An electromagnetic valve

Abstract

This application relates to the field of valve device technology and discloses a solenoid valve. The solenoid valve includes a valve seat core component and a moving iron core component; the solenoid valve has a cavity, and the moving iron core component is at least partially located in the cavity; the valve seat core component includes a valve seat core, which includes a valve port portion; the moving iron core component includes a moving iron core body and a sealing element; the lower part of the moving iron core body has a boss portion; the sealing element has a groove portion with a recessed hole communicating with the cavity; the sealing element is fitted onto the boss portion; the sealing element has a second sealing surface that can abut against or move away from the valve port portion; the sealing element has a pressure relief hole; one side of the pressure relief hole forms a guide end, and the other side forms a discharge end; the guide end extends to the recessed hole, and the discharge end extends to the outer surface of the sealing element; the pressure relief hole is used to introduce fluid from the guide end and discharge it through the discharge end when fluid flows into the interior of the recessed hole. In application, when the solenoid valve is fully open, it can relatively maintain the opening degree of the valve port.

Description

Technical Field

[0001] This application relates to the field of valve device technology, and in particular to a solenoid valve. Background Technology

[0002] A solenoid valve may include a stationary iron core component, a valve seat component, and a valve seat core, with a moving iron core component inside the valve body. The valve seat core has a valve port portion with a valve orifice. The moving iron core component includes a moving core body and a piston component, which can abut against or move away from the valve port portion. The moving core body has a flange mating portion, and the piston component is fitted onto the outer periphery of the flange mating portion. Fluid easily flows into the mating groove of the piston component through the position between the flange mating portion of the moving core body and the piston component. The lower end face of the piston component is easily bulged under pressure, causing the valve opening to decrease to less than the theoretical design opening when fully open.

[0003] Therefore, how to provide a solenoid valve to solve or alleviate the above-mentioned defects remains a technical problem that urgently needs to be solved by those skilled in the art. Summary of the Invention

[0004] The purpose of this application is to provide a new type of solenoid valve that, when fully open, can relatively guarantee the opening degree of the valve port.

[0005] To solve the above-mentioned technical problems, this application provides a solenoid valve, including a valve seat core component and a moving iron core component; the solenoid valve has a cavity, and the moving iron core component is at least partially located in the cavity; the valve seat core component includes a valve seat core, the valve seat core includes a valve port portion, the moving iron core component includes a moving iron core body and a sealing element, the lower part of the moving iron core body has a boss portion, the sealing element has a groove portion, the groove portion has a concave hole, the concave hole communicates with the cavity, the sealing element is fitted onto the boss portion, the sealing element has a second sealing surface, the second sealing surface can abut against or move away from the valve port portion, and the sealing element has a pressure relief hole;

[0006] One side of the pressure relief hole forms a drainage end, and the other side forms a drainage end. The drainage end extends through the concave hole, and the drainage end extends through the outer surface of the seal. In the fully open state, the seal is away from the valve port, and the cavity, the concave hole, and the pressure relief hole are connected.

[0007] This invention provides an electromagnetic valve that features a pressure relief hole on a sealing element. One side of the pressure relief hole extends into the recessed hole of the groove, while the other side extends into the outer surface of the sealing element. In the fully open state, the second sealing surface is away from the valve port, with one side opening connected to the recessed hole and the other side opening connected to the cavity. Even if fluid enters the recessed hole from the cavity, pressure can be relieved through the pressure relief hole, significantly reducing the risk of the sealing surface of the sealing element bulging downwards due to the internal pressure of the recessed hole. In the fully open state, the valve port opening can be relatively guaranteed. Attached Figure Description

[0008] Figure 1 This is a partial cross-sectional view of the solenoid valve provided in the embodiments of this application;

[0009] Figure 2 This is a full sectional view of the solenoid valve provided in the embodiments of this application;

[0010] Figure 3 for Figure 2 A schematic diagram of the valve seat core component of a solenoid valve;

[0011] Figure 4 for Figure 3 A schematic diagram of the valve seat core of the valve seat core component;

[0012] Figure 5 for Figure 3 A schematic diagram of the structure of the valve seat core sleeve of the valve seat core component;

[0013] Figure 6 for Figure 2 A schematic diagram of the moving iron core component of the solenoid valve;

[0014] Figure 7 for Figure 6 A schematic diagram of the structure of the moving iron core body of the central moving iron core component;

[0015] Figure 8 for Figure 6 A schematic diagram of the sealing components of the moving iron core assembly;

[0016] Figure 9 for Figure 2 A schematic diagram of the instantaneous shape of the boss part of the moving iron core body and the concave hole of the sealing element when the coil is energized, with a small interference fit.

[0017] Figure 10 for Figure 2 A schematic diagram of the fluid path between the boss portion of the moving iron core body and the concave hole of the sealing element after the valve port is opened in a solenoid valve.

[0018] The reference numerals in the above figures are explained as follows:

[0019] 1-Stationary iron core components;

[0020] 2-Valve seat assembly;

[0021] 3-Valve seat core component, 31-Valve seat core, 311-First channel, 312-Valve port, 313-First sealing surface, 32-Valve seat core sleeve, 321-Second channel;

[0022] 4-Returning spring;

[0023] 5-Moving iron core component, 51-Moving iron core body, 511-Boss portion, 512-First lower end face, 513-First outer side face, 514-First stepped surface, 515-Second outer side face, 516-Second lower end face, 52-Seal, 521-Concave hole, 522-Second sealing surface, 523-First upper end face, 524-First inner side face, 525-Second stepped surface, 526-Second inner side face, 527-Bottom surface, 528-Pressure relief hole; a1-Protruding rod, a2-Boss, b1-Inner hole, b2-Stepped hole, c1-Groove portion, c2-Sealing portion, e1-Draining end, e2-Draining end;

[0024] 6-Cavity. Detailed Implementation

[0025] To enable those skilled in the art to better understand the present application, the present application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0026] In the description of this application, it should be noted that the terms "up" and "down" used in this application refer to directions that are... Figure 1 From this perspective, the vertical direction is also the axis of the solenoid valve.

[0027] The terms "first" and "second" used in this application are merely for the convenience of describing two or more structures or components that are identical or similar in structure and / or function, and do not imply any special limitation on their order and / or importance.

[0028] Please refer to Figures 1 to 8 , Figure 1 This is a partial cross-sectional view of the solenoid valve provided in the embodiments of this application. Figure 2 This is a full sectional view of the solenoid valve provided in the embodiments of this application. Figure 3 for Figure 2 A schematic diagram of the valve seat core component of a solenoid valve. Figure 4 for Figure 3 A schematic diagram of the valve seat core of the valve seat core component. Figure 5 for Figure 3 A schematic diagram of the valve seat core sleeve of the valve seat core component. Figure 6 for Figure 2 A schematic diagram of the moving iron core component of the solenoid valve. Figure 7 for Figure 6 A schematic diagram of the moving iron core body of the moving iron core component. Figure 8 for Figure 6 A schematic diagram of the sealing element of the moving iron core component.

[0029] In the embodiments provided in this application, such as Figure 1 and Figure 2As shown, the solenoid valve includes a valve seat core component 3 and a moving iron core component 5. The solenoid valve has a cavity 6, and the moving iron core component 5 is at least partially located in the cavity 6. The valve seat core component 3 includes a valve seat core 31, as shown... Figure 3 and Figure 4 As shown, the valve seat core 31 includes a valve port portion 312. (As indicated...) Figure 6 As shown, the moving iron core component 5 includes a moving iron core body 51 and a sealing member 52. The lower part of the moving iron core body 51 is provided with a boss portion 511, and the sealing member 52 has a groove portion c1. The groove portion c1 is provided with a recessed hole 521, which communicates with the cavity 6. The sealing member 52 is fitted onto the boss portion 511. Figure 8 As shown, the seal 52 has a second sealing surface 522, which can abut against or move away from the valve port 312. Figure 6 and Figure 8 As shown, the sealing element 52 has a pressure relief hole 528. One side of the pressure relief hole 528 is open to form a flow-in end e1 and the other side is open to form a flow-out end e2. The flow-in end e1 is the end where the fluid flows in, and the flow-out end e2 is the end where the fluid flows out. The flow-in end e1 extends to the recess 521, and the flow-out end e2 extends to the outer surface of the sealing element 52. In the fully open state, the sealing element 52 is away from the valve port 312, and the cavity 6, the recess 521, and the pressure relief hole 528 are connected.

[0030] With this configuration, in the fully open state, one side of the pressure relief hole 528 communicates with the recessed hole 521, and the other side communicates with the cavity 6. Even if fluid flows from the cavity 6 into the recessed hole 521 through the position between the upper end face of the seal 52 and the lower end face of the moving iron core body 51, it can be depressurized through the pressure relief hole 528. Specifically, the flow-inlet e1 can introduce fluid into the pressure relief hole 528 and flow out of the seal 52 through the flow-outlet e2 and into the cavity 6, so that the fluid pressure in the gap between the boss 511 and the recessed hole 521 is quickly and to a large extent balanced. Thus, the second sealing surface 522 on the seal 52 remains relatively flat. After the valve is fully open, the vertical distance between the sealing surface of the seal 52 and the sealing surface of the valve seat core 31 is relatively consistent with the design distance, which can relatively ensure the consistency between the actual opening degree of the solenoid valve and the theoretical design opening degree, thereby relatively ensuring the matching of the actual value of the fully open flow rate of the solenoid valve with the design value.

[0031] For actual setup, please refer to... Figure 1 and Figure 2 The solenoid valve may further include a stationary iron core component 1, which can be axially connected to the valve seat core component 3. As can be seen from the above, the solenoid valve provided in this embodiment solves the technical problem of the actual opening degree of the solenoid valve being too small due to fluid flowing into the concave hole 521. Please refer to... Figures 1 to 2Without a pressure relief hole 528, it is often necessary to increase the actual opening between the moving iron core component 5 and the stationary iron core component 1 to compensate for the reduced opening caused by fluid flowing into the concave hole 521. However, increasing the opening between the moving iron core component 5 and the stationary iron core component 1 often requires increasing the opening current of the solenoid valve. For example, actual measurements show that fluid flowing into the concave hole 521 may cause the second sealing surface 522 to bulge downwards by more than 0.1 mm. When the opening is increased by 0.1 mm, the opening current may need to increase by 0.3 A. This improvement method is prone to compromise and weakens the opening performance of the solenoid valve. However, the solenoid valve provided in this embodiment only needs to have a pressure relief hole 528 on the sealing component 52, without increasing the opening current. This allows the opening performance of the solenoid valve to be maintained while ensuring the opening of the solenoid valve.

[0032] In actual installation, the stationary iron core component 1 and the valve seat core component 3 are connected axially. The specific connection structure between them is not limited. For example, please refer to... Figure 1 and Figure 2 The solenoid valve may also include a valve seat component 2, and the stationary iron core component 1 and the valve seat core component 3 can be connected through the valve seat component 2.

[0033] The specific structure of the valve seat core component 3 is not limited in this application embodiment, as long as it has a valve seat core 31. For example, please refer to [reference needed]. Figure 3 and Figure 5 The valve seat core component 3 may also include a valve seat core sleeve 32. The upper end of the valve seat core 31 is inserted into the valve seat core sleeve 32 axially and fixed. The upper end of the valve seat core sleeve 32 is inserted into the valve seat component 2 axially and fixed. The valve seat core 31 is provided with a first channel 311 that runs through it axially. The upper end of the first channel 311 forms the valve port portion 312. The upper end surface of the valve seat core 31 forms a first sealing surface 313. The valve seat core sleeve 32 is provided with a second channel 321. The interior of the valve seat component 2 and the interior of the valve seat core sleeve 32 form the cavity 6.

[0034] Please refer to the embodiments provided in this application. Figure 7 In the moving iron core component 5, the moving iron core body 51 and the boss portion 511 are integrally formed, resulting in a stable structure, ease of manufacturing, and low cost. Obviously, the moving iron core body 51 and the boss portion 511 can also be formed separately, and this application does not impose any restrictions on this.

[0035] Please combine Figures 1-8It is understood that a return spring 4 can be provided between the stationary iron core component 1 and the moving iron core component 5. The solenoid valve provided in this application embodiment also includes a coil (not shown in the figure), which realizes the opening and closing of the valve port 312 by energizing and de-energizing the coil. Specifically, when the coil is energized, it forms a magnetic field around the valve body. Under the action of electromagnetic force, the moving iron core body 51 overcomes the force of the return spring 4 and moves upward, thereby driving the sealing element 52 to move upward. The second sealing surface 522 of the sealing element 52 moves away from the first sealing surface 313 of the valve seat core 31, and the valve port 312 opens. At this time, fluid flows into the cavity 6 from the second channel 321 and flows out from the first channel 311. This flow direction is defined as positive. When the coil is de-energized, the magnetic field around the valve body disappears, the electromagnetic force disappears, and the moving iron core body 51 moves downward under the restoring force of the return spring 4, thereby driving the sealing element 52 to move downward to approach the valve seat core 31 until the second sealing surface 522 of the sealing element 52 is in contact with the first sealing surface 313 of the valve seat core 31, and the valve port 312 closes.

[0036] In actual installation, the sealing element 52 can be made of an elastic material to achieve a good sealing effect. The elastic material is a type of material with the ability to recover its deformation. It can undergo elastic deformation under the action of external force, but can return to its original shape after the external force is removed. Specifically, it can be a rubber material, a spring steel material, or a thermoplastic elastomer material. This application does not limit this.

[0037] As an optional solution, the seal 52 is made of rubber. With this configuration, the seal 52 not only has good elasticity and deformation recovery ability, and excellent sealing performance, but also can tightly fit with the first sealing surface 313 when it is pressed against and plugged at the valve port 312 to prevent fluid leakage. In addition, it has good wear resistance, oxidation resistance and corrosion resistance, and can be used for a long time in harsh environments, thereby improving the reliability and applicability of the solenoid valve.

[0038] In the embodiments provided in this application, the seal 52 is fitted onto the boss portion 511, that is, the boss portion 511 is confined within the recess 521. Here, the confinement means that the relative axial movement of the boss portion 511 and the seal 52 is constrained. Specifically, when the boss portion 511 moves upward, it can drive the seal 52 to move upward. When the boss portion 511 moves downward, the seal 52 will not detach from the boss portion 511. In this way, the process of opening and closing the valve is more stable.

[0039] In actual installation, the specific limiting structure between the boss 511 and the recess 521 is not limited, as long as it can restrict the axial separation of the boss 511 and the seal 52.

[0040] As an optional solution, please refer to Figures 6-8Both the boss portion 511 and the recess 521 are constructed to have a T-shaped axial cross section. The boss portion 511 has a first stepped surface 514, and the recess 521 has a second stepped surface 525. The first stepped surface 514 and the second stepped surface 525 interact to limit the boss portion 511 to the recess 521.

[0041] The T-shaped surface is a stepped shape where the profile dimension at one end is smaller than that at the other end. Specifically, the boss portion 511 includes a protruding rod a1 and a boss a2 along the axial direction from top to bottom, and the concave hole 521 includes an inner hole b1 and a stepped hole b2 along the axial direction from top to bottom. Taking the boss portion 511 as an example, the protruding rod a1 and the boss a2 can both be cylindrical or prism in shape.

[0042] Please refer to Figure 7 and Figure 8 Understand that both the protruding rod a1 and the boss a2 can be cylindrical, the outer diameter of the protruding rod a1 is smaller than the outer diameter of the boss a2, the inner hole b1 is a circular hole that matches the shape of the protruding rod a1, the stepped hole b2 is a circular hole that matches the shape of the boss a2, and the inner diameter of the inner hole b1 is smaller than the inner diameter of the stepped hole b2. In this embodiment, the portion of the seal 52 with a recessed hole 521 along the axial direction from top to bottom is the groove portion c1, and the remaining portion is the sealing portion c2. The upper end face of the seal 52 is the first upper end face 523, and the lower end face of the moving iron core body 51 is the first lower end face 512. The outer side of the protrusion a1 is the first outer side face 513, the upper end face of the protrusion a2 is the aforementioned first step surface 514, the outer side of the protrusion a2 is the second outer side face 515, and the lower end face of the protrusion a2 is the second lower end face 516. The inner side of the inner hole b1 is the first inner side face 524, the top surface of the stepped hole b2 is the aforementioned second step surface 525, the inner side of the stepped hole b2 is the second inner side face 526, and the stepped hole b2 has a bottom surface 527.

[0043] With this configuration, the first step surface 514 in the boss portion 511 and the second step surface 525 in the recess 521 interact to form a limiting structure, which allows the boss portion 511 to drive the seal 52 to move upward and ensures that the seal 52 does not fall off during the downward movement of the boss portion 511. This restricts the axial separation of the boss portion 511 and the seal 52, making the connection structure between the boss portion 511 and the seal 52 more stable. Thus, the boss portion 511 can drive the seal 52 to move upward stably, and when moving downward, the boss portion 511 can press the seal 52 stably onto the valve seat core 31 to achieve a stable seal.

[0044] The above embodiments describe how the boss portion 511 and the recessed hole 521 form the aforementioned limiting structure through two stepped surfaces. In other embodiments of this application, the two can form a limiting structure through two surfaces of other structures. For example, the boss portion 511 and the recessed hole 521 can both be frustum-shaped or truncated pyramid-shaped, so that a limiting structure is formed through the outer surface of the boss portion 511 and the inner surface of the recessed hole 521. The specific principle is similar to the limiting structure formed by the two stepped surfaces described above, and will not be repeated here.

[0045] It is easy to understand that the location of the pressure relief hole 528 is not limited, as long as it can release the fluid flowing into the recess 521. For example, the drain end e1 of the pressure relief hole 528 can extend to the first inner side surface 524 or the second inner side surface 526 of the recess 521 to drain from the side, or it can extend to the bottom surface 527 of the recess 521 to drain from the bottom; the discharge end e2 of the pressure relief hole 528 can extend to the side of the seal 52 to release pressure laterally, or it can extend to the second sealing surface 522 of the seal 52 to release pressure downward.

[0046] Please refer to the embodiments provided in this application. Figure 8 Along the thickness direction of the seal 52, that is, the vertical direction, the flow-in end e1 extends to the bottom surface 527 of the recess 521, and the discharge end e2 extends to the second sealing surface 522. That is, the pressure relief hole 528 extends from the bottom surface 527 to the second sealing surface 522. In this way, the pressure relief hole 528 can draw fluid from the bottom of the recess 521 and discharge the fluid to the bottom of the seal 52. The flow-in point is located at the end of the fluid flow direction in the recess 521, and the discharge direction is consistent with the main flow direction of the fluid in the cavity 6. This can improve the pressure relief effect and improve the consistency between the actual opening degree and the theoretical opening degree of the solenoid valve.

[0047] In actual installation, the specific shape of the pressure relief hole 528 is not limited. As an optional solution, the pressure relief hole 528 is a round hole, which is easy to process and can make the fluid release process smoother, thus improving the pressure relief effect.

[0048] In the embodiments provided in this application, the pressure relief hole 528 and the recessed hole 521 are also coaxially arranged with the first channel 311, which can not only improve the pressure relief effect of using the pressure relief hole 528, but also reduce the impact of the opening of the pressure relief hole 528 on the sealing effect when the second sealing surface 522 on the seal 52 contacts the first sealing surface 313 on the valve seat core 31.

[0049] Please continue to refer to this. Figure 9 and Figure 10 , Figure 9 for Figure 2 A schematic diagram showing the instantaneous shape of the boss portion of the moving iron core body and the concave hole of the seal when the coil is energized, with a small interference fit. Figure 10 for Figure 2A schematic diagram of the fluid path after the boss portion of the moving iron core body and the concave hole of the sealing element in the solenoid valve are opened at the valve port. Figure 9 The dashed lines represent the instantaneous shape of the seal 52 after elastic deformation, and the arrows represent the fluid pressure on the corresponding end face. Figure 10 The dashed line with an arrow in the middle represents the fluid flow path.

[0050] In actual installation, the boss 511 and the recess 521 can be fitted with either a clearance fit or a tight fit, and this application does not impose any restrictions on this.

[0051] In one embodiment provided in this application, a first gap exists between the lower end face 512 of the moving iron core body 51 and the upper end face 523 of the seal 52. The protruding rod a1 in the boss portion 511 has a clearance fit with the side wall of the groove portion c1. The gap between the protruding rod a1 and the side wall is defined as a second gap. The first gap, the second gap, and the cavity 6 are connected. This configuration allows the boss portion 511, even with a T-shaped axial cross-section, to be smoothly assembled into the recessed hole 521, and also facilitates the disassembly of the boss portion 511. The clearance fit between the protruding rod a1 and the groove portion c1 allows for a certain clearance to be reserved, making the assembly and disassembly process more convenient and reducing manufacturing costs. The side wall of the groove c1 that is used to cooperate with the protrusion a1 corresponds to the first inner side surface 524 of the inner hole b1. It is easy to understand that in the boss 511, in addition to the protrusion a1 being able to cooperate with the side wall of the groove c1, the boss a2 can also be able to cooperate with the side wall of the groove c1.

[0052] In another embodiment provided in this application, there is a first gap between the lower end face of the moving iron core body 51 and the upper end face of the seal 52. The protruding rod a1 in the boss portion 511 is tightly fitted with the side wall of the groove portion c1, which means that there can be a small interference fit, which can provide good positioning accuracy, ensure good centering and coaxiality, and improve the stability of the connection between the boss portion 511 and the recessed hole 521.

[0053] Please combine Figure 2 and Figure 10 It is understood that after the fluid flows into the cavity 6, it may flow from the first gap to the area above the recess 521. Of course, if the first gap does not exist, the fluid may also permeate from the position between the first lower end face 512 and the first upper end face 523 to the area above the recess 521. The working principle of the solenoid valve provided in this application embodiment is explained below with the first gap present as an example:

[0054] When the second gap is present between the boss 511 and the recess 521: When the coil is energized and the solenoid valve opens, the fluid entering the cavity 6 may pass through the first gap and then the second gap into the recess 521. If the pressure relief hole 528 is not provided, the fluid entering the recess 521 will exert a downward force on the bottom surface 527 of the recess 521, causing the sealing part c2 in the seal 52 to elastically deform and bulge downwards. This causes the second sealing surface 522 on the seal 52 to bulge downwards, resulting in a vertical distance between the second sealing surface 522 and the first sealing surface 313 on the valve seat core 31 being less than the design distance after the valve is opened. This causes the actual opening degree of the solenoid valve to be less than the theoretical design opening degree, resulting in a mismatch between the actual flow rate and the design flow rate after the valve is fully open. Please refer to [reference needed]. Figure 10 In the embodiments provided in this application, a pressure relief hole 528 communicating with the recessed hole 521 is provided on the sealing member 52. After the fluid enters the interior of the recessed hole 521, it will continue to flow out of the sealing member 52 from the pressure relief hole 528. As a result, the second sealing surface 522 can remain relatively flat, which can relatively ensure the consistency between the actual opening degree of the solenoid valve and the theoretical design opening degree.

[0055] When there is a small interference fit between the boss 511 and the recess 521: Although there is no second gap between the contact surfaces of the boss 511 and the recess 521 when the coil is not energized, when the valve port 312 is closed, the second sealing surface 522 on the seal 52 and the first sealing surface 313 on the valve seat core 31 are in contact. When the fluid in the pipeline connected to the solenoid valve flows forward, the fluid flows into the cavity 6 from the second channel 321. Since the area of ​​the first upper end surface 523 of the seal 52 is larger than the area of ​​the exposed part of the second sealing surface 522 of the seal 52, the fluid pressure acting on the first upper end surface 523 is greater than the fluid pressure acting on the second sealing surface 522. The resultant force of the pressure on these two ends is downward. At the instant the coil is energized, the moving iron core body 51 begins to move upward. At this time, please refer to... Figure 9The pressure differential force acting on the seal 52 keeps it pressed against the valve seat core 31, meaning the second sealing surface 522 and the first sealing surface 313 have not yet separated. The boss portion 511 exerts an upward pulling force on the groove portion c1, causing the groove portion c1 to undergo elastic deformation. Consequently, the first upper end surface 523, the first inner side surface 524, and the second step surface 525 undergo elastic deformation. Specifically, the first inner side surface 524 expands radially outward, creating a second gap between it and the first outer side surface 513 of the protrusion a1 in the boss portion 511. This allows fluid to enter through the second gap from the first gap. If a pressure relief hole 528 is not provided in the recessed hole 521, the fluid entering the recessed hole 521 will cause the sealing part c2 in the seal 52 to elastically deform and bulge downwards, thus causing the second sealing surface 522 to bulge downwards. When the moving iron core body 51 continues to move upwards, driving the seal 52 away from the valve seat core 31, the aforementioned elastic deformation of the sealing part c2 has not yet recovered. This results in the vertical distance between the second sealing surface 522 and the first sealing surface 313 after the valve is opened being less than the design distance. Consequently, the actual opening degree of the solenoid valve is less than the theoretical design opening degree, and the actual flow rate after the valve is fully open does not match the design flow rate. In the embodiment provided in this application, a pressure relief hole 528 communicating with the recessed hole 521 is provided on the seal 52. After the fluid enters the interior of the recessed hole 521, it will continue to flow downwards from the seal 52 through the pressure relief hole 528, thus the second sealing surface 522 can remain relatively flat, which can relatively ensure the consistency between the actual opening degree of the solenoid valve and the theoretical design opening degree.

[0056] As can be seen, the solenoid valve provided in this application embodiment has a pressure relief hole 528 on the sealing element 52, so that whether the boss part 511 and the concave hole 521 are clearance-fitted or tight-fitted, the consistency between the actual opening degree and the theoretical design opening degree can be relatively guaranteed.

[0057] In actual setup, the dimensional relationship between the pressure relief hole 528, the recessed hole 521 and the first channel 311 is not restricted.

[0058] Please refer to the embodiments provided in this application. Figure 10 Let the inner diameter of the pressure relief hole 528 be d1, the maximum outer diameter of the boss 511 be d2 (that is, the outer diameter of the boss a2 be d2), and the inner diameter of the first channel 311 be d3. Let d1, d2, and d3 satisfy the following conditions:

[0059] d1 <d3<d2。

[0060] With such a setting, not only is there a first mating wall thickness of (d2 - d1) / 2 between the concave hole 521 and the convex boss portion 511, but when the second sealing surface 522 in the seal 52 contacts the first sealing surface 313 in the valve seat core 31, there is a second mating wall thickness of (d3 - d1) / 2 at the valve port portion 312. On the basis of ensuring the pressure relief effect of the pressure relief hole 528, it can ensure good sealing when the second sealing surface 522 in the seal 52 contacts the first sealing surface 313 in the valve seat core 31, so that the opening of the pressure relief hole 528 will not weaken the sealing performance of the solenoid valve.

[0061] It is not difficult to understand that the inner diameter size of the pressure relief hole 528 will affect the pressure relief effect of the pressure in the concave hole 521. The larger the inner diameter of the pressure relief hole 528, the better the pressure relief effect; and the sizes of the above two mating wall thicknesses will affect the sealing performance of the solenoid valve.

[0062] In some embodiments provided by the present application, 1mm < d3 ≤ 2.0mm, 0.6mm ≤ d1 ≤ 1.6mm. In this way, when d3 is a smaller value of 1 - 2mm, a reasonable second mating wall thickness can be formed, so as to further ensure that the opening of the pressure relief hole 528 will not weaken the sealing performance of the solenoid valve.

[0063] In some embodiments provided by the present application, 1mm < d3 ≤ 2.0mm, d2 ≥ 3d3 / 2. In this way, when d3 is a smaller value of 1 - 2mm, since d1 < d3 and d2 ≥ 3d3 / 2 can form a reasonable first mating wall thickness, it can further ensure that the opening of the pressure relief hole 528 will not weaken the sealing performance of the solenoid valve.

[0064] It can be understood that when 1mm < d3 ≤ 2.0mm, 0.6mm ≤ d1 ≤ 1.6mm and d2 ≥ 3d3 / 2 can also be satisfied simultaneously to ensure a more reasonable first mating wall thickness and second mating wall thickness, so as to further ensure that the opening of the pressure relief hole 528 will not weaken the sealing performance of the solenoid valve.

[0065] In some embodiments provided by the present application, d3 > 2.0mm, d1 > 1.6mm. In this way, when d3 is a larger value greater than 2mm, the pressure relief effect of the pressure relief hole 528 can be improved as much as possible, and since d1 < d3, the opening of the pressure relief hole 528 with a larger aperture will not weaken the sealing performance of the solenoid valve.

[0066] In some embodiments provided by the present application, d3 > 2.0mm, d2 ≥ 2d3. In this way, when d3 is a larger value greater than 2mm, since d1 < d3 and d2 ≥ 2d3 can form a larger first mating wall thickness, it can further ensure that the opening of the pressure relief hole 528 will not weaken the sealing performance of the solenoid valve.

[0067] It is understandable that when d3 > 2.0mm, d1 > 1.6mm and d2 ≥ 2d3 can also be satisfied simultaneously, so as to ensure the pressure relief effect of the pressure relief hole 528 while forming a reasonable first and second mating wall thickness, thereby further ensuring that the opening of the pressure relief hole 528 will not weaken the sealing performance of the solenoid valve.

[0068] As can be seen, in the embodiments provided in this application, the design of the relationship between the inner diameter of the pressure relief hole 528, the maximum outer diameter of the boss portion 511, and the inner diameter of the first channel 311 can ensure the pressure relief effect of the pressure relief hole 528, thereby relatively ensuring the matching of the actual value of the fully open flow rate after the solenoid valve is opened with the design value, without weakening the sealing performance of the solenoid valve.

[0069] This document uses specific examples to illustrate the principles and implementation methods of this application. The descriptions of the embodiments above are only for the purpose of helping to understand the apparatus and core ideas of this application. It should be noted that those skilled in the art can make several improvements and modifications to this application without departing from the principles of this application, and these improvements and modifications also fall within the protection scope of the claims of this application.

Claims

1. A solenoid valve, characterized in that, The system includes a valve seat core component (3) and a moving iron core component (5); the solenoid valve has a cavity (6), and the moving iron core component (5) is at least partially located in the cavity (6); the valve seat core component (3) includes a valve seat core (31), the valve seat core (31) includes a valve port (312), the moving iron core component (5) includes a moving iron core body (51) and a sealing element (52), the lower part of the moving iron core body (51) is provided with a boss (511), the sealing element (52) has a groove (c1), the groove (c1) is provided with a concave hole (521), the concave hole (521) communicates with the cavity (6), the sealing element (52) is fitted onto the boss (511), the sealing element (52) is provided with a second sealing surface (522), the second sealing surface (522) can abut against or move away from the valve port (312), and the sealing element (52) is provided with a pressure relief hole (528); The pressure relief hole (528) has an opening on one side to form a flow guide (e1) and an opening on the other side to form a flow drain (e2). The flow guide (e1) extends through the recess (521), and the flow drain (e2) extends through the outer surface of the seal (52). The flow guide (e1) can introduce fluid into the pressure relief hole (528) and flow out of the seal (52) through the flow drain (e2) and into the cavity (6). In the fully open state, the seal (52) is away from the valve port (312), and the cavity (6), the recess (521), and the pressure relief hole (528) are connected.

2. The solenoid valve according to claim 1, characterized in that, The lower end face of the moving iron core body (51) and the upper end face of the sealing element (52) have a first gap. The boss part (511) includes a protruding rod (a1), and the groove part (c1) is provided with a side wall. The protruding rod (a1) is fitted with the side wall with a clearance, and the clearance between the protruding rod (a1) and the side wall is defined as the second clearance. The first clearance, the second clearance and the cavity (6) are connected.

3. The solenoid valve according to claim 1, characterized in that, The lower end face of the moving iron core body (51) and the upper end face of the sealing element (52) have a first gap. The boss part (511) includes a protruding rod (a1), and the groove part (c1) is provided with a side wall. The protruding rod (a1) is tightly fitted to the side wall.

4. The solenoid valve according to any one of claims 1 to 3, characterized in that, Both the boss (511) and the recess (521) are configured to have a T-shaped axial cross section. The boss (511) has a first stepped surface (514), and the recess (521) has a second stepped surface (525). The first stepped surface (514) and the second stepped surface (525) interact to confine the boss (511) within the recess (521).

5. The solenoid valve according to any one of claims 1 to 3, characterized in that, Along the thickness direction of the seal (52), the drain end (e1) extends to the bottom surface (527) of the recess (521), and the drain end (e2) extends to the second sealing surface (522).

6. The solenoid valve according to claim 5, characterized in that, The valve seat core (31) is provided with a first channel (311), and the pressure relief hole (528), the concave hole (521) and the first channel (311) are coaxially arranged.

7. The solenoid valve according to claim 6, characterized in that, The inner diameter of the pressure relief hole (528) is defined as d1, the maximum outer diameter of the boss (511) is defined as d2, and the inner diameter of the first channel (311) is defined as d3. d1, d2, and d3 satisfy the following conditions: d1 <d3<d2。 8. The solenoid valve according to claim 7, characterized in that, When 1mm < d3 ≤ 2.0mm, 0.6mm ≤ d1 ≤ 1.6mm, and / or, d2 ≥ 3d3 / 2.

9. The solenoid valve according to claim 7, characterized in that, When d3 > 2.0 mm, d1 > 1.6 mm, and / or, d2 ≥ 2d3.

10. The solenoid valve according to any one of claims 1 to 3, characterized in that, The seal (52) is made of an elastic material.

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