Stop valve and air conditioning system

Abstract

The application relates to a stop valve and an air conditioning system. The stop valve comprises a valve seat and a valve core, the valve seat is provided with a valve cavity, the valve core is movably arranged in the valve cavity, a first taper surface is arranged on the inner wall of the valve cavity, the valve core is provided with a second taper surface, the valve core is configured to form a face seal by extrusion of the second taper surface and the first taper surface when under pressure, and the width W2 of the second taper surface along the generatrix direction is greater than the width W1 of the first taper surface along the generatrix direction. The stop valve provided by the application can improve the sealing reliability of the stop valve.

Description

[0001] Cross-references to related applications

[0002] This application claims priority to Chinese patent application CN202621111329.X, filed on July 21, 2026, entitled “Stop Valve and Air Conditioning System”, the entire contents of which are incorporated herein by reference. Technical Field

[0003] This application relates to the field of valve component technology, and in particular to a shut-off valve and an air conditioning system. Background Technology

[0004] Gate valves, as common fluid control components, are widely used in refrigeration and air conditioning, hydraulic transmission, and industrial piping systems. They rely on the sealing fit between the valve core and the valve seat to control the flow of fluid. The valve seat, as a key sealing component in a gate valve, directly affects the sealing reliability and service life of the entire valve due to its structural form.

[0005] In existing gate valve designs, the common sealing structure of the valve seat is a pointed-corner structure. Specifically, this refers to a right-angled step structure on the valve seat that mates with the valve core to achieve a seal. The apex of this right-angled step structure forms a sealing contact with the inclined surface of the valve core. During valve closing, the valve core moves towards the valve seat under the action of driving force. The inclined surface of the valve core presses against the apex of the right-angled step structure of the valve seat, achieving a seal through the pointed tip.

[0006] However, the sharp-angled structure results in an excessively small contact area between the valve seat and the valve core, causing a high concentration of sealing stress in the extremely small area of ​​the sharp corner. Under the combined effects of high-pressure conditions and repeated switching operations, the tip of the sharp corner is highly susceptible to penetrating scratches, localized defects, or even fatigue spalling, leading to insufficient sealing reliability.

[0007] Therefore, it is necessary to propose a new technical solution to overcome the shortcomings of existing technologies. Utility Model Content

[0008] Based on this, this application provides a shut-off valve and an air conditioning system, which can improve the sealing reliability of the shut-off valve.

[0009] Therefore, this application adopts the following technical solution: a shut-off valve, including a valve seat and a valve core, wherein the valve seat has a valve cavity, the valve core is movably disposed in the valve cavity, a first conical surface is provided on the inner wall of the valve cavity, the valve core is provided with a second conical surface, and the valve core is configured to form a surface seal by the compression of the second conical surface and the first conical surface when under pressure, wherein the width W2 of the second conical surface along the generatrix direction is greater than the width W1 of the first conical surface along the generatrix direction.

[0010] In some embodiments, under the compression sealing state, the first conical surface is within the coverage area of ​​the second conical surface, such that the width of the first conical surface along the generatrix direction constitutes the width of the surface seal, and the first conical surface and the second conical surface are fitted together.

[0011] In some embodiments, the width of the second conical surface along the generatrix direction is 2 to 6 times the width of the first conical surface along the generatrix direction.

[0012] In some embodiments, the minor diameter of the second cone is smaller than the minor diameter of the first cone, and the major diameter of the second cone is larger than the major diameter of the first cone.

[0013] In some embodiments, the ratio of the arithmetic mean of the major and minor diameters of the first conical surface to the arithmetic mean of the major and minor diameters of the second conical surface is 0.5 to 2.

[0014] In some embodiments, the angle α between the first and second conical surfaces and the radial plane of the valve core is 15° to 75°.

[0015] In some embodiments, under the compression sealing state, both the large-diameter edge and the small-diameter edge of the second conical surface are suspended in a state that does not contact the valve seat.

[0016] In some embodiments, the valve core has a higher hardness than the valve seat.

[0017] In some embodiments, the inner wall of the valve cavity has a stepped surface above the first conical surface, and the inner diameter of the stepped surface is larger than the major diameter of the second conical surface.

[0018] This application also adopts the following technical solution: an air conditioning system, including a shut-off valve as described in any of the above embodiments.

[0019] The gate valve provided in this application has a valve core second conical surface width W2 along the generatrix direction that is larger than the valve seat first conical surface width W1 along the generatrix direction. This allows the valve core conical surface to form a surface seal contact with the valve seat conical surface with a wider coverage area during sealing, effectively increasing the contact area between the valve seat and the valve core. This avoids the problem of high stress concentration caused by insufficient contact area due to sharp corner structures. Simultaneously, it ensures a uniform and complete sealing contact zone between the valve core conical surface and the valve seat conical surface, effectively avoiding the potential for localized failure due to edge contact of the conical surfaces. Therefore, the gate valve provided in this application improves the sealing reliability and service life of the gate valve. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of this application or the conventional technology, the drawings used in the description of the embodiments or the conventional technology will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a perspective view of an embodiment of the shut-off valve of this application.

[0022] Figure 2 This is a cross-sectional view of an embodiment of the shut-off valve of this application, wherein the valve core and valve seat are in the open state.

[0023] Figure 3 This is a cross-sectional view of an embodiment of the shut-off valve of this application, wherein the valve core and the valve seat are in a sealed state.

[0024] Figure 4 This is a partial enlarged view of an embodiment of the shut-off valve of this application.

[0025] Figure 5 for Figure 2 A magnified view of a portion of point A in the middle.

[0026] Figure 6 for Figure 3 A magnified view of a section at point B.

[0027] The components are labeled as follows: 1. Valve seat; 10. Valve cavity; 11. First conical surface; 111. First major diameter edge; 112. First minor diameter edge; 12. Stepped surface; 2. Valve core; 21. Second conical surface; 211. Second major diameter edge; 212. Second minor diameter edge. Detailed Implementation

[0028] To make the above-mentioned objectives, features, and advantages of this application more apparent and understandable, the specific embodiments of this application are described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of this application. However, this application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this application. Therefore, this application is not limited to the specific embodiments disclosed below.

[0029] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on the other component or there may be an intermediate component. When a component is considered to be "connected to" another component, it can be directly connected to the other component or there may be an intermediate component present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used in this application are for illustrative purposes only and do not represent the only possible implementation.

[0030] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0031] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature and the second feature are in indirect contact through an intermediate medium. Furthermore, "above," "over," and "on top" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0032] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains. The terminology used in this application is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. The term "and / or" as used in this application includes any and all combinations of one or more of the associated listed items.

[0033] Please see Figures 1 to 6 This application provides a shut-off valve. This shut-off valve can be applied to refrigeration and air conditioning systems, hydraulic transmission systems, and various industrial pipeline systems for controlling the flow of fluid. The shut-off valve includes a valve seat 1 and a valve core 2. The valve seat 1 has a valve cavity 10 extending along the axial direction of the valve seat 1, which accommodates the valve core 2 and provides space for its movement. The valve core 2 is movably disposed in the valve cavity 10 and can be driven to reciprocate along the axial direction of the valve seat 1, thereby realizing the opening and closing of the shut-off valve.

[0034] In this application, a first conical surface 11 is provided on the inner wall of the valve cavity 10 of the valve seat 1. The first conical surface 11 is located on the inner wall of the valve seat 1 near the moving end of the valve core 2, and is used to form a sealing fit with the valve core 2 when the shut-off valve is closed. In this embodiment, the first conical surface 11 is a conical structure with a certain taper along the axial direction of the valve seat 1. Specifically, the small-diameter end of the first conical surface 11 forms a first small-diameter edge 112, and the large-diameter end of the first conical surface 11 forms a first large-diameter edge 111. In the axial section of the valve seat 1, the first conical surface 11 appears as a diagonal line, which connects the first small-diameter edge 112 and the first large-diameter edge 111. The generatrix of the first conical surface 11 is the diagonal line, and its width W1 along the generatrix direction is the dimension of the first conical surface 11 in the diagonal direction, which corresponds to the sealing band width of the first conical surface 11.

[0035] Correspondingly, the valve core 2 is provided with a second conical surface 21. The second conical surface 21 is located at the end of the valve core 2 facing the valve seat 1, and is used to cooperate with the first conical surface 11 of the valve seat 1 when the shut-off valve needs to be closed. In this embodiment, the second conical surface 21 is also a conical surface structure, with its small-diameter end forming a second small-diameter edge 212 and its large-diameter end forming a second large-diameter edge 211. In the axial section of the valve core 2, the second conical surface 21 appears as a diagonal line, which connects the second small-diameter edge 212 and the second large-diameter edge 211. The generatrix of the second conical surface 21 is this diagonal line, and its width W2 along the generatrix direction is the dimension of the second conical surface 21 in the diagonal line direction. The valve core 2 is configured to form a surface seal by the compression of the second conical surface 21 and the first conical surface 11 when under pressure. Specifically, when the shut-off valve needs to be closed, the valve core 2 moves toward the valve seat 1 under the action of the driving force, and the second cone surface 21 gradually approaches and finally squeezes the first cone surface 11, forming an annular sealing contact zone between the two, thereby achieving a shut-off seal for the fluid.

[0036] It should be noted that, in the preferred embodiment, the first conical surface 11 and the second conical surface 21 are standard conical surface structures; however, the conical surface in this application is not limited to this. The conical surface mentioned in this application refers to a surface that is larger at one end and smaller at the other end, and whose size gradually changes from one end to the other end. It can also be an approximate conical surface, a pyramidal surface, an approximate pyramidal surface, etc.

[0037] like Figure 5As shown in this application, the width W2 of the second conical surface 21 along the generatrix direction is greater than the width W1 of the first conical surface 11 along the generatrix direction. In existing gate valve designs, the sealing structure of the valve seat 1 typically adopts a sharp-angle structure, that is, the part of the valve seat 1 that mates with the valve core 2 is sharp-angled, and the tip of this sharp-angle structure forms line contact with the inclined part on the valve core 2. Due to the small contact area, the sealing contact stress is highly concentrated in the extremely small area of ​​the sharp angle. Under high pressure conditions and repeated switching operations, the tip of the sharp angle is prone to penetrating scratches, local defects, or even fatigue spalling, resulting in insufficient sealing reliability. In contrast, this application adopts a surface seal. This surface seal contact method effectively increases the contact area between the valve seat 1 and the valve core 2, dispersing the stress originally concentrated in the extremely small area of ​​the sharp angle to the entire surface seal contact band, thereby significantly reducing the unit area stress of the sealing part of the valve seat 1. The reduced force per unit area means that the elastic deformation of the valve seat 1 sealing surface is smaller under the same working conditions, making it less likely to reach the material's yield limit. Therefore, it can effectively reduce the risk of penetrating scratches, local defects, and fatigue spalling, significantly improving the sealing reliability and service life of the gate valve under high pressure and repeated switching conditions. Furthermore, by setting the generatrix width W2 of the second conical surface 21 of the valve core 2 to be greater than the generatrix width W1 of the first conical surface 11 of the valve seat 1, the second conical surface 21 of the valve core 2 can form a surface sealing contact with the first conical surface 11 of the valve seat 1 with a wider coverage area during sealing. This ensures that the sealing contact zone between the valve core 2 and the valve seat 1 is uniform and complete, effectively avoiding the potential for local failure caused by contact at the edge of the conical surface.

[0038] In the compression sealing state, the first conical surface 11 is within the coverage area of ​​the second conical surface 21. The coverage area refers to the fact that the extension of the second conical surface 21 in the generatrix direction completely covers the extension of the first conical surface 11 in the generatrix direction. In other words, when the valve core 2 and valve seat 1 are in a sealed fit, the first conical surface 11 and the second conical surface 21 are fitted together, and both ends of the first conical surface 11 along the generatrix direction, namely the first minor diameter edge 112 and the first major diameter edge 111, fall between the two ends of the second conical surface 21 along the generatrix direction, that is, between the second minor diameter edge 212 and the second major diameter edge 211. This coverage relationship ensures that the entire width of the first conical surface 11 along the generatrix direction participates in the sealing contact, and the width of the first conical surface 11 along the generatrix direction constitutes the actual width of the surface seal. Through this arrangement, the width of the sealing contact band is determined by the generatrix width of the first conical surface 11, and the generatrix width of the first conical surface 11 can be precisely controlled according to design requirements, thereby ensuring the consistency of the width of the sealing contact band. Meanwhile, since the coverage area of ​​the second conical surface 21 is larger than that of the first conical surface 11, even with certain machining errors or assembly misalignment, the first conical surface 11 can still fall completely within the coverage area of ​​the second conical surface 21, thus ensuring the integrity and continuity of the sealing contact strip. This design has a higher tolerance for machining errors and assembly misalignment, further ensuring the consistency and stability of sealing performance in mass production.

[0039] Please see Figure 4 As shown, the minor diameter d2 of the second conical surface 21 is set to be smaller than the minor diameter d1 of the first conical surface 11, while the major diameter D2 of the second conical surface 21 is set to be larger than the major diameter D1 of the first conical surface 11. Specifically, in the axial section of the valve seat 1 and the valve core 2, the minor diameter end of the second conical surface 21 is located radially inside the minor diameter end of the first conical surface 11, while the major diameter end of the second conical surface 21 is located radially outside the major diameter end of the first conical surface 11. This structure simultaneously ensures that during the compression sealing process, the major diameter edge (i.e., the second major diameter edge 211) and the minor diameter edge (i.e., the second minor diameter edge 212) of the second conical surface 21 do not contact the major diameter edge (i.e., the first major diameter edge 111) and the minor diameter edge (i.e., the first minor diameter edge 112) of the first conical surface 11. Since the two end edges of the second conical surface 21 do not participate in the sealing contact, these edge areas will not be worn or deformed due to repeated compression, thereby maintaining the overall geometric accuracy of the second conical surface 21, which is beneficial to maintaining the sealing performance during long-term use.

[0040] Furthermore, in some embodiments, the ratio of the arithmetic mean of the major and minor diameters of the first conical surface 11 to the arithmetic mean of the major and minor diameters of the second conical surface 21 is configured to be between 0.5 and 2. This arithmetic mean reflects the relative position of the first conical surface 11 with respect to the second conical surface 21 in the axial direction, effectively defining the degree of centering of the first conical surface 11 relative to the second conical surface 21. When this ratio is in the range of 0.5 to 2, the first conical surface 11 is approximately located in the central region of the second conical surface 21. This centering ensures that the sealing contact strip is located in the center of the second conical surface 21, allowing sufficient clearance at both the major and minor diameter ends of the second conical surface 21. If the ratio is too large, such as greater than 2, it indicates that the first conical surface 11 is closer to the upper end of the second conical surface 21. In this case, the second conical surface 21 has insufficient clearance at the large diameter end, posing a risk of edge contact. If the ratio is too small, such as less than 0.5, it indicates that the first conical surface 11 is closer to the lower end of the second conical surface 21. In this case, the second conical surface 21 has insufficient clearance at the small diameter end, also posing a risk of edge contact. Therefore, controlling the ratio of their average positions within the range of 0.5 to 2 ensures that the first conical surface 11 and the second conical surface 21 have good centering and symmetry during sealing, resulting in a more uniform stress distribution in the sealing contact zone. Preferably, this ratio is set between 0.8 and 1.5; in some specific embodiments, this ratio can be 0.9, 1, 1.1, 1.2, 1.3, 1.4, etc. The sealing contact strip is stably distributed in the middle region of the conical surface of valve core 2, effectively avoiding the stress-weak areas at the upper and lower edges of the conical surface. The sealing specific pressure is more uniformly distributed along the contact width direction, and there are no edge stress peaks. Based on this uniform contact stress distribution characteristic, the width of the conical surface can be quantitatively designed according to the rated closing torque, the working pressure of the medium, and the allowable specific pressure of the valve seat 1 material. This ensures that the sealing specific pressure is always higher than the minimum sealing specific pressure required by the medium under the rated torque, while being lower than the allowable compressive stress of the valve seat 1 material, thus balancing the dual requirements of sealing performance and structural strength. In addition, the structure of the sealing contact strip located in the middle of the conical surface can also effectively prevent particulate impurities in the medium from accumulating or embedding at the edge of the sealing surface, significantly reducing the risk of particles scratching the sealing surface. Specifically, the inner and outer boundaries of the contact strip are both on a continuous and smooth conical surface, without any sharp corners affecting the direction of medium flow. When the valve is opened and closed, solid particles in the medium are less likely to embed at the sealing contact boundary, effectively reducing the risk of particles being squeezed into the sealing surface by the valve core and causing through-scratches on the working surface. In addition, since there is no local stress due to the absence of sharp corner structures, the uniform surface contact stress distribution can effectively reduce the risk of stress corrosion on the sealing surface under corrosive media conditions, effectively improve the corrosion resistance and sealing ability of the sealing structure under corrosive media conditions, and enhance the reliability of the seal.

[0041] In some embodiments, the width of the second conical surface 21 along the generatrix direction is set to be 2 to 6 times the width of the first conical surface 11 along the generatrix direction. From the perspective of sealing performance, the larger the width of the second conical surface 21 of the valve core 2 relative to the first conical surface 11 of the valve seat 1, the farther the edge of the sealing contact strip is from the edge of the second conical surface 21, the more uniform the distribution of sealing contact stress on the contact strip, the weaker the edge stress concentration effect, and the higher the sealing reliability. At the same time, if the widths of the two differ by a large factor, the area size will be mismatched, and many second conical surfaces 21 will be in a useless state. When the generatrix width of the second conical surface 21 is 2 to 6 times the generatrix width of the first conical surface 11, it can ensure that the sealing contact strip has sufficient width margin to eliminate edge stress concentration, and it will not cause a large number of second conical surfaces 21 to be idle due to a large area difference.

[0042] Please see Figures 4 to 6 In a sealed fit, a surface seal is formed between the first conical surface 11 and the second conical surface 21. Specifically, the surface of the first conical surface 11, spanning the entire generatrix width, contacts and presses against the corresponding area of ​​the second conical surface 21. This surface seal differs from the sharp-angle seals in the prior art, where the contact line between the sharp corner of the valve seat 1 and the inclined surface of the valve core 2 is extremely narrow, resulting in extremely high contact stress. In the surface seal of this application, the first conical surface 11 of the valve seat 1, as a complete conical surface, fits against the second conical surface 21 of the valve core 2, and the contact stress is evenly distributed across the entire conical surface. To achieve the aforementioned surface seal, the first conical surface 11 of the valve seat 1 and the second conical surface 21 of the valve core 2 are configured to have matching conical angles. Specifically, the angle between the first conical surface 11 and the second conical surface 21 and the radial plane of the valve core 2, i.e. Figure 4 The angle α shown is set between 15° and 75°. When this angle is too small, the conical surface tends to be parallel to the radial plane of the valve core 2. At this time, under the same axial closing force, the normal sealing force of the conical surface will decrease, resulting in insufficient sealing pressure and reduced sealing performance. When this angle is too large, the conical surface tends to be parallel to the axis of the valve core 2. At this time, although the sealing pressure is large, the lower part of the first conical surface 11 of the valve seat 1 lacks sufficient support. When the conical surface is subjected to excessive force, it is easy for the sealing surface to collapse and deform. After extensive experimental verification, when the conical surface angle is within the range of 15° to 75°, it can ensure sufficient sealing pressure to meet the sealing requirements and ensure that the first conical surface 11 of the valve seat 1 has sufficient structural strength to withstand the compressive load during closing. More preferably, the included angle between the first conical surface 11 and the second conical surface 21 and the radial plane of the valve core 2 is set between 30° and 60°. Within this narrower angle range, the sealing performance and structural strength are both in a better balance, and the manufacturability is also better, which is convenient for precision control in mass production. In some specific embodiments, the included angle can be set to 40°, 45°, 50°, 55°, etc.

[0043] Please see Figure 4 and Figure 6 In the sealed fit state, both the large-diameter edge (i.e., the second large-diameter edge 211) and the small-diameter edge (i.e., the second small-diameter edge 212) of the second conical surface 21 are suspended in a state of non-contact with the valve seat 1. The term "suspended in a state" means that there is a certain gap between the second large-diameter edge 211 and the surface of the valve seat 1 in space, and the two do not come into contact. In this application, since the generatrix width of the second conical surface 21 is greater than the generatrix width of the first conical surface 11, and the first conical surface 11 is completely covered by the second conical surface 21, the large-diameter edge of the second conical surface 21 is radially located above the large-diameter edge of the first conical surface 11, and the small-diameter edge of the second conical surface 21 is radially located below the small-diameter edge of the first conical surface 11. In other words, both ends of the second conical surface 21 extend beyond both ends of the first conical surface 11. This dimensional relationship ensures that, in the sealed state, neither the large-diameter nor the small-diameter edge of the second conical surface 21 contacts the valve seat 1, creating a clearance between them. This clearance concentrates the sealing contact stress in the radially central region of the second conical surface 21, corresponding to the region of the first conical surface 11. This effectively prevents localized overload deformation and micro-fatigue cracks caused by edge stress concentration, improving the service life of the sealing structure under high-pressure alternating loads. Secondly, since the edges of the second conical surface 21 do not participate in the sealing contact, these edge areas will not experience wear or deformation due to repeated compression, thus maintaining the overall geometric accuracy of the second conical surface 21 and contributing to the maintenance of sealing performance during long-term use. Furthermore, the suspended edge state provides space for the slight sway of the valve core 2 during the closing process. Even if the valve core 2 has slight eccentricity due to machining errors or assembly reasons, the edge of the second conical surface 21 will not interfere with the valve seat 1, ensuring the reliability of the sealing contact.

[0044] Please see Figure 5 and Figure 6 In this embodiment, the inner wall of the valve cavity 10 of the valve seat 1 is further provided with a stepped surface 12 above the first conical surface 11. The stepped surface 12 is located axially above the first conical surface 11, that is, on the side close to the valve core 2 in the inlet direction. The inner diameter of the stepped surface 12 is set to be larger than the major diameter of the second conical surface 21. Since the inner diameter of the stepped surface 12 is larger than the major diameter of the second conical surface 21, a certain radial gap is formed between the two. This radial gap can act as a fluid buffer area, where the flow state of the medium changes before entering the sealing strip, and the kinetic energy is reduced to a certain extent, thereby reducing the direct erosion of the sealing surface by the high-speed medium and helping to extend the service life of the sealing surface.

[0045] In this application, the hardness of the valve core 2 is set to be higher than that of the valve seat 1. During the repeated opening and closing of the shut-off valve, there is relative fretting friction between the valve core 2 and the valve seat 1. If the hardness of the two are the same or the hardness of the valve core 2 is lower than that of the valve seat 1, both may wear, and the amount of wear is difficult to control. By setting the hardness of the valve core 2 to be higher than that of the valve seat 1, deformation and wear mainly occur on the valve seat 1 side during sealing compression and fretting friction, and the second conical surface 21 of the valve core 2 can maintain its geometric shape and dimensional accuracy for a long time. As a relatively soft component, the valve seat 1 undergoes a suitable amount of elastic deformation during sealing compression. This deformation is conducive to forming a more closely fitting surface seal between the first conical surface 11 of the valve seat 1 and the second conical surface 21 of the valve core 2. At the same time, due to the lower hardness of the valve seat 1, minor scratches and defects on its surface can be repaired to a certain extent through deformation during subsequent sealing compression, thereby extending the overall service life of the sealing pair. In a specific embodiment, the valve core 2 is made of steel, and the valve seat 1 is made of copper.

[0046] The working process of the gate valve of this application will be described in detail below with reference to the accompanying drawings.

[0047] Please see Figure 2 and Figure 5 This diagram illustrates the structure of the shut-off valve in the open state. In the open state, the second conical surface 21 of the valve core 2 is separated from the first conical surface 11 of the valve seat 1. At this time, the flow path within the valve cavity 10 of the valve seat 1 is unobstructed, allowing the medium to flow from one side of the valve seat 1 to the other. In the open state, the second conical surface 21 and the first conical surface 11 maintain a certain axial distance and do not contact each other, thus preventing sealing and wear.

[0048] Please see Figure 3 and Figure 6This diagram illustrates the structure of the shut-off valve in its sealed closed state. When the shut-off valve needs to be closed, the operator applies force to the valve core 2 using a tool, driving the valve core 2 downwards. The valve core 2 gradually approaches the valve seat 1, and the second conical surface 21 gradually approaches the first conical surface 11. As the valve core 2 continues to move downwards, the second conical surface 21 and the first conical surface 11 begin to contact and press against each other. Since the generatrix width of the second conical surface 21 is greater than that of the first conical surface 11, the first conical surface 11 falls completely within the coverage area of ​​the second conical surface 21. Under the action of the pressing force, the first conical surface 11 of the valve seat 1 undergoes a suitable amount of elastic deformation, forming a tight-fitting surface seal with the second conical surface 21 of the valve core 2. At this time, the entire surface of the first conical surface 11 within its generatrix width is in contact with the corresponding area of ​​the second conical surface 21, and the sealing contact band is uniform and complete. At the same time, the large-diameter edge and the small-diameter edge of the second conical surface 21 are both suspended, maintaining a gap with the valve seat 1, and do not participate in the sealing contact. In the sealed state, due to the significant increase in sealing contact area compared to the sharp-corner structure, the contact stress is evenly distributed, and the unit area of ​​the first conical surface 11 of the valve seat 1 is significantly reduced, thereby effectively avoiding scratches and defects caused by stress concentration.

[0049] During long-term use, the shut-off valve undergoes repeated opening and closing operations. During each closing operation, the second conical surface 21 of the valve core 2 comes into contact with the first conical surface 11 of the valve seat 1 through compression. Because the hardness of the valve core 2 is higher than that of the valve seat 1, deformation and wear are mainly concentrated on the first conical surface 11 of the valve seat 1. However, thanks to the stress dispersion effect brought about by the surface sealing structure, the stress per unit area borne by the first conical surface 11 of the valve seat 1 during each compression is within the elastic deformation range of the material, making it less prone to plastic deformation and cumulative damage. Therefore, even after thousands or even tens of thousands of opening and closing cycles, the first conical surface 11 of the valve seat 1 can still maintain good sealing performance and will not exhibit failure phenomena such as penetrating scratches, local defects, or fatigue spalling. Simultaneously, because the second conical surface 21 of the valve core 2 has high hardness and its edge area does not participate in sealing contact, the second conical surface 21 can maintain its geometric accuracy during long-term use and will not change its generatrix width and conical angle due to wear, thereby ensuring the fitting accuracy of the sealing pair during long-term use. This application also provides an air conditioning system, which includes the shut-off valve described in any of the above embodiments. This shut-off valve is connected to the piping of the air conditioning system to control the flow of fluid media such as refrigerant.

[0050] In summary, this application constructs a gate valve sealing structure that is reliable in sealing, has a long service life, and is easy to process and assemble by setting the generatrix width of the second conical surface 21 of the valve core 2 to be greater than the generatrix width of the first conical surface 11 of the valve seat 1, and by combining the optimized selection of the conical surface angle, the hardness difference design, and the guiding and limiting function of the stepped surface 12.

[0051] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this application.

[0052] The embodiments described above are merely examples of several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these modifications and improvements all fall within the protection scope of this application.

Claims

1. A shut-off valve, comprising a valve seat (1) and a valve core (2), the valve seat (1) having a valve cavity (10), the valve core (2) being movably disposed in the valve cavity (10), characterized in that, The valve cavity (10) has a first conical surface (11) on its inner wall and a second conical surface (21) on its valve core (2). The valve core (2) is configured to form a surface seal by the compression of the second conical surface (21) and the first conical surface (11) when under pressure. The width W2 of the second conical surface (21) along the generatrix direction is greater than the width W1 of the first conical surface (11) along the generatrix direction.

2. The shut-off valve according to claim 1, characterized in that, In the compression sealing state, the first conical surface (11) is within the coverage area of ​​the second conical surface (21), such that the width of the first conical surface (11) along the generatrix direction constitutes the width of the surface seal, and the first conical surface (11) and the second conical surface (21) are fitted together.

3. The shut-off valve according to claim 2, characterized in that, The width of the second cone (21) along the generatrix direction is 2 to 6 times the width of the first cone (11) along the generatrix direction.

4. The shut-off valve according to any one of claims 1 to 3, characterized in that, The minor diameter of the second conical surface (21) is smaller than the minor diameter of the first conical surface (11), and the major diameter of the second conical surface (21) is larger than the major diameter of the first conical surface (11).

5. The shut-off valve according to claim 4, characterized in that, The ratio of the arithmetic mean of the major and minor diameters of the first conical surface (11) to the arithmetic mean of the major and minor diameters of the second conical surface (21) is 0.5 to 2.

6. The shut-off valve according to any one of claims 1 to 3, characterized in that, The included angle α between the first conical surface (11) and the second conical surface (21) and the radial plane of the valve core (2) is 15°~75°.

7. The shut-off valve according to any one of claims 1 to 3, characterized in that, In the squeeze-sealed state, the large-diameter edge and the small-diameter edge of the second conical surface (21) are both in a suspended state that does not contact the valve seat (1).

8. The shut-off valve according to any one of claims 1 to 3, characterized in that, The hardness of the valve core (2) is higher than that of the valve seat (1).

9. The shut-off valve according to any one of claims 1 to 3, characterized in that, The inner wall of the valve cavity (10) has a stepped surface (12) above the first conical surface (11), and the inner diameter of the stepped surface (12) is larger than the major diameter of the second conical surface (21).

10. An air conditioning system, characterized in that, Includes the shut-off valve as described in any one of claims 1 to 9.

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