Solenoid valve, refrigeration apparatus, and automobile

Abstract

The application discloses an electromagnetic valve, a refrigeration device and a car, and relates to the technical field of refrigeration control, wherein the electromagnetic valve comprises a valve cover, a valve seat, a piston assembly and a spring, the valve cover is arranged on the valve seat to form a valve cavity together with the valve seat, an input channel and an output channel which are both communicated with the valve cavity are further arranged on the valve seat, the output channel is communicated with the valve cavity through a valve port, a ring-shaped mounting groove is concavely arranged on the periphery of the valve seat corresponding to the valve port, and the side of the ring-shaped mounting groove facing the input channel is communicated with the input channel; the piston assembly is used for opening or closing the valve port; the spring is arranged between the valve seat and the piston assembly, one end of the spring is mounted in the ring-shaped mounting groove, and the other end of the spring is abutted with the piston assembly; the inner wall of the ring-shaped mounting groove is concavely provided with a pressure relief groove, the pressure relief groove provides an additional flow path for high-pressure refrigerant, so that the lateral pressure impacting the ring-shaped mounting groove is dispersed to the groove and guided to other areas instead of directly acting on the spring, thereby significantly reducing the risk of spring deformation caused by impact.

Description

Technical Field

[0001] This invention relates to the field of refrigeration control technology, and particularly to a solenoid valve, refrigeration equipment, and automobile. Background Technology

[0002] In refrigeration system piping design, solenoid valves are often configured to control the flow and cut-off of media within the pipeline. Especially under certain application conditions, solenoid valves are required to open stably and reliably even at zero pressure differential. Therefore, a piston spring is typically installed at the lower end of the piston assembly to assist the valve opening process.

[0003] However, in actual operation, it was found that when the valve is switched on or off, the refrigerant flows in from the input channel, impacting the piston assembly inside the solenoid valve, particularly the spring responsible for resetting the piston assembly. This lateral refrigerant pressure not only impacts the spring but can also cause it to deform. Once the spring deforms, it directly affects the switching performance of the solenoid valve and may cause internal leakage. These problems reduce the overall efficiency and reliability of the equipment, therefore, the existing design needs to be improved to overcome these defects and ensure that the solenoid valve operates stably and reliably under various operating conditions. Summary of the Invention

[0004] The main objective of this invention is to propose a solenoid valve, refrigeration equipment, and automobile, aiming to solve the problem that the pressure of the refrigerant medium during the operation of existing solenoid valves can easily impact the spring, causing internal leakage.

[0005] To achieve the above objectives, the solenoid valve proposed in this invention includes:

[0006] A valve seat and a valve cover, wherein the valve cover is disposed on the valve seat to form a valve cavity with the valve seat, and the valve seat is also provided with an input channel and an output channel that are both connected to the valve cavity. The output channel is connected to the valve cavity through a valve port. The valve seat is provided with an annular mounting groove on the periphery corresponding to the valve port. The side of the annular mounting groove facing the input channel is connected to the input channel.

[0007] A piston assembly is movably disposed within the valve chamber in directions approaching and away from the valve port to open or close the valve port; and,

[0008] A spring is disposed between the valve seat and the piston assembly, with one end of the spring installed in the annular mounting groove and the other end abutting against the piston assembly;

[0009] The inner wall of the annular mounting groove is recessed with a pressure relief groove.

[0010] In one embodiment, the pressure relief groove is disposed at the bottom of the annular mounting groove and extends circumferentially along the valve port.

[0011] In one embodiment, the pressure relief groove is configured to communicate with the input channel on the side facing the output channel.

[0012] In one embodiment, the valve port is positioned beyond the bottom of the pressure relief groove.

[0013] In one embodiment, the centerline of the input channel extends beyond the bottom of the pressure relief groove.

[0014] In one embodiment, the pressure relief groove is disposed on one side of the bottom of the annular mounting groove located at the inner periphery, so as to form an annular support surface located on the periphery of the pressure relief groove at the bottom of the annular mounting groove, the annular support surface being used to support the spring.

[0015] In one embodiment, the annular support surface has a ring width of a, the spring has a wire diameter of b, and the pressure relief groove has a ring width of c, wherein b < a ≤ c.

[0016] In one implementation, b < a < 2b.

[0017] In one embodiment, the spring includes a tower spring, the diameter of which gradually increases from top to bottom.

[0018] In one embodiment, the valve seat has an annular stepped portion at one end near the valve cover;

[0019] The valve cover includes a cover body and an annular abutment portion. One end of the cover body extends into the cavity of the valve seat. The annular abutment portion protrudes outward from the side wall of the cover body and extends along the circumference of the cover body. The annular abutment portion is supported on the annular step portion.

[0020] In one embodiment, a threaded connection structure is provided between the outer wall of the valve cover and the cavity wall of the valve seat.

[0021] In one embodiment, the solenoid valve further includes a sealing ring disposed between the outer wall of the valve cover and the cavity wall of the valve seat, and located on the side of the threaded connection structure closer to the valve cover.

[0022] The present invention also proposes a refrigeration device, the refrigeration device including a solenoid valve, the solenoid valve comprising:

[0023] A valve seat and a valve cover, wherein the valve cover is disposed on the valve seat to form a valve cavity with the valve seat, and the valve seat is also provided with an input channel and an output channel that are both connected to the valve cavity. The output channel is connected to the valve cavity through a valve port. The valve seat is provided with an annular mounting groove on the periphery corresponding to the valve port. The side of the annular mounting groove facing the input channel is connected to the input channel.

[0024] A piston assembly is movably disposed within the valve chamber in directions approaching and away from the valve port to open or close the valve port; and,

[0025] A spring is disposed between the valve seat and the piston assembly, with one end of the spring installed in the annular mounting groove and the other end abutting against the piston assembly;

[0026] The inner wall of the annular mounting groove is recessed with a pressure relief groove.

[0027] The present invention also proposes a vehicle, the vehicle including a refrigeration device, the refrigeration device including a solenoid valve, the solenoid valve comprising:

[0028] A valve seat and a valve cover, wherein the valve cover is disposed on the valve seat to form a valve cavity with the valve seat, and the valve seat is also provided with an input channel and an output channel that are both connected to the valve cavity. The output channel is connected to the valve cavity through a valve port. The valve seat is provided with an annular mounting groove on the periphery corresponding to the valve port. The side of the annular mounting groove facing the input channel is connected to the input channel.

[0029] A piston assembly is movably disposed within the valve chamber in directions approaching and away from the valve port to open or close the valve port; and,

[0030] A spring is disposed between the valve seat and the piston assembly, with one end of the spring installed in the annular mounting groove and the other end abutting against the piston assembly;

[0031] The inner wall of the annular mounting groove is recessed with a pressure relief groove.

[0032] In the technical solution of this invention, when the refrigerant flows into the valve cavity from the input channel, it first flows through the annular mounting groove. When the refrigerant enters the annular mounting groove from the input channel, some of the high-pressure refrigerant would originally directly impact the spring in the mounting groove, generating lateral pressure. By recessing a pressure relief groove on the inner wall of the annular mounting groove, the pressure relief groove can act as a diversion channel, providing the refrigerant with an additional pressure relief path. This allows the impact force to be dispersed to the outlet or lateral channel of the pressure relief groove, enabling the high-pressure refrigerant to be quickly discharged or dispersed along the pressure relief groove, rather than acting entirely on the spring. This effectively reduces the risk of spring deformation caused by lateral pressure impact and avoids fatigue or failure of the spring due to long-term uneven stress. Attached Figure Description

[0033] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0034] Figure 1 and Figure 2 A cross-sectional schematic diagram of an embodiment of the solenoid valve provided by the present invention;

[0035] Figure 3 and Figure 4 for Figure 1 A cross-sectional view of the valve seat;

[0036] Figure 5 for Figure 1 A cross-sectional view of the middle valve cover.

[0037] Explanation of icon numbers:

[0038] 100. Solenoid valve; 1. Valve seat; 1a. Input channel; 1b. Output channel; b1. Valve port; c. Annular mounting groove; 1d. Pressure relief groove; 11. Annular support surface; 12. Annular stepped part; 2. Valve cover; 21. Cover body; 22. Annular abutment part; 3. Piston assembly; 4. Spring; 5. Threaded connection structure; 6. Sealing ring.

[0039] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0040] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0041] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indications will also change accordingly.

[0042] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0043] When the solenoid valve performs its on / off action, refrigerant flows in from the input channel, impacting the piston assembly inside the valve, particularly the spring responsible for resetting the piston. This lateral refrigerant pressure not only impacts the spring but can also cause it to deform. Once the spring deforms, it directly affects the solenoid valve's on / off performance and may cause internal leaks. These problems reduce the overall efficiency and reliability of the equipment.

[0044] This invention proposes a solenoid valve 100, which aims to solve the problem that the pressure of the cold medium easily impacts the spring during the operation of existing solenoid valves, causing internal leakage.

[0045] Please see Figure 1 In one embodiment of the present invention, the solenoid valve 100 includes a valve cover 2, a valve seat 1, a piston assembly 3, and a spring 4. The valve cover 2 covers the valve seat 1 to form a valve cavity. The valve seat 1 is also provided with an input channel 1a and an output channel 1b that are both connected to the valve cavity. The output channel 1b is connected to the valve cavity through a valve port b1. The valve seat 1 is provided with an annular mounting groove 1c on the periphery of the valve port b1. The side of the annular mounting groove 1c facing the input channel 1a is connected to the input channel 1a. The piston assembly 3 is movably disposed in the valve cavity in the direction close to and away from the valve port b1 to open or close the valve port b1. The spring 4 is disposed between the valve seat 1 and the piston assembly 3. One end of the spring 4 is installed in the annular mounting groove 1c, and the other end abuts against the piston assembly 3. The inner wall of the annular mounting groove 1c is provided with a pressure relief groove 1d.

[0046] It is understood that the valve seat 1 and the valve cover 2 form a sealed valve cavity by covering each other. The valve seat 1 is provided with an input channel 1a and an output channel 1b, both of which are connected to the valve cavity. The output channel 1b is used to control the flow of the medium. The valve seat 1 is provided with an annular mounting groove 1c around the valve port b1. The side of the annular mounting groove 1c facing the input channel 1a is connected to the input channel 1a, forming a path for the refrigerant to enter the mounting groove from the input channel 1a.

[0047] The piston assembly 3 is located inside the valve chamber and can move towards or away from the valve port b1 to open or close the valve port b1. The spring 4 is disposed between the valve seat 1 and the piston assembly 3, with one end fixed in the annular mounting groove 1c and the other end in contact with the piston assembly 3 to provide a restoring force.

[0048] When refrigerant enters the annular mounting groove 1c from the inlet channel 1a, some of the high-pressure refrigerant would originally directly impact the spring 4 inside the mounting groove, generating lateral pressure. By recessing a pressure relief groove 1d on the inner wall of the annular mounting groove 1c, the pressure relief groove 1d can act as a diversion channel, providing an additional pressure relief path for the refrigerant. This allows the impact force to be dispersed to the outlet or lateral channel of the pressure relief groove 1d, enabling the high-pressure refrigerant to be quickly discharged or dispersed along the pressure relief groove 1d, rather than acting entirely on the spring 4.

[0049] It should be noted that the shape of the pressure relief groove 1d can be a straight groove, a spiral groove, or a mesh groove. For example, a straight groove extending axially or circumferentially along the annular mounting groove 1c can directly guide the refrigerant; a spiral groove consumes kinetic energy by extending the refrigerant flow path; and a mesh groove disperses pressure through multiple paths, so that the refrigerant impacting the annular mounting groove 1c is evenly distributed, reducing the concentrated impact force on the spring 4.

[0050] The pressure relief groove 1d can be located on the bottom wall or side wall of the annular mounting groove 1c: the bottom wall pressure relief groove 1d directly guides the refrigerant to flow in other directions, avoiding the refrigerant from impacting the bottom of the spring 4; the side wall pressure relief groove 1d guides the refrigerant impacted laterally along the groove to other areas of the valve seat 1, weakening the pressure on the side wall of the spring 4 and ensuring that the refrigerant pressure is fully dispersed.

[0051] The size and distribution of the pressure relief groove 1d are designed according to the refrigerant flow rate and impact intensity, and the width is matched with the refrigerant flow rate. Under high impact conditions, the number of grooves or the distribution density can be increased. For example, multiple pressure relief grooves 1d can be evenly distributed along the annular installation groove 1c to improve the pressure dispersion effect by increasing the pressure relief area.

[0052] Through the above design, the pressure relief groove 1d provides an additional flow path for the high-pressure refrigerant, so that the lateral pressure impacting the annular mounting groove 1c is dispersed to the channel and guided to other areas, rather than acting directly on the spring 4, thereby significantly reducing the risk of the spring 4 being deformed by impact and improving the switching stability and sealing performance of the solenoid valve 100.

[0053] Specifically, please refer to Figure 2 and Figure 3 In some embodiments, the pressure relief groove 1d is disposed at the bottom of the annular mounting groove 1c and extends circumferentially along the valve port b1.

[0054] The pressure relief groove 1d is located directly at the bottom of the annular mounting groove 1c, and its extension direction is consistent with the circumferential direction of the valve port b1, forming an annular or continuous flow path.

[0055] It should be noted that by placing the pressure relief groove 1d at the bottom of the annular mounting groove 1c, the pressure relief groove 1d can change the impact direction of the refrigerant from a "top pressure" perpendicular to the spring 4 to a lateral flow along the bottom of the groove, significantly reducing the vertical pressure on the bottom of the spring 4 and reducing the risk of deformation of the spring 4 due to direct impact. In addition, the pressure relief groove 1d extends circumferentially along the valve port b1, so that the refrigerant pressure is evenly distributed along the annular path, avoiding high pressure in local areas due to refrigerant accumulation and ensuring that the spring 4 is subjected to balanced force.

[0056] By placing the pressure relief groove 1d at the bottom of the annular mounting groove 1c, when the refrigerant impacts the annular mounting groove 1c from the input channel 1a, the lateral pressure that originally acted vertically on the bottom of the spring 4 is directly guided to the pressure relief groove 1d at the bottom of the groove. The pressure relief groove 1d, which extends circumferentially, disperses the refrigerant to other areas of the valve seat 1 (such as the valve cavity or external channel), avoiding the impact force from being concentrated on the bottom of the spring 4. This optimizes the refrigerant flow path and reduces the direct impact on the spring 4, thereby improving the switching performance and sealing reliability of the solenoid valve 100.

[0057] For further information, please refer to [link / reference]. Figure 3 In some embodiments, the pressure relief groove 1d is connected to the input channel 1a on the side facing the output channel 1b.

[0058] The pressure relief groove 1d is located at the bottom of the annular mounting groove 1c and extends circumferentially along the valve port b1. The side of the pressure relief groove 1d facing the output channel 1b is directly connected to the input channel 1a. This allows some of the refrigerant to flow directly into the pressure relief groove 1d through the connection between the pressure relief groove 1d and the input channel 1a when it enters from the input channel 1a, instead of having to flow through the annular mounting groove 1c first. Therefore, the refrigerant is dispersed before reaching the bottom of the spring 4, preventing high-pressure impacts caused by refrigerant accumulation in the annular mounting groove 1c.

[0059] By directly connecting the pressure relief groove 1d to the input channel 1a, the flow path of the refrigerant is shortened, and its impact energy is diverted to the pressure relief groove 1d before entering the annular mounting groove 1c. This further reduces the lateral pressure of the refrigerant on the bottom of the spring 4, thereby effectively suppressing the risk of deformation of the spring 4 due to lateral pressure and improving the stability and sealing of the solenoid valve 100 under high pressure or frequent opening and closing conditions.

[0060] Furthermore, to better guide the flow of the refrigerant towards the pressure relief tank 1d for pressure relief, please refer to [link to relevant documentation]. Figure 3 In this embodiment, the valve port b1 is positioned beyond the bottom of the pressure relief groove 1d.

[0061] Understandably, the valve port b1 is positioned higher than the bottom of the pressure relief groove 1d, meaning the bottom face of valve port b1 is above the bottom of pressure relief groove 1d. This means that when the refrigerant enters the valve chamber from the input channel 1a, it must first pass through the space below valve port b1, and then flow naturally towards the bottom area of ​​pressure relief groove 1d below due to gravity or flow inertia. Because of the height difference between valve port b1 and the bottom of pressure relief groove 1d, the refrigerant will be preferentially guided to the lower pressure relief groove 1d during flow, rather than directly impacting the bottom of spring 4 located in the annular mounting groove 1c.

[0062] By setting the valve port b1 above the bottom of the pressure relief groove 1d, the refrigerant pressure of the input channel 1a can be guided more efficiently to the pressure relief groove 1d below through the height difference, so that the refrigerant is dispersed by the pressure relief groove 1d before contacting the spring 4, thereby further reducing the direct lateral impact force of the refrigerant on the bottom of the spring 4.

[0063] For further information, please refer to [link / reference]. Figure 3 In this embodiment, the centerline of the input channel 1a extends beyond the bottom of the pressure relief groove 1d.

[0064] It is understandable that the centerline of the input channel 1a is positioned above the bottom of the pressure relief groove 1d, meaning the axis of the input channel 1a is above the bottom of the pressure relief groove 1d. After the refrigerant enters the valve chamber from the input channel 1a, it needs to flow downwards to the bottom area of ​​the pressure relief groove 1d. Due to the height difference between the centerline of the input channel 1a and the bottom of the pressure relief groove 1d, the refrigerant is preferentially guided to the lower pressure relief groove 1d under the influence of gravity or flow inertia, thus dispersing pressure in advance and preventing the refrigerant from directly impacting the bottom of the spring 4 within the annular mounting groove 1c.

[0065] By setting the centerline of the input channel 1a above the bottom of the pressure relief groove 1d, the high-pressure refrigerant is naturally guided to the pressure relief groove 1d below after entering the valve chamber due to the height difference. This allows the refrigerant to be dispersed by the pressure relief groove 1d before contacting the spring 4, thus optimizing the flow path of the refrigerant and further reducing the lateral impact force on the bottom of the spring 4.

[0066] Specifically, please refer to Figure 1 and Figure 3 In some embodiments, the pressure relief groove 1d is disposed on one side of the bottom of the annular mounting groove 1c located at the inner periphery, so as to form an annular support surface 11 located around the pressure relief groove 1d at the bottom of the annular mounting groove 1c, the annular support surface 11 being used to support the spring 4.

[0067] The pressure relief groove 1d is located on the inner periphery of the bottom of the annular mounting groove 1c, near the center of the valve port b1, thus forming a complete annular support surface 11 on the outer side of the bottom of the annular mounting groove 1c, away from the center of the valve port b1. One end of the spring 4 is directly supported on this annular support surface 11, while the sidewall of the annular mounting groove 1c limits the radial position of the spring 4. This ensures that when the spring 4 is subjected to lateral impact, its bottom is always supported by the annular support surface 11, and the sidewall prevents the spring 4 from tilting inward or sliding into the pressure relief groove 1d, ensuring that the spring 4 is always in stable contact with the annular support surface 11.

[0068] By supporting the spring 4 on the annular support surface 11 surrounding the pressure relief groove 1d and using the side wall of the annular mounting groove 1c for radial restraint, the spring 4 can be effectively prevented from tilting or getting stuck due to partial embedment of its bottom into the pressure relief groove 1d caused by lateral impact force. At the same time, the annular support surface 11 provides uniform axial support force for the spring 4, reducing the risk of deformation of the spring 4 caused by unstable support.

[0069] Further, please refer to Figure 2 and Figure 4 In this embodiment, the annular support surface 11 has an annular width of a, the spring 4 has a wire diameter of b, and the pressure relief groove 1d has an annular width of c, wherein b < a ≤ c.

[0070] By making the ring width a of the annular support surface 11 greater than the wire diameter b of the spring 4, it is ensured that the bottom of the spring 4 has sufficient support width when it contacts the annular support surface 11, thus preventing the spring 4 from tilting or getting stuck due to local narrowness.

[0071] The annular support surface 11 is set to have a width a that is less than or equal to the annular width c of the pressure relief groove 1d, i.e., a does not exceed the annular width c of the pressure relief groove 1d. This allows the width c of the pressure relief groove 1d to be further expanded, thereby increasing the volume and flow area of ​​the pressure relief groove 1d, enhancing the refrigerant diversion efficiency, and reducing the risk of pressure concentration.

[0072] Furthermore, a larger c-value indicates a wider pressure relief groove 1d, which facilitates manufacturing, reduces the difficulty of precision machining, and ensures the stability and consistency of the pressure relief groove 1d structure. This design maximizes the pressure relief capacity of the pressure relief groove 1d while ensuring reliable support for the spring 4, thus balancing functionality and technological feasibility.

[0073] Preferably, b < a < 2b. By limiting the dimensional relationship between the ring width a of the annular support surface 11 and the wire diameter b of the spring 4, b < a < 2b (i.e., the ring width a is slightly larger than the wire diameter b of the spring 4), sufficient support width is provided for the spring 4 to avoid tilting or jamming. At the same time, a is limited to no more than twice the wire diameter of the spring 4, i.e., a < 2b, to prevent the support surface from being too wide, which would cause the width c of the pressure relief groove 1d to be greater than or equal to a, forcing an excessive increase that would affect the structural compactness. Setting a range of a and b between b < a < 2b ensures stable support for the spring 4 while reserving space for further widening of the pressure relief groove 1d, thereby improving pressure relief efficiency, while also considering ease of processing and reducing the need for precision machining.

[0074] Specifically, please refer to Figure 1 and Figure 2 In this embodiment, the spring 4 includes a tower-shaped spring 4, the diameter of which gradually increases from top to bottom.

[0075] Spring 4 is configured as a tower-shaped spring, with its diameter gradually increasing from top to bottom, meaning its top diameter is smaller and its bottom diameter is larger. When the tower-shaped spring 4 is compressed, it can provide a more uniform axial support force. The increased diameter at the bottom can form a larger contact area with the annular support surface 11 of the annular mounting groove 1c, enhancing the radial stability of the bottom of the spring 4 and avoiding tilting or displacement caused by lateral impacts. At the same time, the gradual diameter characteristic of the tower-shaped spring 4 can optimize the stiffness distribution of the spring 4, reduce stress concentration during valve opening and closing, extend the service life of the spring 4, and further reduce the risk of internal leakage caused by deformation of the spring 4.

[0076] Specifically, please refer to Figure 3 and Figure 5 In this embodiment, an annular stepped portion 12 is formed at one end of the valve seat 1 near the valve cover 2; the valve cover 2 includes a cover body 21 and an annular abutment portion 22, one end of the cover body 21 extends into the cavity of the valve seat 1, the annular abutment portion 22 protrudes outward from the side wall of the cover body 21 and extends along the circumference of the cover body 21, and the annular abutment portion 22 is supported on the annular stepped portion 12.

[0077] It should be noted that the valve cover 2 consists of a cover body 21 and an annular abutment portion 22. One end of the cover body 21 extends into the cavity of the valve seat 1, while the annular abutment portion 22 protrudes outward from the side wall of the cover body 21 and extends circumferentially, ultimately being directly supported on the annular stepped portion 12 of the valve seat 1. Thus, assembly can be completed simply by fitting the valve cover 2 and the valve seat 1 together, without the need for additional threads or fasteners. Through the cooperation between the annular stepped portion 12 of the valve seat 1 and the annular abutment portion 22 of the valve cover 2, it is only necessary to fit the valve cover 2 onto the valve seat 1 and press it tightly, enabling the valve body assembly to be quickly and accurately positioned and sealed, simplifying the assembly process, reducing assembly difficulty and time costs, while ensuring radial sealing and axial stability between the valve cover 2 and the valve seat 1.

[0078] Further, please refer to Figure 1 , Figure 3 and Figure 5 In this embodiment, a threaded connection structure 5 is provided between the outer wall of the valve cover 2 and the cavity wall of the valve seat 1.

[0079] Specifically, the inner wall of the valve seat 1 is machined with internal threads, and the outer wall of the valve cover 2 is correspondingly machined with external threads. The two are tightly connected through thread engagement. Thus, after the valve cover 2 is fitted onto the valve seat 1, rotating the valve cover 2 to make its threads engage with the internal threads of the valve seat 1 not only achieves axial compression sealing, but also prevents the valve cover 2 from loosening or shifting from the valve seat 1 through the radial limiting effect of the threads.

[0080] Through the threaded connection structure 5, the threaded contact surface can be used with a sealing gasket or achieve a double seal through the tight fit of the threads themselves, effectively blocking the refrigerant leakage path. While ensuring rapid assembly, it enhances the sealing reliability and connection strength under high-pressure conditions.

[0081] To further ensure the sealing between valve cover 2 and valve seat 1, please refer to [link / reference needed]. Figure 1 In this embodiment, the solenoid valve 100 further includes a sealing ring 6, which is disposed between the outer wall of the valve cover 2 and the cavity wall of the valve seat 1, and is located on the side of the threaded connection structure 5 near the valve cover 2.

[0082] The sealing ring 6 is fixed by being embedded in the annular groove of the valve cover 2 or the valve seat 1. When the valve cover 2 and the valve seat 1 are tightened by the threaded connection, the sealing ring 6 is compressed between the contact surfaces of the two to form a radial seal.

[0083] By setting a sealing ring 6 on the side of the threaded connection structure 5 near the valve cover 2, its elastic deformation can effectively seal the thread gap or small gaps on the connection surface. Especially under high-pressure refrigerant flow or vibration conditions, the sealing ring 6 is continuously compressed and evenly adheres to the contact surface, significantly improving the sealing reliability at the connection between the valve cover 2 and the valve seat 1. At the same time, the sealing ring 6 is set near the valve cover 2 end, which can avoid sealing failure due to excessive pre-tightening force during thread engagement, taking into account both ease of assembly and sealing strength, ensuring no refrigerant leakage and a stable connection structure.

[0084] The present invention also proposes a refrigeration device, which includes a heat exchanger and a solenoid valve 100. The specific structure of the solenoid valve 100 is as described in the above embodiments. Since the refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0085] The present invention also proposes a vehicle, which includes a body and a refrigeration device. The specific structure of the refrigeration device is as described in the above embodiments. Since the present vehicle adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0086] The above description is merely an exemplary embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention's specification and drawings under the technical concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A solenoid valve, characterized in that, include: A valve seat and a valve cover, wherein the valve cover is disposed on the valve seat to form a valve cavity with the valve seat, and the valve seat is also provided with an input channel and an output channel that are both connected to the valve cavity. The output channel is connected to the valve cavity through a valve port. The valve seat is provided with an annular mounting groove on the periphery corresponding to the valve port. The side of the annular mounting groove facing the input channel is connected to the input channel. A piston assembly is movably disposed within the valve chamber in directions approaching and away from the valve port to open or close the valve port; as well as, A spring is disposed between the valve seat and the piston assembly, with one end of the spring installed in the annular mounting groove and the other end abutting against the piston assembly; The inner wall of the annular mounting groove is recessed with a pressure relief groove.

2. The solenoid valve as described in claim 1, characterized in that, The pressure relief groove is located at the bottom of the annular mounting groove and extends circumferentially along the valve port.

3. The solenoid valve as described in claim 2, characterized in that, The pressure relief groove is connected to the input channel on the side facing the output channel.

4. The solenoid valve as described in claim 3, characterized in that, The valve port is positioned beyond the bottom of the pressure relief groove.

5. The solenoid valve as described in claim 3, characterized in that, The centerline of the input channel extends beyond the bottom of the pressure relief groove.

6. The solenoid valve as described in claim 2, characterized in that, The pressure relief groove is located on one side of the inner periphery of the bottom of the annular mounting groove, so as to form an annular support surface located on the periphery of the pressure relief groove at the bottom of the annular mounting groove, and the annular support surface is used to support the spring.

7. The solenoid valve as described in claim 6, characterized in that, The annular support surface has a ring width of a, the spring has a wire diameter of b, and the pressure relief groove has a ring width of c, where b < a ≤ c.

8. The solenoid valve as described in claim 7, characterized in that, b < a < 2b.

9. The solenoid valve as described in claim 1, characterized in that, The spring includes a tower-shaped spring, the diameter of which gradually increases from top to bottom.

10. The solenoid valve as claimed in claim 1, characterized in that, The valve seat has an annular stepped portion at one end near the valve cover; The valve cover includes a cover body and an annular abutment portion. One end of the cover body extends into the cavity of the valve seat. The annular abutment portion protrudes outward from the side wall of the cover body and extends along the circumference of the cover body. The annular abutment portion is supported on the annular step portion.

11. The solenoid valve as claimed in claim 1, characterized in that, A threaded connection structure is provided between the outer wall of the valve cover and the cavity wall of the valve seat.

12. The solenoid valve as described in claim 11, characterized in that, The solenoid valve also includes a sealing ring, which is disposed between the outer wall of the valve cover and the cavity wall of the valve seat, and is located on the side of the threaded connection structure closer to the valve cover.

13. A refrigeration device, characterized in that, Includes the solenoid valve as described in any one of claims 1 to 12.

14. A car, characterized in that, This includes the refrigeration equipment as described in claim 13.

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