Electromagnetic valve

Abstract

The invention relates to the technical field of valve devices, and discloses an electromagnetic valve. The electromagnetic valve comprises a valve seat core component and a movable iron core component, the electromagnetic valve is provided with a cavity, and the movable iron core component is at least partially located in the cavity; the valve seat core component comprises a valve seat core, the valve seat core comprises a valve port part, the movable iron core component comprises a movable iron core body and a sealing piece, a boss part is arranged on the lower portion of the movable iron core body, the sealing piece is provided with a groove part, the groove part is provided with a concave hole, the concave hole is communicated with the cavity, the boss part is sleeved with the sealing piece, the sealing piece is provided with a second sealing face, and the second sealing face can abut against or be away from the valve port part. A pressure relief hole is formed in the sealing piece; one side of the pressure relief hole is opened to form a drainage end, the other side of the pressure relief hole is opened to form a drainage end, the drainage end penetrates to the concave hole, and the drainage end penetrates to the outer surface of the sealing part; the pressure relief hole is used for leading in fluid from the drainage end and discharging the fluid from the drainage end when the fluid flows into the concave hole. When the electromagnetic valve is applied, the opening degree of the valve port part can be relatively guaranteed in a full-open state.

Description

Technical Field

[0001] The present application relates to the technical field of valve devices, and in particular to a solenoid valve. Background Art

[0002] The solenoid valve may include a stationary iron core component, a valve seat component, and a valve seat core, with a moving iron core component disposed within the valve body. The valve seat core is provided with a valve port portion having a valve port, and the moving iron core component includes a moving core body and a piston member, which can abut against or move away from the valve port portion. The moving core body has a flange mating portion, and the piston member fits within the outer periphery of the flange mating portion. Fluid easily flows into the mating groove of the piston member through the position between the flange mating portion of the moving core body and the piston member. The lower end face of the piston member is easily bulged by pressure, which reduces the valve opening 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 is still a technical problem that needs to be solved urgently by those skilled in the art. Summary of the Invention

[0004] The purpose of this application is to provide a solenoid valve with a new structure, which can relatively guarantee the opening of the valve mouth in the fully open state.

[0005] To solve the above technical problems, the present application provides a solenoid valve, comprising a valve seat core component and a movable iron core component; the solenoid valve is provided with a cavity, and the movable 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, and the movable iron core component includes a movable iron core body and a sealing member, the lower portion of the movable iron core body is provided with a boss portion, the sealing member has a groove portion, the groove portion is provided with a concave hole, and the concave hole is communicated with the cavity, the sealing member is sleeved on the boss portion, the sealing member is provided with a second sealing surface, the second sealing surface can abut against or away from the valve port portion, and the sealing member is provided with a pressure relief hole;

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

[0007] The present invention provides a solenoid valve, which is provided with a pressure relief hole on the sealing member, so that one side opening of the pressure relief hole is connected to the concave hole of the groove portion, and the other side opening of the pressure relief hole is connected to the outer surface of the sealing member. In the fully open state, the second sealing surface is away from the valve mouth portion, one side opening is connected to the concave hole, and the other side opening is connected to the cavity. Even if the fluid enters the concave hole from the cavity, the pressure can be relieved through the pressure relief hole, which greatly reduces the risk of the sealing surface of the seal being convex downward due to the pressure inside the concave hole. In the fully open state, the opening of the valve mouth portion can be relatively guaranteed. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 A partial cross-sectional view of a solenoid valve according to an embodiment of the present application;

[0009] Figure 2 A full cross-sectional view of the solenoid valve according to an embodiment of the present application;

[0010] Figure 3 for Figure 2 Schematic diagram of the structure of the valve seat core component of the solenoid valve;

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

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

[0013] Figure 6 for Figure 2 Schematic diagram of the structure 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 moving iron core component;

[0015] Figure 8 for Figure 6 Schematic diagram of the structure of the seal of the moving iron core component;

[0016] Figure 9 for Figure 2 Schematic diagram of the instantaneous state of the coil when power is applied when the boss portion of the movable iron core body and the recessed hole of the seal have a small interference fit in the solenoid valve;

[0017] Figure 10 for Figure 2 Schematic diagram of the fluid path between the boss of the moving iron core body and the recessed hole of the seal in the solenoid valve after the valve port is opened.

[0018] The reference numerals in the above drawings are described as follows:

[0019] 1-static iron core components;

[0020] 2-valve seat component;

[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-Return spring;

[0023] 5 - moving iron core component, 51 - moving iron core body, 511 - boss portion, 512 - first lower end surface, 513 - first outer side surface, 514 - first step surface, 515 - second outer side surface, 516 - second lower end surface, 52 - sealing member, 521 - recessed hole, 522 - second sealing surface, 523 - first upper end surface, 524 - first inner side surface, 525 - second step surface, 526 - second inner side surface, 527 - bottom surface, 528 - pressure relief hole; a1 - boss rod, a2 - boss, b1 - inner hole, b2 - step hole, c1 - groove portion, c2 - sealing portion, e1 - drainage end, e2 - discharge end;

[0024] 6-Cavity. DETAILED DESCRIPTION

[0025] In order to enable those skilled in the art to better understand the present application, the present application is further described in detail below with reference to the accompanying drawings and specific implementation methods.

[0026] In the description of this application, it should be noted that the directions "up" and "down" in this application are all in the Figure 1 For perspective, the up and down direction is also the axial direction of the solenoid valve.

[0027] The terms "first", "second", etc. mentioned in this application are only used to facilitate the description of two or more structures or components with the same or similar structures and / or functions, and do not mean any special limitation on the 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 according to the embodiment of the present application. Figure 2 This is a full cross-sectional view of the solenoid valve according to the embodiment of the present application. Figure 3 for Figure 2 Schematic diagram of the structure of the valve seat core component of the solenoid valve. Figure 4 for Figure 3 Schematic diagram of the structure of the valve seat core of the valve seat core component, Figure 5 for Figure 3 Schematic diagram of the structure of the valve seat core sleeve of the valve seat core component, Figure 6 for Figure 2 The structural diagram of the moving iron core component of the solenoid valve. Figure 7 for Figure 6 The structural diagram of the moving iron core body of the moving iron core component, Figure 8 for Figure 6 Schematic diagram of the structure of the seal of the moving iron core component.

[0029] In the examples provided in this application, 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 is provided with 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 in FIG. Figure 3 and Figure 4 As shown, the valve seat core 31 includes a valve port portion 312. Figure 6 As shown, the moving iron core component 5 includes a moving iron core body 51 and a sealing member 52. The lower portion of the moving iron core body 51 is provided with a boss portion 511. The sealing member 52 has a groove portion c1. The groove portion c1 is provided with a recessed hole 521. The recessed hole 521 is connected to the cavity 6. The sealing member 52 is sleeved on the boss portion 511. Figure 8 As shown, the sealing member 52 is provided with a second sealing surface 522, and the second sealing surface 522 can abut against or be away from the valve mouth portion 312. Figure 6 and Figure 8 As shown, the seal 52 is provided with a pressure relief hole 528, one side of the pressure relief hole 528 is opened to form a drainage end e1, and the other side is opened to form a drainage end e2, the drainage end e1 is also the end where the fluid flows in, and the drainage end e2 is also the end where the fluid flows out, the drainage end e1 is connected to the recessed hole 521, and the drainage end e2 is connected to the outer surface of the seal 52; in the fully open state, the seal 52 is away from the valve mouth portion 312, and the cavity 6, the recessed hole 521 and the pressure relief hole 528 are connected.

[0030] With such arrangement, in the fully open state, one side opening of the pressure relief hole 528 is connected to the recessed hole 521, and the other side opening is connected to the cavity 6. Even if the fluid flows from the cavity 6 through the position between the upper end surface of the seal 52 and the lower end surface of the moving iron core body 51 into the interior of the recessed hole 521, the pressure can be relieved through the pressure relief hole 528. Specifically, the diversion end e1 can introduce the fluid into the pressure relief hole 528, and flow out of the seal 52 through the discharge end e2 and into the cavity 6, so that the fluid pressure in the gap between the boss portion 511 and the recessed hole 521 is quickly balanced to a large extent, so that the second sealing surface 522 on the seal 52 remains relatively flat. After the valve is fully opened, 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 of the solenoid valve and the theoretical design opening, thereby relatively ensuring the matching of the actual value of the fully open flow of the solenoid valve with the design value.

[0031] For actual settings, please refer to Figure 1 and Figure 2 The solenoid valve may further include a static iron core component 1, which may be axially connected to the valve seat core component 3. As can be seen from the above, the solenoid valve provided by the embodiment of the present application solves the technical problem that the actual opening of the solenoid valve is too small due to the fluid flowing into the concave hole 521. Please refer to Figures 1 to 2If the pressure relief hole 528 is not provided, it is often necessary to increase the actual opening between the moving iron core component 5 and the static iron core component 1 to compensate for the reduction in opening caused by the fluid flowing into the recessed hole 521. Increasing the opening between the moving iron core component 5 and the static iron core component 1 often requires increasing the valve opening current of the solenoid valve. For example, according to actual measurements, the fluid flowing into the recessed hole 521 may cause the second sealing surface 522 to bulge downward by a distance greater than 0.1 mm. When the opening increases by 0.1 mm, the valve opening current may need to be increased by 0.3 A. This improvement method is prone to lose sight of one thing while focusing on another, and will weaken the valve opening performance of the solenoid valve. The solenoid valve provided in the embodiment of the present application only needs to provide a pressure relief hole 528 on the sealing component 52, without increasing the valve opening current. It can relatively guarantee the opening of the solenoid valve without affecting the valve opening performance of the solenoid valve.

[0032] In actual setting, the static iron core component 1 and the valve seat core component 3 are connected along the axial direction. The specific connection structure between the two is not limited. For example, please refer to Figure 1 and Figure 2 The solenoid valve may further include a valve seat component 2 , through which the static iron core component 1 and the valve seat core component 3 may be connected.

[0033] The embodiment of the present application does not limit the specific structure of the valve seat core component 3, as long as it has a valve seat core 31. For example, please refer to Figure 3 and Figure 5 The valve seat core component 3 may further include a valve seat core sleeve 32. The upper end of the valve seat core 31 is axially inserted into the valve seat core sleeve 32 and fixed. The upper end of the valve seat core sleeve 32 is axially inserted into the valve seat component 2 and fixed. A first channel 311 is provided on the valve seat core 31, and the upper end of the first channel 311 forms the above-mentioned valve mouth portion 312. The upper end surface of the valve seat core 31 forms a first sealing surface 313. A second channel 321 is provided on the valve seat core sleeve 32. The interior of the valve seat component 2 and the interior of the valve seat core sleeve 32 form the above-mentioned cavity 6.

[0034] In the examples provided in this application, please refer to Figure 7 In the moving iron core component 5, the moving iron core body 51 and the boss portion 511 are integrally arranged, which has a stable structure, is easy to manufacture, and has a low cost. Obviously, the moving iron core body 51 and the boss portion 511 can also be arranged separately, and this application does not limit this.

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

[0036] In actual configuration, the seal 52 can be made of an elastic material to achieve a good sealing effect. The elastic material is a material with the ability to recover deformation, which can undergo elastic deformation under the action of an external force but return to its original shape after the external force is removed. Specifically, the elastic material can be a rubber material, a spring steel material, or a thermoplastic elastomer material, which is not limited in this application.

[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 capabilities, resulting in excellent sealing performance, and can tightly engage with the first sealing surface 313 when pressing against and blocking the valve opening 312 to prevent fluid leakage, but also has excellent wear resistance, oxidation resistance, and corrosion resistance, allowing for long-term use in harsh environments, thereby improving the reliability and applicability of the solenoid valve.

[0038] In the embodiment provided in the present application, the seal 52 is mounted on the boss portion 511, that is, the boss portion 511 is limited to the recessed hole 521. The limitation here refers to the constraint on the relative movement of the boss portion 511 and the seal 52 in the axial direction. 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 separate from the boss portion 511. In this way, the process of opening and closing the valve is smoother.

[0039] In actual configuration, the specific limiting structure between the boss portion 511 and the recessed hole 521 is not limited, as long as it can limit the axial separation of the boss portion 511 and the sealing member 52 .

[0040] As an alternative, please refer to Figure 6-Figure 8The boss portion 511 and the recessed hole 521 are both constructed to have a T-shaped axial cross-section, the boss portion 511 has a first step surface 514, and the recessed hole 521 has a second step surface 525. The first step surface 514 interacts with the second step surface 525 to limit the boss portion 511 to the recessed hole 521.

[0041] The T-shaped surface is a stepped shape with one end having a smaller outline than the other. Specifically, the boss portion 511 comprises, from top to bottom along the axial direction, a protruding rod a1 and a boss a2, while the recessed hole 521 comprises, from top to bottom along the axial direction, an inner hole b1 and a stepped hole b2. Taking the boss portion 511 as an example, both the protruding rod a1 and the boss a2 can be cylindrical or prism-shaped.

[0042] Please refer to Figure 7 and Figure 8 It is understood that the convex rod a1 and the boss a2 can both be cylindrical, the outer diameter of the convex rod a1 is smaller than the outer diameter of the boss a2, the inner hole b1 is a circular hole matching the shape of the convex rod a1, the step hole b2 is a circular hole matching the shape of the boss a2, and the inner diameter of the inner hole b1 is smaller than the inner diameter of the step hole b2. In this embodiment, the portion of the seal 52 in which the recessed hole 521 is opened axially from top to bottom is the recessed groove portion c1, and the remaining portion is the seal 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 face of the protruding rod a1 is the first outer side face 513, the upper end face of the boss a2 is the above-mentioned first step face 514, the outer side face of the boss a2 is the second outer side face 515, and the lower end face of the boss a2 is the second lower end face 516; the inner side face of the inner hole b1 is the first inner side face 524, the top face of the step hole b2 is the above-mentioned second step face 525, the inner side face of the step hole b2 is the second inner side face 526, and the step hole b2 has a bottom face 527.

[0043] In this arrangement, the first step surface 514 in the boss portion 511 interacts with the second step surface 525 in the recessed hole 521 to form a limiting structure, so that the boss portion 511 can drive the seal 52 to move upward, and ensure that the seal 52 does not fall off during the downward movement of the boss portion 511, thereby limiting 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, so that 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 on the valve seat core 31 to achieve stable sealing.

[0044] The above embodiment describes that the boss portion 511 and the recessed hole 521 form the above-mentioned limiting structure through two step surfaces. In other embodiments of the present 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 truncated cone-shaped or prism-shaped to form a limiting structure through the outer side surface of the boss portion 511 and the inner side surface of the recessed hole 521. The specific principle is similar to the limiting structure formed by the above-mentioned two step surfaces and will not be repeated here.

[0045] It is readily understood that the location of the pressure relief hole 528 is not limited, as long as it can discharge the fluid flowing into the recessed hole 521. For example, the drainage end e1 of the pressure relief hole 528 may extend through the first inner side surface 524 or the second inner side surface 526 of the recessed hole 521 to drain the fluid laterally, or through the bottom surface 527 of the recessed hole 521 to drain the fluid from the bottom. The drainage end e2 of the pressure relief hole 528 may extend through the side surface of the sealing member 52 to relieve pressure laterally, or through the second sealing surface 522 of the sealing member 52 to relieve pressure downward.

[0046] In the examples provided in this application, please refer to Figure 8 Along the thickness direction of the sealing member 52, that is, the up and down direction, the drainage end e1 penetrates to the bottom surface 527 of the recessed hole 521, and the discharge end e2 penetrates to the second sealing surface 522, that is, the pressure relief hole 528 penetrates from the bottom surface 527 to the second sealing surface 522. In this way, the pressure relief hole 528 can drain the fluid from the bottom of the recessed hole 521 and discharge the fluid to the bottom of the sealing member 52. The drainage point is located at the end of the fluid flow in the recessed hole 521. The discharge direction is consistent with the main flow direction of the fluid in the cavity 6, which can improve the pressure relief effect and improve the consistency between the actual opening and the theoretical opening of the solenoid valve.

[0047] In actual setting, 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 discharge process smoother, thereby improving the pressure relief effect.

[0048] In the embodiment provided in the present 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 effect of using the pressure relief hole 528 for pressure relief, but also reduce the influence 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 Figure 9 and Figure 10 , Figure 9 for Figure 2 Schematic diagram of the instantaneous state of the coil when power is applied when the boss of the moving iron core body and the recessed hole of the seal have a small interference fit in the solenoid valve. Figure 10 for Figure 2Schematic diagram of the fluid path after the boss of the moving iron core body and the concave hole of the seal are opened in the solenoid valve. Figure 9 The dotted line represents the instantaneous shape of the seal 52 after elastic deformation, and the arrow represents the fluid pressure on the corresponding end face. Figure 10 The dashed line with an arrow is the fluid flow path.

[0050] In actual configuration, the boss portion 511 and the recessed hole 521 may be clearance-fitted or tight-fitted, and this application does not impose any restrictions thereto.

[0051] In one embodiment provided herein, a first gap is defined between the lower end face 512 of the movable iron core body 51 and the upper end face 523 of the seal 52. The protruding rod a1 in the boss portion 511 is clearance-matched with the sidewall of the recessed portion c1. The gap between the protruding rod a1 and the sidewall is defined as a second gap. The first gap, the second gap, and the cavity 6 are interconnected. This arrangement ensures that the first gap allows the boss portion 511, even with a T-shaped axial cross-section, to be smoothly assembled into the recessed hole 521, facilitating removal of the boss portion 511. The clearance between the protruding rod a1 and the recessed portion c1 allows for a certain amount of clearance to be reserved, making assembly and disassembly of the two more convenient and reducing manufacturing costs. Among them, the side wall of the groove part c1 used to cooperate with the protruding rod a1 corresponds to the first inner surface 524 of the above-mentioned inner hole b1. It is not difficult to understand that in the boss part 511, in addition to the protruding rod a1 being able to cooperate with the side wall clearance of the groove part c1, the boss a2 can also cooperate with the side wall clearance of the groove part c1.

[0052] In another embodiment provided in the present application, there is a first gap between the lower end surface of the moving iron core body 51 and the upper end surface of the seal 52, and the protruding rod a1 in the boss portion 511 is tightly fitted with the side wall of the groove portion c1, that is, it can have a small interference fit, which can provide good positioning accuracy, ensure good centering and coaxiality, and enhance 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 top of the concave hole 521. Of course, if the first gap does not exist, the fluid may also penetrate from the position between the first lower end surface 512 and the first upper end surface 523 to the top of the concave hole 521. The following takes the existence of the first gap as an example to illustrate the working principle of the solenoid valve provided by the embodiment of the present application:

[0054] When the second gap is present between the boss portion 511 and the recessed hole 521, the coil is energized, and after the solenoid valve is opened, the fluid entering the cavity 6 may enter the recessed hole 521 from the first gap through the second gap. At this time, if the pressure relief hole 528 is not provided, the fluid entering the recessed hole 521 will generate a downward force acting on the bottom surface 527 of the recessed hole 521, causing the sealing portion c2 in the sealing member 52 to elastically deform and bulge downward, thereby causing the second sealing surface 522 on the sealing member 52 to bulge downward, resulting in the vertical distance between the second sealing surface 522 and the first sealing surface 313 on the valve seat core 31 being less than the designed distance after the valve is opened, causing the actual opening of the solenoid valve to be less than the theoretical designed opening, and thus the actual flow rate after the valve is fully opened does not match the designed flow rate. Please refer to Figure 10 In the embodiment provided in the present application, a pressure relief hole 528 connected to the recessed hole 521 is provided on the sealing member 52. After the fluid enters the recessed hole 521, it will continue to flow downward out of the sealing member 52 from the pressure relief hole 528, so that the second sealing surface 522 can remain relatively flat, which can relatively ensure the consistency between the actual opening of the solenoid valve and the theoretical design opening.

[0055] When there is a small interference fit between the boss portion 511 and the recessed hole 521: although there is no second gap between the contact surfaces of the boss portion 511 and the recessed hole 521 when the coil is not energized, when the valve mouth portion 312 is closed, the second sealing surface 522 on the sealing member 52 fits with the first sealing surface 313 on the valve seat core 31. When the fluid in the pipeline connected to the solenoid valve flows in the forward direction, the fluid flows from the second channel 321 into the cavity 6. Since the area of ​​the first upper end surface 523 of the sealing member 52 is larger than the area of ​​the exposed portion of the second sealing surface 522 of the sealing member 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 direction of the combined pressure of the two end surfaces is downward. At the moment 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 sealing member 52 causes the sealing member 52 to still be pressed against the valve seat core 31, that is, the second sealing surface 522 has not yet separated from the first sealing surface 313, and the boss portion 511 exerts an upward pulling effect on the groove portion c1, causing the groove portion c1 to elastically deform, thereby elastically deforming the first upper end surface 523, the first inner side surface 524, and the second step surface 525. Specifically, the first inner side surface 524 expands radially outward, and a second gap appears between it and the first outer side surface 513 of the protruding rod a1 in the boss portion 511, so that the fluid can enter from the first gap through the second gap. If the pressure relief hole 528 is not provided, the fluid entering the recessed hole 521 will cause the sealing portion c2 of the seal 52 to elastically deform and bulge downward, thereby causing the second sealing surface 522 to bulge downward. When the movable iron core body 51 continues to move upward, driving the seal 52 to leave the valve seat core 31, the above-mentioned elastic deformation of the sealing portion c2 has not yet recovered, resulting in the vertical distance between the second sealing surface 522 and the first sealing surface 313 being less than the designed distance after the valve is opened, thereby causing the actual opening of the solenoid valve to be less than the theoretical design opening, and the actual flow rate after the valve is fully opened to not match the designed flow rate. In the embodiment provided in the present application, a pressure relief hole 528 is provided on the seal 52 that is connected to the recessed hole 521. After the fluid enters the interior of the recessed hole 521, it will continue to flow downward out of the seal 52 through the pressure relief hole 528, thereby allowing the second sealing surface 522 to remain relatively flat, which can relatively ensure the consistency between the actual opening of the solenoid valve and the theoretical design opening.

[0056] It can be seen that the solenoid valve provided in the embodiment of the present application has a pressure relief hole 528 on the seal 52, so no matter whether the boss portion 511 and the recessed hole 521 are clearance-fitted or tight-fitted, the actual opening can be relatively guaranteed to be consistent with the theoretical design opening.

[0057] In actual configuration, the size relationship among the pressure relief hole 528 , the recessed hole 521 and the first channel 311 is not limited.

[0058] In the examples provided in this application, please refer to Figure 10 , define the inner diameter of the pressure relief hole 528 as d1, the maximum outer diameter of the boss portion 511 as d2, that is, the outer diameter of the boss a2 is d2, and the inner diameter of the first channel 311 is d3. d1, d2 and d3 meet 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 easy 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 can be understood that when d3>2.0mm, d1>1.6mm and d2≥2d3 can also be satisfied at the same time, so as to form a reasonable first matching wall thickness and second matching wall thickness while ensuring the pressure relief effect of the pressure relief hole 528, thereby further ensuring that the opening of the pressure relief hole 528 will not weaken the sealing performance of the solenoid valve.

[0068] It can be seen that in the embodiment provided in the present application, by designing 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, the pressure relief effect of the pressure relief hole 528 can be ensured, so as to relatively ensure the matching between the actual value of the fully open flow rate after the solenoid valve is opened and the design value, while not 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 description of the above embodiments is only intended to help understand the device and its core concept of this application. It should be noted that for those skilled in the art, without departing from the principles of this application, various improvements and modifications can be made to this application, and such improvements and modifications also fall within the scope of protection of the claims of this application.

Claims

1. A solenoid valve, characterized in that: The invention comprises a valve seat core component (3) and a moving iron core component (5); the solenoid valve is provided with 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) comprises a valve seat core (31), and the valve seat core (31) comprises a valve mouth portion (312); the moving iron core component (5) comprises a moving iron core body (51) and a sealing member (52); the lower portion of the moving iron core body (51) is provided with a boss portion (511), and the moving iron core body (51) is provided with a boss portion (511). The sealing member (52) has a groove portion (c1), the groove portion (c1) is provided with a recessed hole (521), the recessed hole (521) is communicated with the cavity (6), the sealing member (52) is sleeved on the boss portion (511), the sealing member (52) is provided with a second sealing surface (522), the second sealing surface (522) can abut against or be away from the valve port portion (312), and the sealing member (52) is provided with a pressure relief hole (528); One side opening of the pressure relief hole (528) forms a drainage end (e1), and the other side opening forms a drainage end (e2). The drainage end (e1) passes through the concave hole (521), and the drainage end (e2) passes through the outer surface of the sealing member (52). In the fully open state, the sealing member (52) is away from the valve mouth (312), and the cavity (6), the concave hole (521) and the pressure relief hole (528) are connected.

2. The solenoid valve according to claim 1, characterized in that A first gap is provided between the lower end surface of the movable iron core body (51) and the upper end surface of the sealing member (52); the boss portion (511) includes a boss (a1); and the groove portion (c1) is provided with a side wall; The convex rod (a1) is fitted with the side wall gap, and the gap between the convex rod (a1) and the side wall is defined as a second gap. The first gap, the second gap and the cavity (6) are connected.

3. The solenoid valve according to claim 1, characterized in that A first gap is provided between the lower end surface of the movable iron core body (51) and the upper end surface of the sealing member (52); the boss portion (511) includes a boss (a1); and the groove portion (c1) is provided with a side wall; The protruding rod (a1) is tightly fitted with the side wall.

4. The solenoid valve according to any one of claims 1 to 3, characterized in that: The boss portion (511) and the recessed hole (521) are both constructed to have a T-shaped axial cross-section, the boss portion (511) has a first step surface (514), and the recessed hole (521) has a second step surface (525); the first step surface (514) and the second step surface (525) interact with each other to limit the boss portion (511) to the recessed hole (521).

5. The solenoid valve according to any one of claims 1 to 3, characterized in that: Along the thickness direction of the sealing member (52), the drainage end (e1) penetrates to the bottom surface (527) of the recessed hole (521), and the drainage end (e2) penetrates 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 recessed 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 portion (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>2.0mm, d1>1.6mm, and / or, d2≥2d3.

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

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