Normally open valve for double-cavity air spring

Abstract

The utility model relates to a normally open valve for a double-cavity air spring, which comprises a shell, a movable iron core axially moving and a coil assembly controlling the movable iron core to move are arranged in the shell, a base is mounted at one end of the shell, a base is mounted between the base and the coil assembly, and a valve port is arranged on the base. A tappet capable of moving axially is arranged at the position, corresponding to the valve port, between the base and the base, the tappet comprises a sleeve seat and a rod portion axially arranged at the top of the sleeve seat, the sleeve seat is of a circular sleeve-shaped structure, a first conical side wall is arranged in the middle of the sleeve seat, one end of the rod portion penetrates through the base to abut against the movable iron core, and an elastic piece is arranged between the sleeve seat and the base. And a first sealing ring which is in sealing fit with the first conical side wall is arranged at an inner hole of the base. According to the utility model, the outer diameters of different sections of the tappet are set, so that the friction force borne by the whole rotor is different and is gradually increased from opening to closing; and meanwhile, the variation of comprehensive force is reduced as much as possible, and the NVH characteristic of the whole electromagnetic valve is optimized.

Description

Technical Field

[0001] This utility model relates to the field of automotive air spring technology, and in particular to a normally open valve for a dual-chamber air spring. Background Technology

[0002] Under a specific air pressure condition, a single-chamber air spring exhibits only a single characteristic curve for its stiffness. However, by using a solenoid valve to connect and disconnect an additional air reservoir outside the main reservoir, the volume of the reservoir can vary under a given air pressure. When the solenoid valve opens, the total volume of the reservoir increases, leading to a decrease in pressure and a softening of the vehicle's suspension. Conversely, if the solenoid valve remains closed, the suspension can remain relatively stiff. Therefore, by adding a solenoid valve, the air spring exhibits a multi-stiffness characteristic curve.

[0003] Currently, spring-loaded solenoid valves suffer from a challenge in coordinating sealing pressure and NVH (Noise, Vibration, and Harshness). The existing valve design uses a cylindrical mating surface between the pushrod and the sealing ring, with a constant interference fit. This results in a uniform frictional force on the entire actuator, leading to high sealing friction. To counteract this friction, a large electromagnetic force is required. As is well known, static friction is much greater than dynamic friction. After overcoming static friction, the electromagnetic force becomes the primary force, resulting in a large overall force. This leads to increased actuator acceleration and unacceptable solenoid valve vibration. Therefore, it is necessary to optimize the existing solenoid valve structure to achieve NVH optimization while maintaining performance requirements. Summary of the Invention

[0004] The technical problem to be solved by this utility model is to provide a normally open valve for a double-chamber air spring. By setting the outer diameter of the tappet with different cross-sections, the frictional force on the entire mover is different, gradually increasing from opening to closing; at the same time, the variation of the overall force is minimized, thereby optimizing the overall NVH characteristics of the solenoid valve.

[0005] The technical solution adopted by this utility model to solve its technical problem is as follows: a normally open valve for a double-cavity air spring is provided, including a housing, the interior of which has an axially movable moving iron core and a coil assembly for controlling the movement of the moving iron core. A base is installed at one end of the housing, and a base is installed between the base and the coil assembly. A valve port is opened on the base, and an axially movable push rod is provided between the base and the base at the position corresponding to the valve port. The push rod includes a sleeve seat and a rod portion axially arranged at the top of the sleeve seat. The sleeve seat has a circular sleeve-shaped structure, and a first conical sidewall is provided in the middle of the sleeve seat. The outer diameter of the first conical sidewall gradually increases from the base towards the moving iron core in the axial direction. One end of the rod portion passes through the base and abuts against the moving iron core. An elastic element is provided between the sleeve seat and the base, and a first sealing ring is provided at the inner hole of the base to seal with the first conical sidewall.

[0006] As a supplement to the technical solution described in this utility model, the top of the sleeve seat is provided with multiple through holes around the rod, and several venting grooves are provided on the side walls around the rod.

[0007] As a supplement to the technical solution described in this utility model, a guide post is provided inside the base at the valve port, and the sleeve seat is sleeved on the guide post and slides back and forth along the guide post.

[0008] As a supplement to the technical solution described in this utility model, a step is arranged on the upper part of the guide post, and the elastic element is a spring, which is located inside the sleeve seat. The lower end of the spring is sleeved on the guide post and supported by the step.

[0009] As a supplement to the technical solution described in this utility model, a vertical guide bar is provided on one side of the guide post, and a guide groove that cooperates with the guide bar is provided on the inner wall of the sleeve seat.

[0010] As a supplement to the technical solution described in this utility model, the coil assembly includes enameled wire and a frame. The frame is installed inside the housing, and enameled wire is wound around the outside of the frame. A magnetic shielding tube is installed in the inner hole of the frame, and the moving iron core is axially movable inside the magnetic shielding tube.

[0011] As a supplement to the technical solution described in this utility model, a connector connected to the frame is installed at one axial end of the outer shell, and the connector has a terminal connected to the enameled wire inside.

[0012] As a supplement to the technical solution described in this utility model, a vibration damping pad for reducing noise is provided between the inside of the magnetic shielding tube and the end of the moving iron core.

[0013] As a supplement to the technical solution described in this utility model, a sliding bearing is provided between the base and the push rod, and a retaining ring and a stop block are respectively provided on both sides of the first sealing ring along the axial direction, with the retaining ring located between the sliding bearing and the first sealing ring.

[0014] As a supplement to the technical solution described in this utility model, the inner wall of the base located above the valve port is provided with a second conical sidewall, and the lower part of the sleeve seat is provided with a second sealing ring for forming a seal with the second conical sidewall, the vertical cross section of the second sealing ring being rectangular.

[0015] As a supplement to the technical solution described in this utility model, the upper sidewall of the sleeve seat is a first cylindrical surface, the outer diameter of which is the same as the maximum outer diameter of the first conical sidewall, and the lower sidewall of the sleeve seat is a second cylindrical surface, the outer diameter of which is the same as the maximum outer diameter of the first conical sidewall.

[0016] Beneficial effects: This utility model relates to a normally open valve for a double-chamber air spring, and designs a new push rod structure. During the closing process of the solenoid valve, the electromagnetic force increases exponentially with the decrease of the electromagnetic gap. By setting the outer diameter of different cross-sections of the push rod, the frictional force on the entire moving part is different, gradually increasing from opening to closing; at the same time, the variation of the overall force is minimized, thereby optimizing the overall NVH characteristics of the solenoid valve. This utility model balances the electromagnetic force by changing the frictional force in the closing stroke of the solenoid valve, thereby optimizing the overall force during the closing process and reducing vibration and noise. Attached Figure Description

[0017] Figure 1 This is a cross-sectional view of the utility model in its open state;

[0018] Figure 2 This is a cross-sectional view of the present invention in its closed state;

[0019] Figure 3 This is a schematic diagram of the structure of the pushrod described in this utility model;

[0020] Figure 4 This is a schematic diagram of the structure of the pushrod at different angles according to this utility model;

[0021] Figure 5 This is a structural schematic diagram of the base described in this utility model.

[0022] Diagram: 1. Push rod, 2. First seal, 3. Second seal ring, 4. Moving iron core, 5. Base, 6. Base, 7. Enamelled wire, 8. Sliding bearing, 9. Elastic element, 10. Shock-absorbing pad, 11. Housing, 12. Terminal, 13. Connector, 14. Frame, 15. Magnetic shielding tube, 16. Valve port, 17. Stop block, 18. Second conical sidewall, 19. Retaining ring, 20. Sleeve seat, 21. Rod, 22. First conical sidewall, 23. Through hole, 24. Guide post, 25. Guide groove, 26. Step, 27. Guide strip, 28. Side opening, 29. First cylindrical surface, 30. Exhaust groove, 31. Second cylindrical surface. Detailed Implementation

[0023] The present invention will be further illustrated below with reference to specific embodiments. It should be understood that these embodiments are for illustrative purposes only and are not intended to limit the scope of the present invention. Furthermore, it should be understood that after reading the teachings of this invention, those skilled in the art can make various alterations or modifications to the present invention, and these equivalent forms also fall within the scope defined by the appended claims.

[0024] The embodiments of this utility model relate to a normally open valve for a double-cavity air spring, such as... Figure 1-5As shown, the device includes a housing 11, inside which is a movable iron core 4 that moves axially and a coil assembly that controls the movement of the movable iron core 4. A base 6 is installed at one end of the housing 11, and a base 5 is installed between the base 6 and the coil assembly. A valve port 16 is provided on the base 6. A axially movable push rod 1 is provided between the base 6 and the base 5 at the position corresponding to the valve port 16. The push rod 1 includes a sleeve seat 20 and a rod portion 21 axially disposed at the top of the sleeve seat 20. The sleeve seat 20 has a circular sleeve-shaped structure. A first conical sidewall 22 is provided in the middle of the sleeve seat 20. The outer diameter of the first conical sidewall 22 gradually increases from the base 6 towards the movable iron core 4 in the axial direction. One end of the rod portion 21 passes through the base 5 and abuts against the movable iron core 4. An elastic element 9 is provided between the sleeve seat 20 and the base 6. A first sealing ring 2 is provided at the inner hole of the base 5 to seal against the first conical sidewall 22.

[0025] In this embodiment, the sealing at the valve port 16 is achieved by providing a second conical sidewall 18 on the inner sidewall of the base 6 located above the valve port 16, and a second sealing ring 3 for forming a seal with the second conical sidewall 18 is provided at the lower part of the sleeve seat 20. The vertical cross-section of the second sealing ring 3 is rectangular, and the second sealing ring 3 contacts and is pressed with the second conical sidewall 18 to form a seal.

[0026] The push rod 1, the moving iron core 4, and the coil assembly that controls the movement of the moving iron core 4 constitute the moving part structure of the solenoid valve.

[0027] To reduce the combined force, the mover needs to maintain a small difference between dynamic and static friction. Therefore, after overcoming static friction, dynamic friction also needs to increase, and it increases in a positive correlation with electromagnetic force. Thus, the push rod 1 in the mover of this invention is designed with a structure that changes in outer diameter. The maximum friction force of the push rod 1 during its movement is static friction. After overcoming static friction, the dynamic friction force is designed to gradually increase. Therefore, the push rod 1 needs to have a first conical sidewall 22 in the middle so that after movement, the friction force gradually increases with the increase of displacement, that is, the interference of the first sealing ring 2 gradually increases.

[0028] like Figure 1 As shown (solenoid valve is open), as Figure 2As shown (with the solenoid valve closed), the auxiliary sealing of the solenoid valve mainly relies on the interference fit between the auxiliary first sealing ring 2 and the circumferential surface of the push rod 1. When the solenoid valve is de-energized and open, the push rod 1 and the first sealing ring 2 form a static seal. At this time, a large interference fit is required to meet the sealing requirements, resulting in a large frictional force. After overcoming the static frictional force and entering the dynamic frictional force, the frictional force is greatly reduced. At the same time, the stroke between the base 5 and the moving iron core 4 is the electromagnetic gap. As the gap decreases, the electromagnetic force increases significantly. The combined force on the solenoid valve mover (moving iron core 4, push rod 1, and second sealing ring 3) increases, which leads to a deterioration in the NVH of the solenoid valve. That is, due to the large force difference between dynamic and static friction, the combined force is large, which increases the vibration of the solenoid valve.

[0029] This utility model includes key components such as Figure 3 and 4 The push rod 1 shown is a design; the push rod 1 includes a sleeve seat 20 and a rod portion 21. The sleeve seat 20 has a circular sleeve-shaped structure. The upper sidewall of the sleeve seat 20 is a first cylindrical surface 29, the outer diameter of which is the same as the maximum outer diameter of the first conical sidewall 22. The lower sidewall of the sleeve seat 20 is a second cylindrical surface 31, the outer diameter of which is the same as the maximum outer diameter of the first conical sidewall 22. The outer diameter of the first conical sidewall 22 gradually decreases from top to bottom. The first cylindrical surface 29, the first conical sidewall 22, and the second cylindrical surface 31 are designed to minimize the difference between dynamic and static friction. Figure 1 As shown, when the solenoid valve is in the open state, the first sealing ring 2 of the auxiliary seal contacts and engages with the first conical sidewall 22. The interference fit on the first conical sidewall 22 is small, meaning that the friction force on the push rod 1 is small. As the solenoid valve gradually closes to the open state... Figure 2 As the valve opens, the friction of the push rod 1 gradually increases until the first sealing ring 2 of the auxiliary seal contacts and engages with the first cylindrical surface 29. That is, during the entire opening process, due to the different outer diameter settings of the push rod 1, the friction of the entire moving part is different, gradually increasing from opening to closing. At the same time, the variation of the overall force is minimized, thereby optimizing the overall NVH characteristics of the solenoid valve.

[0030] As an explanation of the specific structure of the push rod 1, the top of the sleeve seat 20 is arranged with multiple through holes 23 around the rod 21, and several exhaust grooves 30 are opened on the side wall around the rod 21. The structure of the through holes 23 and the exhaust grooves 30 allows the internal space of the normally open valve to be connected with the outside, eliminating the air pressure difference, thereby avoiding the risk of the solenoid valve being pushed open due to excessive air pressure difference.

[0031] In this embodiment, a guide post 24 is provided inside the base 6 at the valve port 16. The sleeve seat 20 is sleeved on the guide post 24 and slides back and forth along the guide post 24. A vertical guide strip 27 is provided on one side of the guide post 24. A guide groove 25 that cooperates with the guide strip 27 is opened on the inner wall of the sleeve seat 20. Through the clearance fit between the inner hole of the sleeve seat 20 and the guide post 24, and the cooperation between the guide groove 25 and the guide strip 27, the sleeve seat 20 can move up and down smoothly and stably. The elastic element 9 is a spring. The upper end of the spring is located inside the sleeve seat 20. The upper end of the spring is limited by the inner hole of the sleeve seat 20. A step 26 is arranged on the upper part of the guide post 24. The lower end of the spring is sleeved on the guide post 24 and supported by the step 26. The upper end of the spring is supported by the upper surface of the step 26. At the same time, the lower end of the spring is limited by the guide post 24, so as to realize the overall limitation of the spring and ensure that the spring can extend and retract within the stroke range.

[0032] In this embodiment, the coil assembly includes enameled wire 7 and a bobbin 14. The bobbin 14 is installed inside the outer shell 11. The bobbin 5 is preferably made of high-strength nylon. The enameled wire 7 is wound around the outside of the bobbin 14. A magnetic shielding tube 15 is installed in the inner hole of the bobbin 14. The moving iron core 4 is axially movably disposed inside the magnetic shielding tube 15. A connector 13 connected to the bobbin 14 is installed at one axial end of the outer shell 11. The connector 13 has a terminal 12 connected to the enameled wire 7 inside.

[0033] In this embodiment, a noise-reducing damping pad 10 is provided between the inside of the magnetic shielding tube 15 and the end of the moving iron core 4. The damping pad 10 is fixed to the top of the magnetic shielding tube 15. The fixing method between the two can be embedded installation, snap-fit, etc. The damping pad 10 can slow down the moving iron core 4 and effectively reduce noise.

[0034] In this embodiment, in order to ensure smooth sliding between the base 5 and the push rod 1, a sliding bearing 8 is provided between the base 5 and the push rod 1 to assist sliding; a retaining ring 19 and a stop block 17 are respectively provided on both axial sides of the first sealing ring 2, and the retaining ring 19 is located between the sliding bearing 8 and the first sealing ring 2.

[0035] Working principle: When the solenoid valve is energized, the moving iron core 4 is subjected to electromagnetic force, overcoming the resistance of the elastic element 9, and pushing the push rod 1 downward until the second sealing ring 3 presses against the valve port 16 of the base 6. At this time, the solenoid valve is closed, and the valve port 16 at the bottom of the base 6 is not connected to the side port 28 on the side of the base 6. When the solenoid valve is de-energized, the electromagnetic force on the moving iron core 4 disappears, and the elastic element 9 pushes the push rod 1 and the moving iron core 4 upward until the shock-absorbing pad 10 touches the top of the magnetic shielding tube 15. At this time, the second sealing ring 3 separates from the valve port 16 of the base 6, the solenoid valve opens, and the valve port 16 at the bottom of the base 6 is connected to the side port 28 on the side of the base 6.

[0036] In the description of this utility model, it should be understood that the directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this utility model. The directional terms "inner" and "outer" refer to the inner and outer contours of each component itself.

[0037] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0038] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this utility model.

[0039] The above provides a detailed description of a normally open valve for a double-chamber air spring provided in this application. Specific examples have been used to illustrate the principle and implementation of this application. The description of the above embodiments is only for the purpose of helping to understand the method and core idea of ​​this application. At the same time, for those skilled in the art, there will be changes in the specific implementation and application scope based on the idea of ​​this application. Therefore, the content of this specification should not be construed as a limitation of this application.

Claims

1. A normally open valve for a double-cavity air spring, comprising a housing (11), wherein the housing (11) has an axially movable moving iron core (4) and a coil assembly for controlling the movement of the moving iron core (4) inside, a base (6) is mounted on one end of the housing (11), a base (5) is mounted between the base (6) and the coil assembly, and a valve port (16) is provided on the base (6), characterized in that: A axially movable push rod (1) is provided between the base (6) and the base (5) at the position corresponding to the valve port (16). The push rod (1) includes a sleeve seat (20) and a rod part (21) axially arranged on the top of the sleeve seat (20). The sleeve seat (20) has a circular sleeve structure. A first conical sidewall (22) is provided in the middle of the sleeve seat (20). The outer diameter of the first conical sidewall (22) gradually increases from the base (6) towards the moving iron core (4) in the axial direction. One end of the rod part (21) passes through the base (5) and abuts against the moving iron core (4). An elastic element (9) is provided between the sleeve seat (20) and the base (6). A first sealing ring (2) is provided in the inner hole of the base (5) to seal with the first conical sidewall (22).

2. The normally open valve for a double-chamber air spring according to claim 1, characterized in that: The top of the sleeve seat (20) is provided with multiple through holes (23) around the rod (21), and several venting grooves (30) are provided on the side walls around the rod (21).

3. The normally open valve for a double-chamber air spring according to claim 1, characterized in that: The base (6) has a guide post (24) located inside the valve port (16), and the sleeve seat (20) is sleeved on the guide post (24) and slides back and forth along the guide post (24).

4. A normally open valve for a double-chamber air spring according to claim 3, characterized in that: The guide post (24) has a ring of steps (26) arranged on its upper part. The elastic element (9) is a spring, which is located inside the sleeve seat (20). The lower end of the spring is sleeved on the guide post (24) and supported by the steps (26).

5. A normally open valve for a double-chamber air spring according to claim 3, characterized in that: A vertical guide bar (27) is provided on one side of the guide post (24), and a guide groove (25) that cooperates with the guide bar (27) is provided on the inner wall of the sleeve seat (20).

6. A normally open valve for a double-chamber air spring according to claim 1, characterized in that: The coil assembly includes enameled wire (7) and a bobbin (14). The bobbin (14) is installed inside the outer shell (11). The enameled wire (7) is wound around the outside of the bobbin (14). A magnetic shielding tube (15) is installed in the inner hole of the bobbin (14). The moving iron core (4) is axially movable inside the magnetic shielding tube (15).

7. A normally open valve for a double-chamber air spring according to claim 6, characterized in that: A noise-reducing damping pad (10) is provided between the inside of the magnetic shielding tube (15) and the end of the moving iron core (4).

8. A normally open valve for a double-chamber air spring according to claim 1, characterized in that: A sliding bearing (8) is provided between the base (5) and the push rod (1). A retaining ring (19) and a stop block (17) are respectively provided on both sides of the first sealing ring (2). The retaining ring (19) is located between the sliding bearing (8) and the first sealing ring (2).

9. A normally open valve for a double-chamber air spring according to claim 1, characterized in that: The inner wall of the base (6) located above the valve port (16) is provided with a second conical sidewall (18), and the lower part of the sleeve seat (20) is provided with a second sealing ring (3) for forming a seal with the second conical sidewall (18). The vertical cross section of the second sealing ring (3) is rectangular.

10. A normally open valve for a double-chamber air spring according to claim 1, characterized in that: The upper sidewall of the sleeve seat (20) is a first cylindrical surface (29), the outer diameter of which is the same as the maximum outer diameter of the first conical sidewall (22). The lower sidewall of the sleeve seat (20) is a second cylindrical surface (31), the outer diameter of which is the same as the maximum outer diameter of the first conical sidewall (22).

Images