Rigidity valve

Abstract

The utility model provides a rigidity valve which comprises fixed iron, a valve element and a valve seat. The valve core is sleeved in the fixed iron and the valve seat; the valve element can move in the axial direction relative to the fixed iron and the valve seat so as to selectively open or close a valve port in the valve seat. The stress areas of the upper surface and the lower surface of the valve element are equal, so that the upward gas pressure and the downward gas pressure borne by the valve element are equal. Through the configuration, the operation comfort and the response speed of the rigidity valve are improved, meanwhile, the sealing performance is improved, and the sealing stability is improved.

Description

TECHNICAL FIELD

[0001] The utility model belongs to air spring technical field, and particularly relates to a stiffness valve. BACKGROUND

[0002] With the development of the automobile industry, the automobile positioning in the consumer market is changing. End consumers no longer regard the automobile as a transport tool, and the automobile has become a carrier and space for improving the quality of life. This consumption trend means that the industry needs to further improve the comfort and driving quality of the automobile while pursuing automobile intelligence. Vehicles with air springs have good ride smoothness and ride stability when driving on winding roads due to the stiffness characteristics and vibration frequency of the air springs, can effectively ensure the excellent adhesion of the tires to the road, and can effectively reduce the road damage ability of the vehicle, thereby improving the steering stability and driving safety of the vehicle when driving at high speed. The stiffness valve as an important component of the air spring system enables the air suspension system to also achieve a variable volume additional air chamber, a switchable characteristic curve, and a set motion or comfort mode switching. Therefore, the demand for stiffness valves is also increasing.

[0003] The stiffness valve currently used in the automobile industry generally includes a valve body, a fixed iron, a dynamic seal, a valve core, and a valve seat, and belongs to a normally open electromagnetic valve. When the stiffness valve is not powered, the valve port on the valve seat is in an open state, and air flows between two valve cavities through a radial passage on the valve seat. After the stiffness valve is powered, the valve core moves downward under the action of electromagnetic force and contacts the valve seat, closes the valve port, cuts off the flow passage between the two valve cavities, and seals the circumferential gap between the valve core and the fixed iron through the dynamic seal. However, the existing stiffness valve needs to be improved in terms of response speed, sealing effect, and sealing stability.

[0004] It should be noted that the information disclosed in the background section of this application is only intended to deepen the understanding of the general background of the application, and should not be regarded as acknowledging or implying in any form that the information constitutes prior art known to those skilled in the art. CONTENT OF THE UTILITY MODEL

[0005] The utility model aims at providing a stiffness valve which can effectively improve the response speed, increase the sealing performance and sealing stability.

[0006] To achieve the above-mentioned purpose, the utility model provides a stiffness valve which comprises a fixed iron, a valve core and a valve seat; the fixed iron and the valve seat are sleeved with the valve core; the valve core can move in the axial direction relative to the fixed iron and the valve seat to selectively open or close the valve port on the valve seat; and the valve core is arranged such that the force receiving areas of the upper and lower surfaces are equal, so that the upward and downward gas pressures received by the valve core are equal.

[0007] Optionally, the diameter of the sealing contact surface of the valve core and the valve port is equal to the maximum outer diameter of the valve core.

[0008] Optionally, the valve core has a first diameter section and a second diameter section, the outer diameter of the second diameter section is greater than that of the first diameter section, the first diameter section and the second diameter section are staggered, and the diameter of the sealing contact surface is equal to the outer diameter of the second diameter section; or the valve core is of equal diameter structure.

[0009] Optionally, the stiffness valve further comprises a dynamic sealing assembly between the valve core and the fixed iron; the dynamic sealing assembly comprises a metal skeleton and a lateral sealing rubber piece; the lateral sealing rubber piece is mounted on the metal skeleton; and the metal skeleton is connected with the mounting slot of the fixed iron in interference fit, while the valve seat is connected with the lateral sealing rubber piece in clearance fit.

[0010] Optionally, the lateral sealing rubber piece and the metal skeleton are integrally formed by rubber vulcanization.

[0011] Optionally, the lateral sealing rubber piece comprises a base and a sealing lip; one sealing lip is arranged on each of the upper and lower sides of the outer part of the base; the two sealing lips are bent away from each other; an annular protrusion is arranged on the outer surface of the base; the annular protrusion forms a static sealing pair with the fixed iron in interference fit, and the base and the fixed iron are connected in clearance fit.

[0012] Optionally, the upper surface and the lower surface of the base are both provided with the annular protrusion, and the annular protrusion is arranged away from the sealing lip.

[0013] Optionally, the annular protrusion is a single protrusion structure or a multi-protrusion structure.

[0014] Optionally, the mounting slot comprises an interference fit groove, a rubber accommodating groove and a sealing lip accommodating groove arranged in the radial direction from inside to outside and distributed in steps; the metal skeleton is connected with the interference fit groove in interference fit; the base is located in the rubber accommodating groove, and the sealing lip is located in the sealing lip accommodating groove; the sealing lip protrudes from the sealing lip accommodating groove in the radial direction of the fixed iron; the mounting slot axially penetrates the bottom of the fixed iron, so that the bottom of the mounting slot is open.

[0015] Optionally, the metal skeleton comprises a central column, an annular flange is arranged on the outer circumferential surface of the central column, the annular flange is lower than the central column at both axial ends, the annular flange is connected with the mounting slot in interference fit, and / or a plurality of through holes are arranged on the central column of the metal skeleton in the radial direction, and the plurality of through holes are uniformly distributed.

[0016] Compared with the prior art, the technical scheme of the utility model has at least the following beneficial effects:

[0017] The foregoing rigidity valve can make the upward and downward gas pressure that the valve core receives equal when the valve core works, no matter axial air intake or radial air intake, through the equal force area of the upper and lower surfaces of the valve core, on the one hand, only small spring force is needed to open the valve port, so that the opening operation is more comfortable and controllable, the response speed is faster, on the other hand, the valve core only bears the electromagnetic force in the direction of pressing the valve seat, does not bear additional upward or downward gas pressure, the pressing force between the valve core and the valve seat, that is, the sealing of the valve port is only guaranteed by the electromagnetic force, the sealing effect is good, and the sealing performance is more stable.

[0018] The foregoing rigidity valve connects the dynamic sealing assembly and the fixed iron in an integrated manner through the interference fit connection of the metal framework in the dynamic sealing assembly and the fixed iron, so that the dynamic sealing assembly is positioned and installed without the aid of the valve seat and the fixed iron, thereby simplifying the structure of the dynamic sealing, reducing the assembly difficulty and processing cost of the dynamic sealing.

[0019] The foregoing rigidity valve sets the annular protrusion on the lateral sealing rubber piece, so that the annular protrusion forms interference fit with the fixed iron, thereby further sealing the leakage channel between the fixed iron and the dynamic sealing assembly, increasing the sealing performance, and meanwhile not affecting the sealing effect of the sealing lip, ensuring the dynamic sealing performance.

[0020] The foregoing rigidity valve sets the annular protrusion as a multi-protrusion structure, increasing the reliability of the sealing, and through the clearance fit between the valve seat and the lateral sealing piece, avoids the contact between the lateral sealing rubber piece and the valve seat, prevents the deformation of the lateral sealing rubber piece, thereby ensuring the dynamic sealing performance and prolonging the service life of the lateral sealing rubber piece.

[0021] The foregoing rigidity valve adopts the variable diameter structure of the valve core, greatly reduces the risk of deformation and damage of the lateral sealing rubber piece during use, ensures the dynamic sealing performance, and greatly prolongs the service life of the lateral sealing rubber piece. BRIEF DESCRIPTION OF DRAWINGS

[0022] The accompanying drawings are used to better understand the utility model, and do not constitute undue limitation on the utility model. Among them:

[0023] Figure 1 is a structure schematic view of the rigidity valve in the preferred embodiment of the utility model;

[0024] Figure 2 is Figure 1 the rigidity valve about the local enlarged view of detail B;

[0025] Figure 3 is an axial sectional view of the metal framework in the preferred embodiment of the utility model;

[0026] Figure 4is another preferred embodiment of the utility model Figure 1 Partial enlarged view of the medium stiffness valve about detail B;

[0027] Figure 5 is another preferred embodiment of the utility model Figure 1 Enlarged view of the medium stiffness valve about detail B;

[0028] Figure 6 is a structure schematic view of the valve core adopting variable diameter when closing the valve port with the valve seat in the preferred embodiment of the utility model;

[0029] Figure 7 is a structure schematic view of the valve core adopting equal diameter when closing the valve port with the valve seat in the preferred embodiment of the utility model.

[0030] [The following mark is explained as follows]:

[0031] 11-electromagnetic module, 12-sleeve, 13-armature, 14-connecting rod, 15-spring, 16-fixed iron, 160-mounting notch, 161-interference fit groove, 162-rubber accommodating groove, 163-sealing lip accommodating groove, 17-valve core, 171-first diameter section, 172-second diameter section, 18-valve seat, 181-valve port, 19-housing, 20-moving sealing assembly, 21, 22, 23-sealing ring, 24-valve port sealing rubber, 101, 102-two valve cavities; 31-metal framework, 311-center column, 312-annular flange, 3101-outer ring surface of the metal framework, 3102-lower surface of the metal framework, 32-lateral sealing rubber piece, 321-base, 322-sealing lip, 323-annular protrusion, D1-outer diameter of the first diameter section, D2-outer diameter of the second diameter section, D3-diameter of the sealing contact surface. DETAILED DESCRIPTION

[0032] The embodiments of the utility model are explained below through specific concrete examples, and the person skilled in the art can easily understand other advantages and effects of the utility model from the content disclosed in the specification. The utility model can also be implemented or applied through another different specific embodiment, and each detail in the specification can be modified or changed based on different viewpoints and applications without departing from the spirit of the utility model. It should be noted that the drawings provided in the embodiment only illustrate the basic concept of the utility model in a schematic manner, so the drawings only show the components related to the utility model without drawing the number, shape and size of the components in actual implementation, and the type, number and proportion of each component in actual implementation can be randomly changed, and the component layout type can also be more complex.

[0033] In addition, each of the following described embodiments has one or more technical features, and this does not mean that all technical features in any embodiment must be implemented at the same time, or only one or all technical features in different embodiments can be implemented separately. In other words, under the premise of being possible, the person skilled in the art can selectively implement part or all of the technical features in any embodiment according to the disclosure of the present application, and according to the design specification or implementation requirements, or selectively implement a combination of part or all of the technical features in multiple embodiments, thereby increasing the flexibility of the present application when implemented.

[0034] As used in this specification, the singular forms "a," "an" and "the" include plural referents unless the content clearly dictates otherwise. As used in this specification, the term "or" is generally employed in its sense of "and / or" unless the content clearly dictates otherwise, and the terms "mounting," "connected," and "connection" should be given their broadest possible interpretation, for example, they can be fixed connections, or detachable connections, or integrally connected. It can be a mechanical connection, or an electrical connection. It can be directly connected, or indirectly connected through an intermediate medium, it can be the internal communication of two elements or the interaction relationship between two elements. The relationship terms such as "first", "second" and the like are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between the entities or operations, nor indicate or imply relative importance or implicitly indicate the number of indicated technical features. It should be understood that the orientations or positional relationships indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential" and the like are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as limiting the present application. The device or element must have a specific orientation, be constructed and operated in a specific orientation, so it cannot be understood as a limitation of the present application. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0035] In the present application, the "upper surface" refers to the side away from the valve seat, the "lower surface" refers to the side facing the valve seat, the "outer peripheral surface" and the "outer annular surface" are the sides away from the central axis of the stiffness valve, the "inner annular surface" and the "inner side surface" are the sides close to the central axis of the stiffness valve, the "axial direction" refers to the direction along the central axis of the stiffness valve, the "circumferential direction" refers to the direction around the central axis of the stiffness valve, and the "radial direction" refers to the direction perpendicular to the central axis of the stiffness valve, that is, the transverse direction.

[0036] The utility model discloses a stiffness valve, which aims to effectively improve the response speed of the stiffness valve, increase the sealing effect and improve the sealing stability.

[0037] The stiffness valve provided by the utility model includes a valve core, a valve seat and a fixed iron, the fixed iron and the valve seat are sleeved with the valve core, the valve core can move axially relative to the fixed iron and the valve seat to selectively open or close the valve port on the valve seat.

[0038] Figure 1 Fig. 1 is a structural schematic view of a stiffness valve in an exemplary embodiment of the utility model. As shown in Fig. 1, the stiffness valve includes a valve core 1, a valve seat 2 and a fixed iron 3. Figure 1As shown, the stiffness valve includes electromagnetic module 11, sleeve 12, armature 13, connecting rod 14, spring 15, fixed iron 16, valve core 17, valve seat 18 and housing 19 and other components. The stiffness valve also generally includes sealing rings 21, 22 and 23. As shown, the top of the housing 19 is provided with a sealing ring 21, the bottom of the valve seat 18 is provided with a sealing ring 22, and in addition, the sealing ring 23 is provided between the fixed iron 16 and the housing 19. Of course, the number and position of the sealing rings 21, 22 and 23 can be reasonably adjusted according to the actual situation. Specifically, the electromagnetic module 11 is partially arranged in the housing 19 and fixedly connected with the housing 19; the sleeve 12 is located between the electromagnetic module 11 and the armature 13 and the fixed iron 16; and the armature 13 and the fixed iron 16 are arranged along the axial direction of the stiffness valve, and the fixed iron 16 needs to be located below the armature 13; and the upper end of the fixed iron 16 is connected with the sleeve 12, and the lower end of the fixed iron 16 is fixedly sleeved with the housing 19, for example, the fixed iron 16 and the sleeve 12 are first connected in interference, and then welded. In addition, the fixed iron 16 and the valve seat 18 are sleeved with the valve core 17, and the valve core 17 can move in the axial direction relative to the fixed iron 16 and the valve seat 18, so as to selectively open or close the valve port 181 on the valve seat 18. And the valve seat 18 is fixedly connected with the fixed iron 16 and the housing 19 respectively. At the same time, the fixed iron 16, the valve core 17, the spring 15 and the armature 13 are all sleeved on the connecting rod 14; the upper end of the connecting rod 14 is fixedly connected with the armature 13, and the lower end of the connecting rod 14 is fixedly connected with the valve core 17, for example, the connecting rod 14 is connected with the armature 13 and the valve core 17 in interference; and the lower end of the spring 15 is limited on the fixed iron 16, and the upper end of the spring 15 is limited on the armature 13; so that when the electromagnetic module 11 is powered off, the spring 15 releases the elastic potential energy, pushes the armature 13 to drive the valve core 17 to move upward and reset. The inner hole of the valve core 17 is usually provided with two through holes at the connection with the connecting rod 14, for connecting the cavities on the upper and lower sides of the valve core 17.

[0039] As can be understood, the working principle of the foregoing stiffness valve is as follows: when the electromagnetic module 11 is powered on, the armature 13 moves downward under the action of electromagnetic force, and drives the connecting rod 14 and the valve core 17 to move downward until the valve core 17 contacts the valve seat 18, thereby closing the valve port 181, and the bottom end of the valve core 17 and the valve seat 18 is provided with a valve port sealing rubber 24, the valve port sealing rubber 24 and the valve seat 18 form a sealing pair, and the outer periphery of the valve core 17 and the inner periphery of the fixed iron 16 are sealed by the dynamic sealing assembly 20, thereby cutting off the flow channel between the two valve cavities 101, 102; on the contrary, when the electromagnetic module 11 is powered off, the armature 13 moves upward under the action of the spring 15, synchronously drives the connecting rod 14 and the valve core 17 to move upward, opens the valve port 181, and re-connects the flow channel between the two valve cavities 101, 102.

[0040] In the aforementioned stiffness valve, the valve core 17 can be configured as a constant diameter structure or a variable diameter structure. For example... Figure 6 As shown, in one embodiment, the valve core 17 adopts a variable diameter structure. Specifically, the valve core 17 has a first diameter segment 171 and a second diameter segment 172, which are axially staggered. The outer diameter D2 of the second diameter segment 172 is larger than the outer diameter D1 of the first diameter segment 171; optionally, D2 is 0.15 mm larger than D1. There are at least two second diameter segments 172, and correspondingly, there are also at least two first diameter segments 171. When the valve port 181 is open, two corresponding first diameter segments 171 respectively engage with the upper and lower sealing lips 322 in the dynamic sealing assembly 20, resulting in minimal deformation of the sealing lips 322. Conversely, when the valve port 181 is closed, two corresponding second diameter segments 172 respectively engage with the upper and lower sealing lips 322 to ensure sealing performance and effective sealing time, resulting in significant deformation of the sealing lips 322. Figure 7 As shown, in another embodiment, the valve core 17 adopts a constant diameter structure with a fixed outer diameter D2. It should be understood that the outer diameters D1 and D2 of the valve core 17 are actually the outer diameters of the main body of the valve core 17 used to cooperate with the dynamic sealing assembly 20, and do not substantially include the outer diameter of the structure at the bottom end of the valve core 17 where the valve port sealing rubber 24 is installed.

[0041] Regardless of whether the valve core 17 has a variable or constant diameter, its upper and lower surfaces are designed to have equal force-bearing areas. This ensures that the upward and downward gas pressures P1 and P2 experienced by the valve core 17 during operation remain equal. Consequently, the valve core 17 does not experience any additional pressure difference, meaning the pressure difference is zero. With this configuration, when the valve port 181 is closed, the valve core 17 only experiences the electromagnetic force in the direction of pressing against the valve seat 18, without experiencing any additional upward or downward gas pressure. The sealing force between the valve core 17 and the valve seat 18, i.e., the seal of the valve port 181, is solely guaranteed by the electromagnetic force, resulting in a good sealing effect and more stable sealing performance. On the other hand, when the valve port 181 is opened, the valve core 17 only experiences the upward spring force, requiring only a small spring force to open the valve port 181, making the opening operation more comfortable and controllable, and significantly improving the response speed.

[0042] To ensure that the force-bearing areas of the upper and lower surfaces of the valve core 17 are equal, in one embodiment, such as... Figure 6 and Figure 7As shown, the diameter D3 of the sealing contact surface between the valve core 17 and the valve seat 18 is equal to the maximum outer diameter D2 of the valve core 17. In this case, no matter whether the axial air inlet (corresponding to P2) or the radial air inlet (corresponding to P1), the upper and lower action areas of the gas pressure borne by the valve core 17 are equal. Here, it can be understood that when the valve core 17 is of a variable-diameter structure, the diameter D3 of the sealing contact surface is equal to the outer diameter D2 of the second diameter section 172. It should also be noted that the valve port 181 is generally in the shape of a crater, and the sealing contact surface is the contact surface formed between the bottom end of the valve core 17 and the crater.

[0043] Specifically, in this embodiment, when the electromagnetic module 11 is powered on, the valve core 17 is in contact with the valve seat 18, the valve port 181 is closed, and the upper and lower sealing lips 322 in the dynamic sealing assembly 20 cooperate with the two second diameter sections 172 of the valve core 17 to form a dynamic sealing pair, so that the passages of the two valve cavities 101 and 102 of the stiffness valve are cut off, achieving good sealing performance; when the electromagnetic module 11 is powered off, the armature 13, the connecting rod 14 and the valve core 17 move upward under the action of the spring 15. At this time, since the upper and lower pressures and the action areas of the valve core 17 are equal, the valve core 17 will not bear additional upward or downward gas pressure, and the spring 15 only needs to overcome the weight of the moving parts itself to open the valve port 181, realizing the air flow of the two valve cavities 101 and 102. At this time, the upper and lower sealing lips 322 in the dynamic sealing assembly 20 cooperate with the two first diameter sections 1711 of the valve core 17, and the deformation of the sealing lips 322 is reduced.

[0044] Referring back to Figures 1 to 5 , preferably, the dynamic sealing assembly 20 comprises a metal skeleton 31 and a lateral sealing rubber piece 32; the lateral sealing rubber piece 32 is installed on the metal skeleton 31. Correspondingly, the inner side surface of the fixed iron 16 is provided with a mounting notch 160. The dynamic sealing assembly 20 is installed in the mounting notch 160, and the metal skeleton 31 is connected with the mounting notch 160 in an interference fit, so as to position and install the entire dynamic sealing assembly 20 between the valve core 17 and the fixed iron 16. In this way, the dynamic sealing assembly 20 does not need to be limited by the valve seat 18 and the fixed iron 16, thereby simplifying the structure of the dynamic sealing, reducing the assembly difficulty and processing cost of the dynamic sealing. In this way, the dynamic sealing assembly 20 and the fixed iron 16 are assembled and connected as a whole, and are used as an independent fixed iron assembly, which is very convenient to install and use.

[0045] Specifically, the lateral sealing rubber piece 32 cooperates with the valve core 17 to form a dynamic sealing pair, and the metal skeleton 31 is in clearance fit with the valve core 17 without contacting the valve core 17. Preferably, the valve seat 18 is in clearance fit with the lateral sealing rubber piece 32, so as to avoid the contact between the lateral sealing rubber piece 32 and the valve seat 18, prevent the lateral sealing rubber piece 32 from being deformed under stress, and further ensure the dynamic sealing performance and prolong the service life of the lateral sealing rubber piece 32.

[0046] It should also be understood that the metal skeleton 31 and the lateral sealing rubber member 32 are both annular structures. As shown in Figure 2 、 Figure 4 and Figure 5 , the lateral sealing rubber member 32 is mainly installed on the metal skeleton 31 in a sleeved manner, i.e. the lateral sealing rubber member 32 is sleeved on the outside of the metal skeleton 31, and the metal skeleton 31 is embedded in the inside of the lateral sealing rubber member 32, but the lateral sealing rubber member 32 also exposes part of the metal skeleton 31, so that the metal skeleton 31 can be connected with the fixed iron 16 in an interference fit. Preferably, the lateral sealing rubber member 32 and the metal skeleton 31 are integrally formed by rubber vulcanization, i.e. the lateral sealing rubber member 32 is integrally vulcanized on the metal skeleton 31; this structure is simple, convenient to process, has good joint firmness, and also has good overall sealing performance.

[0047] During the vulcanization process, preferably, a plurality of through holes are arranged on the central column 311 of the metal skeleton 31 in the radial direction to increase the flowability of the rubber compound, and the through holes also increase the contact area between the rubber and the metal skeleton 31, thereby ensuring the adhesion between the two. More preferably, the plurality of through holes on the inner annular surface of the metal skeleton 31 are uniformly distributed. It should also be understood that after the rubber is vulcanized, the rubber exists in these through holes on the metal skeleton 31 as part of the lateral sealing rubber member 32.

[0048] In addition, the metal skeleton 31 can have any suitable shape. Alternatively, as shown in Figure 3 , the metal skeleton 31 includes a central column 311, and an annular flange 312 is arranged on the outer peripheral surface of the central column 311, and the annular flange 312 is shorter than the central column 311 at both axial ends. In this way, the metal skeleton 31 can be connected with the mounting slot 160 of the fixed iron 16 in an interference fit through the annular flange 312, i.e. the outer diameter of the annular flange 312 is greater than the maximum inner diameter of the mounting slot 160.

[0049] Continuing to refer to Figure 2 、 Figure 4 and Figure 5 , the lateral sealing rubber member 32 generally includes a base 321 and a sealing lip 322. The outside of the base 321 is provided with one sealing lip 322 on each of the upper and lower sides, and the two sealing lips 322 are bent away from each other, and both the upper and lower sealing lips 322 form a dynamic sealing pair with the valve core 17, so as to provide dynamic sealing when the valve core 17 falls and returns. At the same time, the base 321 needs to be accommodated in the mounting slot 160 and not in contact with the valve core 17.

[0050] Further, in view of the possible leakage between the lateral sealing rubber 32 and the fixed iron 16, preferably, the base 321 of the lateral sealing rubber 32 is in interference fit with the fixed iron 16 at a predetermined position to form a static sealing pair, thereby further sealing the leakage passage between the fixed iron 16 and the dynamic sealing structure 20. Specifically, at least one of the upper surface, the lower surface and the outer circumferential surface of the base 321 is in interference fit with the fixed iron 16.

[0051] It is also found that when the base 321 is directly in interference fit with the fixed iron 16, the planar sealing of the base 321 is deformed too much, and the deformation of the base 321 is easily transmitted to the sealing lip 322 area, affecting the sealing effect of the sealing lip 322. Therefore, preferably, an annular protrusion 323 is arranged on the outer surface of the base 321, and the annular protrusion 323 is located between the fixed iron 16 and the base 321, in interference fit with the fixed iron 16 to form a static sealing pair, while the base 321 needs to be in clearance fit with the fixed iron 16 without contact. Optionally, the annular protrusion 323 is arranged on at least one of the upper surface, the lower surface and the outer circumferential surface of the base 321. The annular protrusion 323 is one or more. Compared with the direct interference fit between the base 321 and the fixed iron 16, the annular protrusion 323 can be designed with a smaller interference amount under the same sealing effect, without affecting the sealing effect of the sealing lip 322.

[0052] Preferably, the upper surface and the lower surface of the base 321 are both provided with the annular protrusion 323, which can be symmetric or asymmetric, and preferably, the annular protrusion 323 is symmetrically arranged. In addition, the annular protrusion 323 is arranged as far away from the sealing lip 322 as possible, for example, close to the outer circumferential surface of the base 321, so that the deformation of the annular protrusion 323 is transmitted to the sealing lip 322 area, affecting the sealing effect of the main leakage passage.

[0053] The annular protrusion 323 can be made into various shapes, such as at least one of point, line and surface, and can also be various shapes such as sharp, blunt, round and non-round, as long as the annular protrusion 323 can have a certain interference amount with the corresponding groove wall of the mounting slot 160. More suitably, the annular protrusion 323 is a point structure, for example, the annular protrusion 323 is a single protruding point structure (see Figure 4 ), or the annular protrusion 323 is a multi-protruding point structure (see Figure 5 ). The multi-protruding point structure can be a double-protruding point structure or other multi-protruding point structure. The multi-protruding point structure is preferred, and the local contact stress is higher, which is more reliable than the planar sealing. It should be understood that adjacent protruding points in the multi-protruding point structure are recessed.

[0054] In this embodiment, the annular protrusion 323 adopts a double convex point structure, and the double convex points locally contact with high stress, and the sealing effect is reliable. Alternatively, when the annular protrusion 323 is a double convex point structure, each convex point can be provided in a circular arc shape, and the circular arc radius, the distance between the two convex points, and the convex point height can be reasonably set according to actual needs. For example, alternatively, when there is no interference fit, the radii of the two convex points of the annular protrusion 323 are consistent, the convex point radius is 0.3-0.5 mm, and the convex point height is 0.15-0.3 mm. Of course, in practice, it can not be limited to this. It should be noted that when the annular protrusion 323 is a single convex point, it means that the annular protrusion 323 only has a maximum height at a corresponding position; when the annular protrusion 323 is a multi-convex point, it means that the annular protrusion 323 has a maximum height at a plurality of corresponding positions.

[0055] Further, when the dynamic sealing assembly 20 is installed, a part of the structure of the installation notch 160 is connected with the metal framework 31 in an interference fit, and another part of the structure of the installation notch 160 is used to accommodate the lateral sealing rubber part 32. As shown in Figure 2 In an embodiment, the installation notch 160 is a stepped structure, including an interference fit groove 161, a rubber accommodating groove 162, and a sealing lip accommodating groove 163 arranged in the radial direction from inside to outside. Here, "inside" and "outside" are relative to the position of the center axis of the anchor iron 16, "inside" is the position farther away from the center axis of the anchor iron 16, and "outside" is the position closer to the center axis of the anchor iron 16. That is, the interference fit groove 161 is provided outside the rubber accommodating groove 162, the rubber accommodating groove 162 is provided outside the sealing lip accommodating groove 163, and the sealing lip accommodating groove 163 is close to the valve core 17.

[0056] Therefore, the metal framework 31 is connected with the interference fit groove 161 in an interference fit, the base 321 of the lateral sealing rubber part 32 is located in the rubber accommodating groove 162, and the sealing lip 322 of the lateral sealing rubber part 32 is located in the sealing lip accommodating groove 163. The sealing lip 322 protrudes from the sealing lip accommodating groove 163 in the radial direction of the anchor iron 16 to fit on the outer surface of the valve core 17. The sealing lip accommodating groove 163 can accommodate the sealing lip 322 when the sealing lip 322 is deformed under stress. In addition, the installation notch 160 axially penetrates the anchor iron 16 close to the bottom of the valve seat 18, so that the bottom of the installation notch 160 is provided in an open manner, thereby facilitating the machining of the anchor iron 16 and the installation of the dynamic sealing assembly 20. Therefore, the installation notch 160 is open in the radial direction towards the valve core 17 and in the axial direction towards the valve seat 18. It should also be understood that the interference fit groove 161, the rubber accommodating groove 162, and the sealing lip accommodating groove 163 are all concave structures arranged around the anchor iron 16.

[0057] Based on this, as Figure 2and Figure 3 As shown, the outer annular surface 3101 of the metal skeleton 31 is connected with the interference fit groove 161 through interference fit, and the lower surface 3102 of the metal skeleton 31 is not in contact with the valve seat 18 but has a gap. In this embodiment, the annular flange 312 is connected with the fixed iron 16 through interference fit via its outer annular surface 3101. In addition, referring to Figure 2 As shown, the outer annular surface 3101 of the metal skeleton 31 is connected with the interference fit groove 161 through interference fit, and the lower surface 3102 of the metal skeleton 31 is not in contact with the valve seat 18 but has a gap. In this embodiment, the annular flange 312 is connected with the fixed iron 16 through interference fit via its outer annular surface 3101. In addition, referring to

[0058] As shown, the outer annular surface 3101 of the metal skeleton 31 is connected with the interference fit groove 161 through interference fit, and the lower surface 3102 of the metal skeleton 31 is not in contact with the valve seat 18 but has a gap. In this embodiment, the annular flange 312 is connected with the fixed iron 16 through interference fit via its outer annular surface 3101. In addition, referring to

[0059] Although the present utility model discloses as above, but is not limited to this. The person skilled in the art can make various modifications and variations to the present utility model without departing from the spirit and scope of the present utility model. Thus, if these modifications and variations of the present utility model belong to the scope of the present utility model and its equivalent technology, then the present utility model also intends to include these modifications and variations.

Claims

1. A stiffness valve characterized by, The valve core is capable of moving axially relative to the fixed iron and the valve seat to selectively open or close the valve port on the valve seat, and the valve core is arranged such that the upper and lower surface areas are equal to make the upward and downward gas pressure on the valve core equal.

2. The stiffness valve of claim 1, wherein The diameter of the sealing contact surface of the valve core and the valve port is equal to the maximum outer diameter of the valve core.

3. The stiffness valve of claim 2, wherein The valve core has a first diameter section and a second diameter section, the outer diameter of the second diameter section is greater than that of the first diameter section, the first diameter section and the second diameter section are staggered, and the diameter of the sealing contact surface is equal to the outer diameter of the second diameter section; or the valve core is of equal diameter structure.

4. The stiffness valve of claim 1 or 2, wherein The dynamic sealing assembly is further provided between the valve core and the fixed iron, and the dynamic sealing assembly comprises a metal skeleton and a lateral sealing rubber piece.

5. The stiffness valve of claim 4, wherein, The lateral sealing rubber piece and the metal skeleton are integrally formed by rubber vulcanization.

6. The stiffness valve of claim 4, wherein The lateral sealing rubber piece comprises a base and a sealing lip, the outer portion of the base is provided with one sealing lip on each of the upper and lower sides, the two sealing lips are bent away from each other, an annular protrusion is arranged on the outer surface of the base, the annular protrusion and the fixed iron form a static sealing pair through interference fit, and the base and the fixed iron are in clearance fit.

7. The stiffness valve of claim 6, wherein The upper surface and the lower surface of the base are both provided with the annular protrusion, and the annular protrusion is arranged away from the sealing lip.

8. The stiffness valve of claim 6, wherein The annular protrusion is a single convex point structure or a multi-convex point structure.

9. The stiffness valve of claim 6, wherein, The installation slot comprises an interference fit groove, a rubber accommodating groove and a sealing lip accommodating groove arranged in the radial direction from inside to outside and distributed in steps, the metal skeleton is connected with the interference fit groove through interference fit, the base is located in the rubber accommodating groove, and the sealing lip is located in the sealing lip accommodating groove, the sealing lip protrudes from the sealing lip accommodating groove in the radial direction of the fixed iron, and the installation slot axially penetrates through the bottom of the fixed iron, so that the bottom of the installation slot is open.

10. The stiffness valve of claim 4, wherein The metal skeleton comprises a center column, an annular flange is arranged on the outer circumferential surface of the center column, the annular flange is lower than the center column at both ends in the axial direction, the annular flange is connected with the installation slot through interference fit, and / or a plurality of through holes are arranged on the center column of the metal skeleton in the radial direction, and the plurality of through holes are uniformly distributed.

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