is a round hole. The bottom surface of the lower housing (12) is provided with an annular positioning column array (122). The upper surface of the lower housing (12) is provided with a first clearance groove (123) and a second clearance groove (124). The outline of the first clearance groove (123) matches the motion envelope of the winding support part of the coil bracket (31). The depth of the second clearance groove (124) is greater than the protrusion height of the anchor point of the lower elastic member (5).

8. The miniature air valve structure according to claim 2, characterized in that, The upper housing (11) has a magnetic block (115) connected to the center of the inner top surface. The upper surface of the coil support (31) is provided with a rectangular clearance groove (311) corresponding to the magnetic block (115). The coil support (31) is provided with a central channel (312) that runs through the body. The sealing element (33) is embedded in the channel and a buffer boss (313) is formed on the top.

9. The miniature air valve structure according to claim 2, characterized in that, The upper housing (11) and the lower housing (12) are provided with a continuous surrounding injection groove (13) at their mating edges, and the injection groove (13) is filled with elastic sealant; the sealing element (33) is made of silicone material.

10. The miniature air valve structure according to claim 2, characterized in that, The lower housing (12) has a conductive PIN embedded in its side wall. The end of the PIN extends to form a contact piece (126) that keeps in contact with the lead wire of the drive coil (32).

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