Valve device

Abstract

A valve device comprises a valve seat, a driving assembly and a piston assembly. The valve device is provided with a valve cavity; the driving assembly comprises a static iron core and a movable iron core; the valve device further comprises a sealing piece, the movable iron core is connected with the piston assembly, and the movable iron core can drive the piston assembly to move in the axial direction of the valve device. The piston assembly comprises a piston; the sealing piece is located on the piston, the wall forming the valve cavity in the axial direction of the valve device comprises a guiding section and a valve closing section, the inner diameter of the guiding section is larger than that of the valve closing section, and when the movable iron core and the static iron core are attracted, the sealing piece is pressed between the piston and the valve closing section in the radial direction of the piston. Or the sealing piece is located on the wall forming the valve cavity, the outer wall of the piston comprises a guiding section and a valve closing section in the axial direction of the valve device, the outer diameter of the guiding section is smaller than that of the valve closing section, and when the movable iron core and the static iron core are attracted, the sealing piece is pressed between the wall forming the valve cavity and the valve closing section in the radial direction of the piston; therefore, the driving force of the valve device can be reduced.

Description

Technical Field

[0001] The present application relates to the field of fluid control technology, and in particular to a valve device for a vehicle. Background Art

[0002] The valve device includes a direct-acting valve device, which uses the suction force of the moving iron core and the stationary iron core to directly drive the valve core or piston to move. The structure is simple, but the resistance is large during the movement of the valve core or piston, and the driving force of the moving iron core is high. Utility Model Content

[0003] The purpose of the present application is to provide a valve device, which is conducive to reducing the driving force of the valve device.

[0004] To achieve the above objectives, this application adopts the following technical solutions:

[0005] A valve device, comprising a valve seat, a drive assembly and a piston assembly; the valve device has a valve cavity; the drive assembly comprises a static iron core and a moving iron core; the valve device also comprises a sealing member, the moving iron core is connected to the piston assembly, and along the axial direction of the valve device, the moving iron core can drive the piston assembly to move; the piston assembly comprises a piston; the sealing member is located on the piston, along the axial direction of the valve device, the wall forming the valve cavity comprises a guide section and a valve closing section, the inner diameter of the guide section is larger than the inner diameter of the valve closing section, and when the moving iron core is attracted with the static iron core, along the radial direction of the piston, the sealing member is pressed between the piston and the valve closing section; or, the sealing member is located on the wall forming the valve cavity, along the axial direction of the valve device, the outer wall of the piston comprises a guide section and a valve closing section, the outer diameter of the guide section is smaller than the outer diameter of the valve closing section, and when the moving iron core is attracted with the static iron core, along the radial direction of the piston, the sealing member is pressed between the wall forming the valve cavity and the valve closing section.

[0006] In a technical solution provided in the present application, the valve device includes a seal located on the piston, and the wall forming the valve cavity includes a guide section and a valve closing section. The inner diameter of the guide section is larger than the inner diameter of the valve closing section. When the moving iron core and the static iron core are attracted, the seal is pressed between the piston and the valve closing section along the radial direction of the piston. In this way, compared with the solution in which the inner diameter of the wall forming the valve cavity remains unchanged, when the seal in this solution is located on the radial inner side of the guide section, the friction resistance between the seal and the guide section is smaller, which can reduce the driving force required for the movement of the piston, which is beneficial to reducing the driving force of the valve device.

[0007] In another technical solution provided by the present application, the valve device includes a seal located on the wall forming the valve cavity, the outer wall of the piston includes a guide section and a valve closing section, the outer diameter of the guide section is smaller than the outer diameter of the valve closing section, and when the moving iron core and the static iron core are attracted, the seal is pressed between the wall forming the valve cavity and the valve closing section along the radial direction of the piston; in this way, compared with the solution in which the outer diameter of the piston remains unchanged, when the seal in this solution is located on the radial outside of the guide section, the friction resistance between the seal and the guide section is smaller, which can reduce the driving force required for the movement of the piston, which is beneficial to reducing the driving force of the valve device. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 It is a schematic diagram of the three-dimensional structure of the valve device provided by the present application;

[0009] Figure 2 is a schematic cross-sectional structural diagram of the valve device in the first embodiment of the valve opening state;

[0010] Figure 3 is a schematic cross-sectional structural diagram of the valve device in a closed valve state in the first embodiment;

[0011] Figure 4 yes Figure 2 A schematic diagram of the enlarged structure at point A;

[0012] Figure 5 yes Figure 3 A schematic diagram of the enlarged structure at B;

[0013] Figure 6 is a structural schematic diagram of another implementation of the second section and its vicinity in the first embodiment of the valve device;

[0014] Figure 7 is an enlarged structural schematic diagram of a portion of a valve seat in the first embodiment of the valve device;

[0015] Figure 8 is a schematic cross-sectional structural diagram of the valve device in the second embodiment of the valve opening state;

[0016] Fig. 9 is a cross-sectional structural schematic diagram of the valve device in a valve-closed state in the second embodiment;

[0017] Fig.10 yes Figure 8 A schematic diagram of the enlarged structure at C;

[0018] Fig.11 yes Fig. 9 A schematic diagram of the structure at D of FIG.

[0019] Fig.12 is a structural schematic diagram of another implementation of the second section and its surrounding structures in the second embodiment of the valve device;

[0020] Fig.13is an enlarged structural schematic diagram of a piston in a second embodiment of a valve device;

[0021] Fig.14 It is an enlarged structural schematic diagram of the guide ring in the first embodiment and the second embodiment of the valve device.

[0022] Reference numerals:

[0023] 1. Valve seat; 10. Valve cavity; 100. Valve device; 101. First valve cavity; 102. Second valve cavity; 11. First channel; 12. Second channel; 13. Valve port;

[0024] 2. Driving assembly; 20. Static iron core; 21. Moving iron core; 22. Return spring; 23. Valve stem;

[0025] 3. Piston assembly; 30. Piston; 300. Accommodating groove; 301. Limiting groove; 31. Sealing member; 310. Sealing ring; 311. Sealing ring; 32. Guide ring; 320. Notch; 33. Balance hole;

[0026] 4. cannula; 40. cannula cavity;

[0027] 5. Coil assembly; 50. Coil body; 51. Frame;

[0028] 6. Resistance spacing;

[0029] L1, guide section; L11, first section; L12, second section; L2, valve closing section. DETAILED DESCRIPTION

[0030] The utility model is further described below in conjunction with the accompanying drawings and specific embodiments:

[0031] Combination Figures 1 to 3 , Figure 8 and Fig. 9 As shown, an embodiment of the valve device 100 is schematically shown. In this embodiment, the valve device 100 includes a valve seat 1, a drive assembly 2, a piston assembly 3, a sleeve 4, and a coil assembly 5. The valve device 100 has a valve cavity 10, which is located in the valve seat 1. The sleeve 4 has a sleeve cavity 40, wherein at least a portion of the piston assembly 3 is located in the valve cavity 10, at least a portion of the drive assembly 2 is located above the piston assembly 3 and in the sleeve cavity 40, the coil assembly 5 is located above the valve seat 1 and is sleeved on the outer periphery of the drive assembly 2 and the sleeve 4, along the axial direction of the valve device 100, part of the sleeve 4 is located between the coil assembly 5 and the valve seat 1, the sleeve 4 is fixedly or limit-connected to the valve seat 1 and sealed at the connection between the two, and in this embodiment, the sleeve 4 and the valve seat 1 are fixed and sealed by welding.

[0032] Combination Figure 2 , Figure 3 , Figure 8 and Fig. 9 As shown, the valve seat 1 includes a valve mouth portion 13, and the valve seat 1 also has a first channel 11 and a second channel 12. The sleeve cavity 40 is connected to the valve cavity 10, and the second channel 12 is connected to the valve cavity 10. The first channel 11 is located in the valve mouth portion 13 and is connected to the valve cavity 10. The second channel 12 is located in the valve mouth portion 13 and can be connected to the valve cavity 10. Specifically, the first channel 11 and the second channel 12 are both formed in the valve mouth portion 13.

[0033] Combination Figure 2 , Figure 3 , Figure 8 and Fig. 9 As shown, at least part of the drive assembly 2 is located above the piston assembly 3 and within the sleeve cavity 40. Specifically, the drive assembly 2 includes a static iron core 20 and a moving iron core 21. At least part of the static iron core 20 is located within the sleeve cavity 40 and is fixed to the wall forming the sleeve cavity 40. The fixing method may be welding, riveting or interference fit. The moving iron core 21 can move axially within the sleeve cavity 40. The static iron core 20 is closer to the piston assembly 3 than the moving iron core 21, or the moving iron core 21 is located above the static iron core 20. Of course, in other embodiments, the moving iron core 21 may also be closer to the piston assembly 3 than the static iron core 20, or the static iron core 20 is located above the moving iron core 21.

[0034] Combination Figure 2 , Figure 3 , Figure 8 and Fig. 9 As shown, the driving component 2 also includes a return spring 22, which is used to drive the moving iron core 21 to separate from the static iron core 20, or in other words, the return spring 22 can keep the moving iron core 21 and the static iron core 20 in a separated state. Specifically, the return spring 22 is arranged between the static iron core 20 and the moving iron core 21, and along the axial direction of the driving component 2, the opposite ends of the return spring 22 are respectively in contact with the static iron core 20 and the moving iron core 21.

[0035] Combination Figure 2 , Figure 3 , Figure 8 and Fig. 9 As shown, the coil assembly 5 is sleeved on the outer periphery of the drive assembly 2 and part of the sleeve 4. Further, the coil assembly 5 is sleeved on the outside of the sleeve 4, the static iron core 20 and the moving iron core 21, and the coil body 50 is located on the outside of the static iron core 20 and part of the moving iron core 21. Specifically, the coil assembly 5 also includes a coil body 50 and a skeleton 51. The coil body 50 is wound around the outside of at least part of the skeleton 51, the coil body 50 surrounds at least part of the static iron core 20, the coil body 50 surrounds at least part of the moving iron core 21, and the skeleton 51 is fixedly connected to the valve seat 1 by screws, or the skeleton 51 is interference fit with the sleeve 4 or fixedly connected by screws.

[0036] Combination Figure 2, Figure 3 , Figure 8 and Fig. 9 As shown, the piston assembly 3 includes a piston 30, and the moving iron core 21 is connected to the piston 30; specifically, in this embodiment, the drive assembly 2 also includes a valve stem 23, and the moving iron core 21 and the piston 30 are fixedly connected through the valve stem 23, and the two ends of the valve stem 23 are respectively fixedly connected to the moving iron core 21 and the piston 30; of course, in other embodiments, the moving iron core 21 can also be directly connected to the piston 30, or the valve stem 23 and the piston 30 are hinged.

[0037] The valve chamber 10 includes a first valve chamber 101 and a second valve chamber 102. Along the axial direction of the piston 30, the first valve chamber 101 and the second valve chamber 102 are respectively located on opposite sides of the piston 30. The piston 30 has a balancing hole 33, and the balancing hole 33 can communicate with the first valve chamber 101 and the second valve chamber 102.

[0038] Specifically, when the valve device 100 is in a closed valve state, the second valve chamber 102 is connected to the first channel 11, and the second channel 12 is connected to the first valve chamber 101 through the balancing hole 33. When the valve device 100 is in an open valve state, the first channel 11 is connected to the first valve chamber 101, the second channel 12, the balancing hole 33 and the second valve chamber 102.

[0039] Combination Figures 2 to 5 , Figure 7 , Figures 8 to 11 , Fig.13 The valve device 100 also includes a sealing member 31, which is located between the piston 30 and the side wall forming the valve cavity 10. Along the radial direction of the sealing member 31, the radial distance between the side wall forming the valve cavity 10 and the piston 30 is a resistance spacing 6; along the axial direction of the valve device 100, the moving iron core 21 can drive the piston 30 to move inside the valve cavity 10.

[0040] The valve device 100 also includes a guide section L1 and a valve closing section L2. Along the axial direction of the valve device 100, the guide section L1 and the valve closing section L2 are located on the outer wall of the piston 30, or the guide section L1 and the valve closing section L2 are located on the wall forming the valve cavity 10; the resistance spacing 6 of at least part of the guide section L1 is greater than the resistance spacing 6 of the valve closing section L2; when the moving iron core 21 and the static iron core 20 are attracted, the sealing member 31 abuts against the valve closing section L2, and the valve closing section L2 is roughly parallel to the axis of the valve device 100.

[0041] Combination Figures 2 to 5 , Figure 7As shown, in the first embodiment of the valve device 100, the outer wall of the piston 30 has a receiving groove 300, at least part of the sealing member 31 is located in the receiving groove 300, and the outer wall of the piston 30 is in clearance with the side wall forming the valve cavity 10; the side wall forming the valve cavity 10 includes a guide section L1 and a valve closing section L2, and the inner diameter of at least part of the guide section L1 is larger than the inner diameter of the valve closing section L2; specifically, the side wall forming the valve cavity 10 in the valve closing section L2 is substantially parallel to the axis of the piston 30;

[0042] In this arrangement, when the seal 31 abuts against the valve closing section L2, the pressure of the seal 31 abutting against the side wall forming the valve cavity 10 is relatively large, which helps to ensure the sealing effect between the piston 30 and the side wall forming the valve cavity 10;

[0043] In addition, the resistance distance 6 between the piston 30 located in the valve closing section L2 and the side wall forming the valve cavity 10 remains substantially unchanged. When the piston 30 moves axially inside the valve cavity 10, the side wall forming the valve cavity 10 has a stable guiding effect on the seal 31 and the piston 30. The axis of the piston 30 is not easily offset, which helps to prevent the piston 30 from being stuck between the side walls forming the valve cavity 10. Moreover, when the piston 30 abuts against the valve mouth portion 13, it helps to disperse the pressure applied by the piston 30 to the valve mouth portion 13, thereby ensuring the sealing effect of the piston 30 on the second channel 12.

[0044] Further, the guide section L1 includes a first section L11 and a second section L12. Specifically, the inner diameter of the side wall forming the valve cavity 10 in the first section L11 is substantially unchanged, and the inner diameter of the side wall forming the valve cavity 10 in the valve closing section L2 is substantially unchanged. The inner diameter of the side wall forming the valve cavity 10 in the first section L11 is greater than the inner diameter of the side wall forming the valve cavity 10 in the valve closing section L2. From the direction from the first section L11 to the valve closing section L2, the inner diameter of the side wall forming the valve cavity 10 in the second section L12 is reduced.

[0045] Combination Figures 2 to 5 In the first embodiment of the valve device 100, in the first section L11, the sealing member 31 and at least part of the side wall forming the valve cavity 10 are clearance fit, and in the valve closing section L2, the sealing member 31 and the side wall forming the valve cavity 10 are interference fit. Of course, in other embodiments, in the first section L11, the sealing member 31 and the side wall forming the valve cavity 10 may also be transition fit or interference fit; along the moving path of the sealing member 31, the starting end of the second section L12 of the side wall forming the valve cavity 10 is connected to the end of the first section L11, and the end of the second section L12 is connected to the starting end of the valve closing section L2;

[0046] This arrangement helps the seal 31 to smoothly transition from the first section L11 to the valve closing section L2 through the second section L12, which not only reduces the friction between the seal 31 and the side wall forming the valve cavity 10 in the first section L11, but also ensures the sealing between the seal 31 and the side wall forming the valve cavity 10 in the valve closing section L2. The second section L12 ensures the smooth transition from the first section L11 to the valve closing section L2.

[0047] Combination Figure 4 and Figure 5 In this embodiment, the axial cross section of the second section L12 of the side wall forming the valve cavity 10 is a straight line, that is, the slope of the side wall forming the valve cavity 10 does not change. In this embodiment, it is convenient to process the side wall forming the valve cavity 10 in the second section L12; of course, in other embodiments, the axial cross section of the second section L12 of the side wall forming the valve cavity 10 may also be a curve, a combination of curves, a combination of straight lines with different slopes, or a combination of a straight line and a curve;

[0048] Combination Figure 6 In the first embodiment of the valve device 100, in another embodiment of the second section L12, along the axial direction of the piston 30, from the first section L11 to the valve closing section L2, the slope of the second section L12 first increases and then decreases. In this embodiment, such a setting helps to shorten the length of the second section L12 on the outer wall of the piston 30. The slope of the part of the second section L12 close to the first section L11 is relatively small, and gradually increases as it moves away from the first section L11. At this time, there is a gap between the seal 31 and the second section L12, or there is a small pressure. The small slope can slowly change the inner diameter of the wall forming the valve cavity 10, alleviate the situation where the axis of the piston 30 is offset under the action of the wall forming the valve cavity 10, and help the seal 31 to smoothly enter the second section L12 from the first section L11;

[0049] The slope of the middle part of the second section L12 is relatively large. At this time, the pressure between the seal 31 and the middle part of the second section L12 is moderate. The wall forming the valve cavity 10 can play a certain guiding role on the piston 30 through the seal 31, which can alleviate the situation where the piston 30 is offset under the action of the wall forming the valve cavity 10; and at this time, there will be no large resistance between the wall forming the valve cavity 10 and the seal 31, and the distance between the moving iron core 21 and the static iron core 20 is relatively short, which can generate a large driving force, which is enough to overcome the resistance between the wall forming the valve cavity 10 and the seal 31. The large slope can make the inner diameter of the wall forming the valve cavity 10 change quickly, which helps the seal 31 to move quickly to the valve closing section L2;

[0050] The slope of the second section L12 close to the valve closing section L2 is also small, and gradually decreases as it approaches the valve closing section L12. At this time, the pressure between the seal 31 and the second section L12 is large, and the friction between the seal 31 and the second section L12 is large. The seal 31 is easily squeezed and deformed. The gradually decreasing slope can allow the inner diameter of the wall forming the valve cavity 10 to change slowly, which is beneficial to prevent the seal 31 from being squeezed and deformed; it helps the second section L12 of the seal 31 to smoothly enter the valve closing section L2;

[0051] With such arrangement, the beginning and the end of the second section L12 ensure the stability of the piston 30 during movement, and avoid the piston 30 from getting stuck during movement. The middle part of the second section L12 helps to shorten the overall length of the second section L12, and thus can reduce to a greater extent the friction resistance between the seal 31 and the second section L12 that needs to be overcome during the operation of the valve device 100, and thus improve the response speed of the valve device 100. At the same time, the end of part of the second section L12 can also be sealed with the seal 31, which helps to shorten the length of the valve closing section L2 while ensuring the sealing between the seal 31 and the wall forming the valve cavity 10. The friction resistance of the part where the end of the second section L12 is sealed with the seal 31 is relatively small, which helps to reduce the friction resistance of the side wall forming the valve cavity 10 to the seal 31, and helps to further improve the response speed of the valve device 100. It also reduces the friction loss between the side wall forming the valve cavity 10 and the seal 31, and helps to extend the life of the seal 31.

[0052] Combination Figures 2 to 6 As shown, the specific working process of the first embodiment of the valve device 100, the coil assembly 5 is energized, the static iron core 20 and the moving iron core 21 are attracted, in the initial stage of the attraction of the moving iron core 21 and the static iron core 20, the attraction force of the moving iron core 21 and the static iron core 20 is small, the piston 30 drives the seal 31 to move, at this time, the seal 31 abuts against the first section L11, at this time, the seal 31 and the side wall forming the valve cavity 10 are in a clearance fit, the friction between the seal 31 and the side wall forming the valve cavity 10 is small, the moving iron core 21 and the piston 30 mainly overcome the spring force of the return spring 22 to move downward;

[0053] The piston 30 continues to move toward the valve mouth 13. In the middle and late stages of the attraction of the moving iron core 21 and the static iron core 20, the attraction force between the moving iron core 21 and the static iron core 20 is relatively large. When the seal 31 is located at the second section L12, the gap fit between the seal 31 and the side wall forming the valve cavity 10 is changed to an interference fit. The friction between the seal 31 and the side wall forming the valve cavity 10 gradually increases. Since the attraction force between the moving iron core 21 and the static iron core 20 is also relatively large at this time, the moving iron core 21 is sufficient to overcome the friction between the seal 31 and the side wall forming the valve cavity 10 to drive the piston 30 to continue to move.

[0054] In the late stage of the attraction between the moving iron core 21 and the static iron core 20, the seal 31 enters the valve closing section L2, and the attraction force between the moving iron core 21 and the static iron core 20 continues to increase. At this time, the seal 31 and the side wall forming the valve cavity 10 are in interference fit, and the friction between the seal 31 and the side wall forming the valve cavity 10 remains constant. Since the attraction force between the moving iron core 21 and the static iron core 20 continues to increase at this time, the moving iron core 21 is sufficient to overcome the friction between the seal 31 and the side wall forming the valve cavity 10 to drive the piston 30 to abut against the valve mouth 13 to close the second channel 12, and the piston 30 moves to completely close the valve, and the valve device 100 closes the valve;

[0055] When the valve needs to be opened again, the coil assembly 5 is powered off. At this time, the compression amount of the return spring 22 is the largest, and the friction between the seal 31 and the outer wall of the piston 30 is also the largest. The elastic force of the return spring 22 drives the moving iron core 21 and the piston 30 to move, and the piston 30 overcomes the larger friction between the seal 31 and the valve closing section L2 and moves;

[0056] With such arrangement, at the initial stage of attraction of the moving iron core 21 and the stationary iron core 20, the attraction force of the moving iron core 21 and the stationary iron core 20 needs to overcome a smaller friction force between the seal 31 and the side wall forming the valve cavity 10, which helps to reduce the driving force of the valve device 100, especially the driving force required for the initial operation of the valve device 100, thereby reducing the starting power of the coil assembly 5, thereby reducing the volume of the coil assembly 5, and the maximum elastic force of the reset spring 22 overcomes the larger friction force between the seal 31 and the side wall forming the valve cavity 10, which helps to quickly open the valve.

[0057] Moreover, when the moving iron core 21 and the stationary iron core 20 are attracted, the sealing member 31 abuts against the valve closing section L2, and the radial pressure between the sealing member 31 and the valve closing section L2 is relatively large, so the static friction between the sealing member 31 and the valve closing section L2 is also relatively large, and the static friction between the sealing member 31 and the valve closing section L2 and the attraction force between the moving iron core 21 and the stationary iron core 20 can jointly overcome the elastic force of the return spring 22 to keep the moving iron core 21 and the stationary iron core 20 attracted. After the moving iron core 21 and the stationary iron core 20 are attracted, the driving force required to keep the moving iron core 21 and the stationary iron core 20 attracted can be slightly reduced;

[0058] This arrangement can reduce the power of the moving iron core 21 and the stationary iron core 20 of the coil assembly 5 , which helps to reduce the power consumption and heat generation of the coil assembly 5 , and helps to extend the life of the coil assembly 5 .

[0059] Combination Figure 2 , Figure 3 and Fig.14As shown, in the first embodiment of the valve device 100, further, the piston assembly 3 may also include a guide ring 32, the outer wall of the piston 30 has a limiting groove 301, at least part of the guide ring 32 is located in the limiting groove 301, along the radial direction of the piston 30, the outer ring wall of the guide ring 32 abuts against the wall forming the valve cavity 10, the guide ring 32 has a tendency to expand radially outward, and the outer diameter of the guide ring 32 can change under the action of radial force; along the axial direction of the piston 30, the seal 31 is closer to the valve closing section L2 than the guide ring 32.

[0060] Specifically, the guide ring 32 is made of hard material, the surface friction coefficient of the guide ring 32 is low, the friction coefficient of the guide ring 32 is less than or equal to the friction coefficient of the seal 31, and the guide ring 32 has a certain elasticity. In this embodiment, the axial cross-section of the guide ring 32 is rectangular, and along the axial direction of the guide ring 32, the opposite side end walls of the guide ring 32 are respectively abutted against the opposite side end walls forming the limit groove 301 in the axial direction; the guide ring 32 is made of polytetrafluoroethylene, and the guide ring 32 has a notch 320. The elasticity of the guide ring 32 itself can apply a radial outward elastic force to the outside world. The spacing of the notches 320 may decrease as the guide ring 32 is subjected to a radial force directed inward, and the inner diameter of the guide ring 32 decreases accordingly; the circumferential spacing of the portion of the guide ring 32 where the notches 320 are formed may increase as the guide ring 32 is subjected to a radial force directed outward, and the inner diameter of the guide ring 32 increases accordingly. Of course, in other embodiments, the guide ring 32 may not be elastic, and a metal or other elastic ring of material may be provided on the outer side of the guide ring 32 to drive the guide ring 32 to expand outward; or, the guide ring 32 may always abut against the guide segment L11, and the inner diameter of the guide ring 32 may not change;

[0061] With this arrangement, the guide ring 32 can always abut against the side wall forming the valve cavity 10, thereby playing a certain guiding role for the piston 30, thereby preventing the axis of the piston 30 from tilting during the movement of the piston 30, thereby preventing the piston 30 from getting stuck between the side walls forming the valve cavity 10.

[0062] Furthermore, the axial cross section of the guide ring 32 is rectangular, and along the axial direction of the guide ring 32, the opposite side end walls of the guide ring 32 are respectively in contact with the opposite side end walls forming the limiting groove 301;

[0063] Such an arrangement helps to improve the coaxiality between the guide ring 32 and the piston 30 , and utilizes the guide ring 32 to guide the axial direction of the piston 30 to avoid axial deviation of the piston 30 .

[0064] Combination Figures 2 to 6In the first embodiment of the valve device 100, a specific implementation of the sealing member 31 is provided. In this implementation, the sealing member 31 further includes a sealing ring 310 and a sealing ring 311. The sealing ring 311 is sleeved on the outer ring of the sealing ring 310. The sealing ring 311 is pressed between the sealing ring 310 and the side wall forming the valve cavity 10. The sealing ring 311 is fixed relative to the sealing ring 310. Specifically, the inner circumferential surface of the sealing ring 311 has an arc groove abutting against the outer ring of the sealing ring 310. During the movement of the piston 30, the sealing ring 311 slides relative to the side wall forming the valve cavity 10. Specifically, the sealing ring 311 adopts a hard sealing material, and the friction coefficient of the sealing ring 311 is less than the friction coefficient of the sealing ring 310. In this implementation, the sealing ring 311 is made of polytetrafluoroethylene material. Of course, in its implementation, the sealing ring 311 can also be made of other hard sealing materials.

[0065] In this way, the sealing ring 311 can reduce the friction between the sealing member 31 and the outer wall of the piston 30 , thereby reducing the driving force required for the piston 30 .

[0066] Combination Figures 8 to 11 As shown, in the second embodiment of the valve device 100, the side wall forming the valve cavity 10 has a receiving groove 300, and at least part of the sealing member 31 is located in the receiving groove 300. In this embodiment, the guide section L1 and the valve closing section L2 are both located on the side wall of the piston 30, and the outer diameter of at least part of the guide section L1 is smaller than the outer diameter of the valve closing section L2. Specifically, the outer wall of the piston 30 in the valve closing section L2 is substantially parallel to the axis of the piston 30.

[0067] In this arrangement, when the seal 31 abuts against the valve closing section L2, the radial abutment pressure between the seal 31 and the piston 30 is relatively large, which helps to ensure the sealing effect between the piston 30 and the side wall forming the valve cavity 10;

[0068] In addition, the resistance distance 6 between the piston 30 located in the valve closing section L2 and the side wall forming the valve cavity 10 remains substantially unchanged. When the piston 30 moves axially inside the valve cavity 10, the side wall forming the valve cavity 10 has a stable guiding effect on the seal 31 and the piston 30. The axis of the piston 30 is not easily offset, which helps to prevent the piston 30 from being stuck between the side walls forming the valve cavity 10. Moreover, when the piston 30 abuts against the valve mouth portion 13, it helps to disperse the pressure applied by the piston 30 to the valve mouth portion 13, thereby ensuring the sealing effect of the piston 30 on the second channel 12.

[0069] Further, the guide section L1 includes a first section L11 and a second section L12. Specifically, the outer diameter of the piston 30 in the first section L11 is substantially unchanged, and the outer diameter of the piston 30 in the valve closing section L2 is substantially unchanged. The outer diameter of the piston 30 in the first section L11 is smaller than the diameter of the piston 30 in the valve closing section L2. From the first section L11 to the valve closing section L2, the outer diameter of the piston 30 in the second section L12 increases.

[0070] Combination Figures 8 to 11 In the second embodiment of the valve device 100, in the first section L11, the seal 31 and the outer wall of the piston 30 are clearance fit, and in the valve closing section L2, the seal 31 and the outer wall of the piston 30 are interference fit. Of course, in other embodiments, in the first section L11, the seal 31 and the outer wall of the piston 30 may also be transition fit or interference fit; along the moving direction of the piston 30, in the outer wall of the piston 30, the beginning of the second section L12 is connected to the end of the first section L11, and the end of the second section L12 is connected to the beginning of the valve closing section L2;

[0071] In the second embodiment of the valve device 100, a specific implementation of the second section L12 is provided. In this implementation, the axial cross section of the outer wall of the piston 30 in the second section L12 is a straight line. In this implementation, it is convenient to process the outer wall of the piston 30 in the second section L12. Of course, in other implementations, the cross section of the second section L12 in the outer wall of the piston 30 may also be a curve, a combination of curves, a combination of straight lines with different slopes, or a combination of a straight line and a curve.

[0072] Combination Fig.12 In the second embodiment of the valve device 100, in another specific implementation of the second section L12, along the axial direction of the piston 30, from the first section L11 to the direction of the valve closing section L2, the slope of the second section L12 first increases and then decreases. In this embodiment, such a setting helps to shorten the length of the second section L12 on the outer wall of the piston 30. The slope of the part of the second section L12 close to the first section L11 is relatively small, and gradually increases as it moves away from the first section L11. At this time, there is a gap between the seal 31 and the second section L12, or there is a small pressure. The small slope can allow the outer diameter of the piston 30 to change slowly, alleviate the situation where the axis of the piston 30 is offset under the action of the seal 31, and help the seal 31 to smoothly enter the middle of the second section L12 from the first section L11;

[0073] The slope of the middle part of the second section L12 is relatively large. At this time, the pressure between the seal 31 and the second section L12 is moderate. The wall of the valve cavity 10 can play a certain guiding role on the piston 30 through the seal 31, which can alleviate the situation where the axis of the piston 30 is offset under the action of the seal 31; and at this time, no large resistance is generated between the piston 30 and the seal 31, and the distance between the moving iron core 21 and the static iron core 20 is relatively short, which can generate a large driving force, enough to overcome the resistance between the piston 30 and the seal 31. The large slope can make the outer diameter of the piston 30 change quickly, which helps the seal 31 to move quickly to the valve closing section L2;

[0074] The slope of the second section L12 close to the valve closing section L2 is also small, and gradually decreases as it approaches the valve closing section L12. At this time, the pressure between the seal 31 and the second section L12 is large, and the friction between the seal 31 and the second section L12 is large. The seal 31 is easily squeezed and deformed. The gradually decreasing slope can allow the outer diameter of the piston 30 to change slowly, which is beneficial to prevent the seal 31 from being squeezed and deformed; it helps the second section L12 of the seal 31 to smoothly enter the valve closing section L2;

[0075] With such arrangement, the starting end and the end of the second section L12 ensure the stability of the piston 30 during movement, and avoid the piston 30 from getting stuck during movement. The middle part of the second section L12 helps to shorten the overall length of the second section L12, thereby reducing the friction resistance between the seal 31 and the second section L2 that needs to be overcome during the operation of the valve device 100 within a larger stroke, thereby improving the response speed of the valve device 100. At the same time, the end of part of the second section L12 can also be sealed with the seal 31, which helps to shorten the length of the valve closing section L2 while ensuring the sealing of the seal 31 and the side wall of the piston 30; the friction resistance of the part where the end of the second section L12 is sealed with the seal 31 is relatively small, which helps to reduce the friction resistance of the side wall of the valve cavity 10 to the seal 31, and helps to further improve the response speed of the valve device 100; and reduces the friction loss between the side wall of the valve cavity 10 and the seal 31, which helps to extend the life of the seal 31.

[0076] Combination Figure 8 , Fig. 9 and Fig.14 As shown, in the second embodiment of the valve device 100, further, the valve device 100 may also include a guide ring 32, and the wall forming the valve cavity 10 has a limiting groove 301, at least part of the guide ring 32 is located in the limiting groove 301, along the radial direction of the piston 30, the inner ring wall of the guide ring 32 abuts against the outer wall of the piston 30, and the guide ring 32 has a tendency to shrink radially inward, and the outer diameter of the guide ring 32 can change under the action of radial force; along the axial direction of the piston 30, the seal 31 is closer to the valve closing section L2 than the guide ring 32.

[0077] Specifically, the guide ring 32 is made of a hard material with a low surface friction coefficient. The friction coefficient of the guide ring 32 is less than or equal to the friction coefficient of the seal 31, and has a certain elasticity. In the present embodiment, the guide ring 32 is made of polytetrafluoroethylene and has a notch 320. The guide ring 32 can apply a radial outward elastic force to the outside world. The spacing of the notches 320 can be reduced as the guide ring 32 is subjected to a radial force directed inward, and the inner diameter of the guide ring 32 is reduced accordingly; the circumferential spacing of the portion of the guide ring 32 where the notch 320 is formed can be increased as the guide ring 32 is subjected to a radial force directed outward, and the inner diameter of the guide ring 32 is increased accordingly; of course, in other embodiments, the guide ring 32 may also not be elastic, and an elastic ring of metal or other materials may be provided on the outside of the guide ring 32 to drive the guide ring 32 to shrink inward; or, the guide ring 32 is always in contact with the guide section L11, and the inner diameter of the guide ring 32 may not change.

[0078] With this arrangement, the guide ring 32 can always abut against the outer wall of the piston 30, thereby playing a certain guiding role for the piston 30, thereby preventing the axis of the piston 30 from tilting during the movement of the piston 30, thereby causing the piston 30 to be stuck between the side walls forming the valve chamber 10.

[0079] Furthermore, the axial cross section of the guide ring 32 is rectangular, and along the axial direction of the guide ring 32, the opposite side end walls of the guide ring 32 are respectively in contact with the opposite side end walls forming the limiting groove 301;

[0080] Such an arrangement helps to improve the coaxiality between the guide ring 32 and the piston 30 , and utilizes the guide ring 32 to guide the axial direction of the piston 30 to avoid axial deviation of the piston 30 .

[0081] Combination Figure 2 , Figure 3 , Figure 8 and Fig. 9 As shown, when the static iron core 20 is separated from the moving iron core 21, the working medium can enter the second valve chamber 102 from the first channel 11 and then flow out from the second channel 12, and the working medium can fill the balance hole 33 and the first valve chamber 101;

[0082] This arrangement helps to balance the pressure of the fluid medium inside the first valve chamber 101 and the second valve chamber 102, and helps to reduce the resistance encountered by the piston 30 during the valve closing process;

[0083] When the coil assembly 5 is energized and the static iron core 20 and the moving iron core 21 are attracted, the moving iron core 21 moves in the direction of the static iron core 20, and the moving iron core 21 drives the piston 30 to move toward the valve mouth 13 until the piston 30 abuts against the valve mouth 13. At this time, the piston 30 closes the second channel 12, and the sealing ring 31 is radially pressed between the piston 30 and the wall forming the valve cavity 10, so that the working medium cannot flow from the second valve cavity 102 into the second channel 12.

[0084] Combination Figures 8 to 12 As shown, the specific working process of the second embodiment of the valve device 100 is that the coil assembly 5 is energized, the static iron core 20 and the moving iron core 21 are attracted, and in the initial stage of the attraction of the moving iron core 21 and the static iron core 20, the attraction force of the moving iron core 21 and the static iron core 20 is small, and the piston 30 moves relative to the sealing member 31. At this time, the sealing member 31 abuts against the first section L11. At this time, the outer wall of the sealing member 31 and the outer wall of the piston 30 are clearance-matched, and the friction force between the sealing member 31 and the outer wall of the piston 30 is small. The moving iron core 21 and the piston 30 can move downward mainly by overcoming the spring force of the return spring 22;

[0085] The piston 30 continues to move toward the valve mouth 13. In the middle and late stages of the attraction between the moving iron core 21 and the static iron core 20, the attraction force between the moving iron core 21 and the static iron core 20 is relatively large. When the seal 31 is located at the second section L12, the seal 31 and the outer wall of the piston 30 change from a clearance fit to an interference fit. The friction between the seal 31 and the outer wall of the piston 30 gradually increases. Since the attraction force between the moving iron core 21 and the static iron core 20 is also relatively large at this time, the moving iron core 21 is sufficient to overcome the friction between the seal 31 and the outer wall of the piston 30 to drive the piston 30 to continue moving.

[0086] In the late stage of the attraction between the moving iron core 21 and the static iron core 20, the seal 31 enters the valve closing section L2, and the attraction force between the moving iron core 21 and the static iron core 20 continues to increase. At this time, the seal 31 and the outer wall of the piston 30 are interference fit, and the friction between the seal 31 and the outer wall of the piston 30 remains constant. Since the attraction force between the moving iron core 21 and the static iron core 20 continues to increase at this time, the moving iron core 21 is sufficient to overcome the friction between the outer wall of the seal 31 and the piston 30 to drive the piston 30 to abut against the valve mouth 13 to close the second channel 12, and the piston 30 moves to completely close the valve, and the valve device 100 closes the valve;

[0087] When the valve needs to be opened again, the coil assembly 5 is powered off. At this time, the compression amount of the return spring 22 is the largest, and the friction between the seal 31 and the outer wall of the piston 30 is also the largest. The elastic force of the return spring 22 drives the moving iron core 21 and the piston 30 to move, and the piston 30 overcomes the friction between the seal 31 and the outer wall of the piston 30 and moves;

[0088] With this arrangement, at the initial stage of attraction of the moving iron core 21 and the stationary iron core 20, the attraction force of the moving iron core 21 and the stationary iron core 20 needs to overcome a smaller friction force between the seal 31 and the side wall forming the valve cavity 10, which helps to reduce the driving force of the valve device 100, especially the driving force required for the initial operation of the valve device 100, thereby reducing the starting power of the coil assembly 5 and reducing the volume of the coil assembly 5; the maximum elastic force of the reset spring 22 overcomes the larger friction force between the seal 31 and the outer wall of the piston 30, which helps to quickly open the valve.

[0089] Moreover, when the moving iron core 21 and the stationary iron core 20 are attracted, the sealing member 31 abuts against the valve closing section L2, and the radial pressure between the sealing member 31 and the valve closing section L2 is relatively large, so the static friction between the sealing member 31 and the valve closing section L2 is also relatively large, and the static friction between the sealing member 31 and the valve closing section L2 and the attraction force between the moving iron core 21 and the stationary iron core 20 can jointly overcome the elastic force of the return spring 22 to keep the moving iron core 21 and the stationary iron core 20 attracted. After the moving iron core 21 and the stationary iron core 20 are attracted, the driving force required to keep the moving iron core 21 and the stationary iron core 20 attracted can be slightly reduced;

[0090] This arrangement can reduce the power of the moving iron core 21 and the stationary iron core 20 of the coil assembly 5 , which helps to reduce the power consumption and heat generation of the coil assembly 5 , and helps to extend the life of the coil assembly 5 .

[0091] In other embodiments of the drive component 2, compared with the first and second embodiments of the valve device 100, the difference lies in that, along the axial direction of the drive component 2, the moving iron core 21 is located between the stationary iron core 20 and the piston 30, and when the moving iron core 21 and the stationary iron core 20 are attracted, the valve device 100 is in an open valve state.

[0092] When the moving iron core 21 and the stationary iron core 20 are attracted, the seal 31 abuts against the valve closing section L2, and the static friction between the seal 31 and the valve closing section L2 is relatively large. The static friction between the seal 31 and the valve closing section L2 and the attraction force between the moving iron core 21 and the stationary iron core 20 can jointly overcome the elastic force of the return spring 22 to keep the moving iron core 21 and the stationary iron core 20 attracted. After the moving iron core 21 and the stationary iron core 20 are attracted, the driving force required to keep the moving iron core 21 and the stationary iron core 20 attracted can be slightly reduced.

[0093] Such an arrangement can also reduce the power of attraction between the moving iron core 21 and the stationary iron core 20 of the coil assembly 5 , which helps to reduce the power consumption and heat generation of the coil assembly 5 , and helps to extend the life of the coil assembly 5 .

[0094] Combination Figures 8 to 12In the second embodiment of the valve device 100, a specific implementation of the sealing member 31 is provided. In this implementation, the sealing ring 311 is sleeved on the inner ring of the sealing ring 310. The sealing ring 311 is pressed between the sealing ring 310 and the outer wall of the piston 30. The sealing ring 311 is fixed relative to the sealing ring 310. Specifically, the outer peripheral surface of the sealing ring 311 has an arc groove abutting against the outer ring of the sealing ring 310. During the movement of the piston 30, the sealing ring 311 slides relative to the outer wall of the piston 30. Specifically, the sealing ring 311 adopts a hard sealing material, and the friction coefficient of the sealing ring 311 is less than the friction coefficient of the sealing ring 310. In this implementation, the sealing ring 311 is made of polytetrafluoroethylene material. Of course, in its implementation, the sealing ring 311 can also be made of other hard sealing materials.

[0095] In this way, the sealing ring 311 can reduce the friction between the sealing member 31 and the outer wall of the piston 30 , thereby reducing the driving force required for the piston 30 .

[0096] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features of the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this description.

[0097] It should be noted that the above embodiments are only used to illustrate the present invention and are not intended to limit the technical solutions described in the present invention. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that those skilled in the art can still modify or make equivalent substitutions to the present invention, and all technical solutions and improvements thereof that do not depart from the spirit and scope of the present invention should be included in the scope of the claims of the present invention.

Claims

1. A valve device, characterized in that: The valve device (100) comprises a drive assembly (2) and a piston assembly (3); The valve device (100) comprises a valve chamber (10); The driving assembly (2) comprises a stationary iron core (20) and a moving iron core (21); The valve device (100) further comprises a sealing member (31), the moving iron core (21) is connected to the piston assembly (3), and the moving iron core (21) can drive the piston assembly (3) to move along the axial direction of the valve device (100); The piston assembly (3) comprises a piston (30); The sealing member (31) is located on the piston (30), and the wall of the valve cavity (10) formed along the axial direction of the valve device (100) includes a guide section (L1) and a valve closing section (L2), the inner diameter of the guide section (L1) is larger than the inner diameter of the valve closing section (L2), and when the moving iron core (21) and the static iron core (20) are attracted, the sealing member (31) is pressed between the piston (30) and the valve closing section (L2) along the radial direction of the piston (30); Alternatively, the sealing member (31) is located on the wall forming the valve cavity (10), and along the axial direction of the valve device (100), the outer wall of the piston (30) includes a guide section (L1) and a valve closing section (L2), and the outer diameter of the guide section (L1) is smaller than the outer diameter of the valve closing section (L2). When the moving iron core (21) and the stationary iron core (20) are attracted, along the radial direction of the piston (30), the sealing member (31) is pressed between the wall forming the valve cavity (10) and the valve closing section (L2).

2. The valve device according to claim 1, characterized in that The outer wall of the piston (30) has a receiving groove (300), at least part of the sealing member (31) is located in the receiving groove (300), and when the sealing member (31) is located radially inward of the guide section (L1), the moving iron core (21) is separated from the static iron core (20); The guide section (L1) comprises a first section (L11) and a second section (L12), and along the axial direction of the wall forming the valve cavity (10), one end of the second section (L12) is connected to the first section (L11), and the other end of the second section (L12) is connected to the valve closing section (L2); The inner diameter of the first section (L11) is larger than the inner diameter of the valve closing section (L2), and the inner diameter of the second section (L12) decreases in the direction from the first section (L11) to the valve closing section (L2).

3. The valve device according to claim 2, characterized in that The piston assembly (3) further comprises a guide ring (32), the outer wall of the piston (30) has a limiting groove (301), and at least a portion of the guide ring (32) is located in the limiting groove (301); Along the radial direction of the piston (30), the outer ring wall of the guide ring (32) abuts against the wall forming the valve cavity (10), the guide ring (32) has a tendency to expand radially outward, and the outer diameter of the guide ring (32) can be changed under the action of radial force; Along the axial direction of the piston (30), the sealing element (31) is closer to the valve closing section (L2) than the guide ring (32).

4. The valve device according to claim 1, characterized in that The wall forming the valve cavity (10) has a receiving groove (300), at least part of the sealing member (31) is located in the receiving groove (300), and when the sealing member (31) is located radially outside the guide section (L1), the moving iron core (21) is separated from the stationary iron core (20); The guide section (L1) comprises a first section (L11) and a second section (L12), and along the axial direction of the wall forming the valve cavity (10), one end of the second section (L12) is connected to the first section (L11), and the other end of the second section (L12) is connected to the valve closing section (L2); The outer diameter of the first section (L11) is smaller than the outer diameter of the valve closing section (L2), and the outer diameter of the second section (L12) increases in a direction from the first section (L11) to the valve closing section (L2).

5. The valve device according to claim 4, characterized in that The valve device (100) further comprises a guide ring (32), the wall forming the valve cavity (10) has a limiting groove (301), and at least a part of the guide ring (32) is located in the limiting groove (301); Along the radial direction of the piston (30), the inner ring wall of the guide ring (32) abuts against the piston (30); Along the axial direction of the piston (30), the sealing element (31) is closer to the valve closing section (L2) than the guide ring (32).

6. The valve device according to claim 3 or 5, characterized in that: The axial cross section of the guide ring (32) is rectangular; Along the axial direction of the guide ring (32), one side end wall of the guide ring (32) abuts against one side end wall forming the limiting groove (301), and / or, along the axial direction of the guide ring (32), the other side end wall of the guide ring (32) abuts against the other side end wall forming the limiting groove (301).

7. The valve device according to claim 3 or 5, characterized in that: The guide ring (32) has a notch (320) along the circumference of the guide ring (32); the inner diameter of the guide ring (32) can be changed under the action of a radial force; and the circumferential spacing of the notch (320) can be changed as the outer diameter of the guide ring (32) changes; When the limiting groove (301) is located on the wall forming the valve cavity (10), the guide ring (32) has a tendency to shrink radially inward; When the limiting groove (301) is located on the outer wall of the piston (30), the guide ring (32) has a tendency to expand radially outward.

8. The valve device according to claim 6, characterized in that The guide ring (32) has a notch (320) along the circumference of the guide ring (32); the inner diameter of the guide ring (32) can be changed under the action of a radial force; and the circumferential spacing of the notch (320) can be changed as the outer diameter of the guide ring (32) changes; When the limiting groove (301) is located on the wall forming the valve cavity (10), the guide ring (32) has a tendency to shrink radially inward; When the limiting groove (301) is located on the outer wall of the piston (30), the guide ring (32) has a tendency to expand radially outward.

9. The valve device according to claim 2 or 3 or 4 or 5 or 8, characterized in that: Along the axial direction of the valve device (100), from the first section (L11) to the valve closing section (L2), the inclination of the second section (L12) first increases and then decreases.

10. The valve device according to claim 6, characterized in that Along the axial direction of the valve device (100), from the first section (L11) to the valve closing section (L2), the inclination of the second section (L12) first increases and then decreases.

11. The valve device according to claim 7, characterized in that Along the axial direction of the valve device (100), from the first section (L11) to the valve closing section (L2), the inclination of the second section (L12) first increases and then decreases.

12. The valve device according to claim 2 or 3 or 4 or 5 or 8 or 10 or 11, characterized in that: The sealing member (31) comprises a sealing ring (310) and a sealing ring (311); along the axial direction of the sealing member (31), the sealing ring (310) and the sealing ring (311) are relatively fixed, and the friction coefficient of the sealing ring (311) is smaller than the friction coefficient of the sealing ring (310); When the sealing ring (311) is located between the sealing ring (310) and the guide section (L1) along the radial direction of the piston (30), the moving iron core (21) is separated from the static iron core (20); When the moving iron core (21) and the stationary iron core (20) are attracted, the sealing ring (311) is pressed tightly between the sealing ring (310) and the valve closing section (L2) along the radial direction of the piston (30).

13. The valve device according to claim 6, characterized in that The sealing member (31) comprises a sealing ring (310) and a sealing ring (311); along the axial direction of the sealing member (31), the sealing ring (310) and the sealing ring (311) are relatively fixed, and the friction coefficient of the sealing ring (311) is smaller than the friction coefficient of the sealing ring (310); When the sealing ring (311) is located between the sealing ring (310) and the guide section (L1) along the radial direction of the piston (30), the moving iron core (21) is separated from the static iron core (20); When the moving iron core (21) and the stationary iron core (20) are attracted, the sealing ring (311) is pressed tightly between the sealing ring (310) and the valve closing section (L2) along the radial direction of the piston (30).

14. The valve device according to claim 7, characterized in that The sealing member (31) comprises a sealing ring (310) and a sealing ring (311); along the axial direction of the sealing member (31), the sealing ring (310) and the sealing ring (311) are relatively fixed, and the friction coefficient of the sealing ring (311) is smaller than the friction coefficient of the sealing ring (310); When the sealing ring (311) is located between the sealing ring (310) and the guide section (L1) along the radial direction of the piston (30), the moving iron core (21) is separated from the static iron core (20); When the moving iron core (21) and the stationary iron core (20) are attracted to each other, the sealing ring (311) is pressed tightly between the sealing ring (310) and the valve closing section (L2) along the radial direction of the piston (30).

15. The valve device according to claim 9, characterized in that The sealing member (31) comprises a sealing ring (310) and a sealing ring (311); along the axial direction of the sealing member (31), the sealing ring (310) and the sealing ring (311) are relatively fixed, and the friction coefficient of the sealing ring (311) is smaller than the friction coefficient of the sealing ring (310); When the sealing ring (311) is located between the sealing ring (310) and the guide section (L1) along the radial direction of the piston (30), the moving iron core (21) is separated from the static iron core (20); When the moving iron core (21) and the stationary iron core (20) are attracted to each other, the sealing ring (311) is pressed tightly between the sealing ring (310) and the valve closing section (L2) along the radial direction of the piston (30).

16. The valve device according to claim 2 or 3 or 4 or 5 or 8 or 10 or 11 or 13 or 14 or 15, characterized in that: The valve device (100) further comprises a coil assembly (5), wherein the coil assembly (5) is sleeved on the outside of the drive assembly (2); The driving assembly (2) further comprises a return spring (22), wherein along the axial direction of the driving assembly (2), one end of the return spring (22) abuts against the moving iron core (21), and the other end of the return spring (22) is separated from the stationary iron core (20); Along the axial direction of the driving component (2), the static iron core (20) is located between the moving iron core (21) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in a valve-closing state; Alternatively, along the axial direction of the drive assembly (2), the moving iron core (21) is located between the static iron core (20) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in an open valve state.

17. The valve device according to claim 6, characterized in that The valve device (100) further comprises a coil assembly (5), wherein the coil assembly (5) is sleeved on the outside of the drive assembly (2); The driving assembly (2) further comprises a return spring (22), wherein along the axial direction of the driving assembly (2), one end of the return spring (22) abuts against the moving iron core (21), and the other end of the return spring (22) is separated from the stationary iron core (20); Along the axial direction of the driving component (2), the static iron core (20) is located between the moving iron core (21) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in a valve-closing state; Alternatively, along the axial direction of the drive assembly (2), the moving iron core (21) is located between the static iron core (20) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in an open valve state.

18. The valve device according to claim 7, characterized in that The valve device (100) further comprises a coil assembly (5), wherein the coil assembly (5) is sleeved on the outside of the drive assembly (2); The driving assembly (2) further comprises a return spring (22), wherein along the axial direction of the driving assembly (2), one end of the return spring (22) abuts against the moving iron core (21), and the other end of the return spring (22) is separated from the stationary iron core (20); Along the axial direction of the driving component (2), the static iron core (20) is located between the moving iron core (21) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in a valve-closing state; Alternatively, along the axial direction of the drive assembly (2), the moving iron core (21) is located between the static iron core (20) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in an open valve state.

19. The valve device according to claim 9, characterized in that The valve device (100) further comprises a coil assembly (5), wherein the coil assembly (5) is sleeved on the outside of the drive assembly (2); The driving assembly (2) further comprises a return spring (22), wherein along the axial direction of the driving assembly (2), one end of the return spring (22) abuts against the moving iron core (21), and the other end of the return spring (22) is separated from the stationary iron core (20); Along the axial direction of the driving component (2), the static iron core (20) is located between the moving iron core (21) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in a valve-closing state; Alternatively, along the axial direction of the drive assembly (2), the moving iron core (21) is located between the static iron core (20) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in an open valve state.

20. The valve device according to claim 12, characterized in that The valve device (100) further comprises a coil assembly (5), wherein the coil assembly (5) is sleeved on the outside of the drive assembly (2); The driving assembly (2) further comprises a return spring (22), wherein along the axial direction of the driving assembly (2), one end of the return spring (22) abuts against the moving iron core (21), and the other end of the return spring (22) is separated from the stationary iron core (20); Along the axial direction of the driving component (2), the static iron core (20) is located between the moving iron core (21) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in a valve-closing state; Alternatively, along the axial direction of the drive assembly (2), the moving iron core (21) is located between the static iron core (20) and the piston (30), and when the moving iron core (21) and the static iron core (20) are attracted, the valve device (100) is in an open valve state.

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