End face sealing valve port structure and normally-open electromagnetic valve for double-cavity air spring

Abstract

The utility model discloses an end face sealing valve port structure and a normally open solenoid valve for a double-cavity air spring, which comprise a base and a base arranged on the upper side of the base, a tappet capable of moving up and down is arranged between the base and the base, a valve port is arranged in the middle of the lower side of the base, and a side port is arranged on the side portion of the base. A main sealing piece is installed on the upper side of the bottom of the base around the valve port, communication between the valve port and the side port is cut off when the lower end of the tappet makes contact with the main sealing piece, and a multi-lip sealing ring is installed between the radial outer side of the tappet and the base. The outer side of the lower end of the tappet is provided with a circle of side pressing step portion with the diameter larger than that of the outer side wall of the tappet. According to the electromagnetic valve, the friction force in the closing stroke of the electromagnetic valve can be reduced, the comprehensive force in the closing process is optimized, and vibration and noise are reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of automobiles, in particular to an end face sealing valve port structure and a normally open electromagnetic valve for a double-cavity empty spring. Background Art

[0002] Under certain air pressure conditions, the stiffness of a single air spring chamber has only a single characteristic curve. For example, a solenoid valve could be used to connect and disconnect an additional air chamber in addition to the main air chamber, allowing the volume of the air chamber to be variable under certain air pressure conditions. In this case, as the solenoid valve opens, the total volume of the air chamber increases, reducing the pressure within the chamber and naturally softening the vehicle's suspension. However, as long as the solenoid valve is closed, the vehicle's suspension can remain relatively stiff. Therefore, adding a solenoid valve allows the air spring to exhibit multiple stiffness characteristic curves. However, the air spring stiffness solenoid valve produces considerable noise and vibration when opening and closing, creating a difficult balance between sealing pressure and NVH performance. Furthermore, the electromagnetic force required to maintain the normally open solenoid valve in the closed state is relatively large, generating significant vibration when the valve port opens and closes. Therefore, improvements to the sealing valve port structure of existing solenoid valves are needed to address this technical issue. Utility Model Content

[0003] The utility model provides an end-face sealing valve port structure and a normally open solenoid valve for a double-cavity empty spring, which can reduce friction in the closing stroke of the solenoid valve, optimize the comprehensive force in the closing process, and reduce vibration and noise.

[0004] To achieve the above-mentioned purpose, in the first aspect, the utility model provides the following technical solutions: an end face sealing valve port structure, comprising a base and a pedestal arranged on the upper side of the base, a push rod movable up and down is arranged between the base and the base, a valve port is arranged in the middle of the lower side of the base, and a side port is arranged on the side of the base, characterized in that a main seal is installed around the valve port on the upper bottom side of the base, the communication between the valve port and the side port is cut off when the lower end of the push rod contacts the main seal, a multi-lip sealing ring is installed between the radial outer side of the push rod and the base, and a side pressure step portion with a diameter larger than the diameter of the outer wall of the push rod is provided on the outer side of the lower end of the push rod. Using a flat main seal as the main seal can achieve reliable line sealing. To ensure the seal, a certain electromagnetic force needs to be maintained at all times when the solenoid valve is closed. After closing, the side pressure step can form a pressure difference from the side port air pressure through the step surface on the upper side of the side pressure step, so that the push rod can withstand a larger lateral pressure. The lateral pressure can reduce the electromagnetic force applied to maintain the seal when the solenoid valve is closed, and reduce the vibration when the valve port is opened and closed. At the same time, the multi-lip sealing ring can be used as an auxiliary seal to reduce the friction between the push rod and the base, and reduce the excessive acceleration generated by the push rod after overcoming the static friction, which increases the vibration and noise of the solenoid valve.

[0005] Preferably, the lower end face of the push rod is provided with a circle of pointed flanges, which are in contact with the main seal. The pointed flanges can achieve a valve port area close to the sealing line, thereby improving the sealing effect and reducing the noise of opening and closing the valve port.

[0006] Preferably, the main seal is a rubber seal vulcanized and molded integrally with the base, and a rib is provided on the lower side of the main seal for coupling with the base, which can improve the coupling strength between the main seal and the base.

[0007] Preferably, the cross-section of the multi-lip sealing ring is X-shaped, and a pair of sealing outer lips are provided on the radial outer side of the multi-lip sealing ring, and a pair of sealing inner lips are provided on the radial inner side of the multi-lip sealing ring. By providing the sealing inner lips and the sealing outer lips, the friction between the multi-lip sealing ring and the push rod can be reduced, and the influence of the friction on other forces can be minimized to the greatest extent. Even if the other forces are more controllable, the influence of NVH of the solenoid valve can be more effectively reduced.

[0008] Preferably, the outside of the multi-lip sealing ring is filled with lubricating grease between the two sealing outer lips and / or between the two sealing inner lips, effectively utilizing the structure of the multi-lip sealing ring to fill the lubricating grease. By filling the lubricating grease, the dynamic friction and static friction between the multi-lip sealing ring and the push rod can be further reduced.

[0009] Preferably, a limit ring connected to the base is provided on the lower side of the multi-lip sealing ring, and the limit ring can be used to limit the axial position of the multi-lip sealing ring and also to limit the leakage of lubricating grease.

[0010] Preferably, the push rod includes a tube sleeve base and a push rod portion axially arranged on the top of the tube sleeve base. The top of the tube sleeve base is provided with a plurality of through holes. The push rod portion can guide the movement of the push rod. The through holes allow the gas at the valve port to enter the inner cavity of the solenoid valve on the upper side of the push rod, thereby achieving the up and down balance of the push rod and reducing the resistance of the push rod to the up and down movement.

[0011] Preferably, a sliding bearing is installed between the outer side of the push rod and the base, which can guide the up and down movement of the sliding bearing, reduce friction, noise and electromagnetic force.

[0012] Preferably, a guide seat extending into the interior of the tube sleeve base is provided in the middle of the base, a reset spring is installed between the upper side of the guide seat and the top of the tube sleeve base, a guide ridge is provided on the outer side of the guide seat along the axial direction, and a guide groove matching the guide ridge is provided on the inner side wall of the tube sleeve base. The guide seat can limit the reset spring, and the guide ridge can match the guide groove to prevent the push rod from deflecting when moving, thereby increasing friction and noise.

[0013] In the second aspect, the present application also includes a normally open solenoid valve for a double-cavity empty spring, including the end face sealing valve port structure described in the first aspect, the normally open solenoid valve also includes an outer shell, a skeleton is installed inside the outer shell, the outer side of the skeleton is wound with enameled wire, the middle inner hole of the skeleton is installed with a magnetic isolation tube, the interior of the magnetic isolation tube is provided with an axially movable moving iron core, the upper end of the outer shell is provided with an electrical interface connected to the skeleton, the upper end of the push rod passes through the base and is against the moving iron core, a buffer is provided between the upper end of the moving iron core and the top of the magnetic isolation tube, and through a compact design, it can be installed between the main cavity and the auxiliary cavity of the double-cavity empty spring to flexibly adjust the stiffness of the double-cavity empty spring.

[0014] Compared with the prior art, the beneficial effects of the present invention are:

[0015] The end face sealing structure is adopted to ensure that the solenoid valve has excellent NVH performance from opening to closing, and only a small electromagnetic force is required; after closing, the sealing between the chambers of the solenoid valve is better, and the structure itself can withstand the large unidirectional air pressure of the main and sub-chambers; the auxiliary seal of the solenoid valve adopts a new structure of multi-lip sealing ring, which can reduce the friction between the tappet and the base, and reduce the excessive acceleration generated after the tappet overcomes the static friction, which increases the vibration and noise of the solenoid valve, so as to optimize the comprehensive force during the closing process and reduce vibration and noise. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 This is a front cross-sectional view of the solenoid valve of the present invention in an open state;

[0017] Figure 2 This is a front cross-sectional view of the solenoid valve of the utility model in a closed state;

[0018] Figure 3 For this utility model Figure 2 A magnified structural diagram;

[0019] Figure 4 This is a cross-sectional structural diagram of the multi-lip sealing ring of the utility model;

[0020] Figure 5 This is a three-dimensional structural diagram of the tappet of the present invention from a first perspective;

[0021] Figure 6 This is a perspective structural diagram of the tappet of the present invention from a second perspective;

[0022] Figure 7 It is a three-dimensional structural diagram of the base of the utility model.

[0023] Reference numerals:

[0024] 1. Base, 11. Sliding bearing, 12. Multi-lip sealing ring, 13. Limiting ring, 14. Buffer, 15. Housing, 16. Skeleton, 17. Magnetic isolation tube, 2. Moving iron core, 3. Electrical interface, 4. Enameled wire, 5. Push rod, 50. Sleeve base, 51. Pointed flange, 52. Push rod part, 53. Side pressure step part, 54. Through hole, 55. Guide groove, 6. Base, 61. Guide seat, 62. Guide rib, 7. Side port, 8. Valve port, 9. Main seal, 91. Raised rib, 10. Return spring, 121. Sealing outer lip, 122. Sealing inner lip, 123. Outer sealing chamber, 124. Inner sealing chamber, 125. Upper sealing chamber, 126. Lower sealing chamber. DETAILED DESCRIPTION

[0025] The technical solutions in the embodiments of the present invention will be described clearly and completely below with reference to the accompanying drawings in the embodiments of the present invention.

[0026] In the prior art, the valve port structure of a dual-chamber air spring involves two seals. One of the seals is the primary seal, which uses the tappet 5 to seal the valve port. The other seal is the auxiliary seal, located between the outer side of the tappet 5 and the base 1. When the solenoid valve is closed, the auxiliary seal has the same pressure differential as the primary seal. To ensure the sealing, the sealing ring in this sealing area needs to have a certain interference fit with the tappet of the actuator. Due to the high sealing pressure, the conventional O-ring design will cause a large sealing friction. To offset 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 plays a major role, resulting in a large combined force. This causes the acceleration of the tappet 5 to increase, the vibration of the solenoid valve to increase, and the noise to be relatively loud.

[0027] like Figure 1-7As shown, in order to solve the above problems, the following technical solutions are provided: an end face sealing valve port structure, comprising a base 6 and a base 1 arranged on the upper side of the base 6, a push rod 5 that can move up and down is arranged between the base 1 and the base 6, a valve port 8 is arranged in the middle of the lower side of the base 6, a side port 7 is arranged on the side of the base 6, a main seal 9 is installed around the valve port 8 on the upper side of the bottom of the base 6, the communication between the valve port 8 and the side port 7 is cut off when the lower end of the push rod 5 contacts the main seal 9, a multi-lip sealing ring 12 is installed between the radial outer side of the push rod 5 and the base 1, and a circle of side pressure step portion 53 with a diameter larger than the diameter of the outer wall of the push rod 5 is provided on the outer side of the lower end of the push rod 5 , using a planar main seal 9 as the main seal can achieve reliable line sealing. To ensure sealing, a certain electromagnetic force needs to be maintained at all times when the solenoid valve is closed. The side pressure step 53 can form a pressure difference from the air pressure of the side port 7 through the step surface on the upper side of the side pressure step 53 after closing, so that the push rod can withstand a larger lateral pressure. With the lateral pressure, the electromagnetic force applied to maintain the seal when the solenoid valve is closed can be reduced, and the vibration when the valve port is opened and closed can be reduced. At the same time, the multi-lip sealing ring 12 can be used as an auxiliary seal to reduce the friction between the push rod 5 and the base 1, and reduce the excessive acceleration generated by the push rod 5 after overcoming the static friction, which increases the vibration and noise of the solenoid valve.

[0028] Specifically, when the solenoid valve is closed, air pressure from the side port 7 acts on the upper surface of the side pressure step 53, creating a vertical pressure differential. This force, combined with the electromagnetic force, compresses the tappet 5 against the main seal 9. This air pressure-assisted sealing reduces the electromagnetic force required to maintain the seal by 30%-50%. The step diameter difference is designed to be 0.5-1.2mm, and the step surface inclination angle is 15°-30°. Fluid dynamics simulations have shown that this angle evenly distributes lateral pressure.

[0029] In this embodiment, the lower end surface of the tappet 5 is provided with a ring of pointed flanges 51. This flange 51 contacts the main seal 9 and allows the valve port area to be close to the sealing line, improving the sealing effect and reducing the noise during valve opening and closing. The flange 51 can be a flange with a relatively small radius. The pointed flange 51 generates localized high pressure (contact pressure ≥ 2 MPa) through a very small contact area, cutting off the gas flow between the valve port 8 and the side port 7. This reduces the impact noise at the moment of closing by 10 dB(A). Due to the small contact area, energy absorption is faster.

[0030] In this embodiment, the main seal 9 is a rubber seal vulcanized and molded integrally with the base 6. The lower side of the main seal 9 is provided with a rib 91 combined with the base 6, which can improve the bonding strength between the main seal 9 and the base 6.

[0031] Preferably, the multi-lip seal ring 12 has an X-shaped cross-section. A pair of outer sealing lips 121 are provided radially outwardly of the multi-lip seal ring 12, and a pair of inner sealing lips 122 are provided radially inwardly of the multi-lip seal ring 12. The provision of the inner and outer sealing lips 122 and 121 reduces friction between the multi-lip seal ring 12 and the tappet 5, minimizing the impact of friction on other forces. This makes other forces more controllable and effectively reduces the NVH impact of the solenoid valve. The inner sealing lips 122 are thin-walled, with a thickness of 0.3-0.5 mm. The contact surface with the tappet 5 is linear, resulting in a contact pressure of ≤0.8 MPa, 50% lower than that of conventional O-rings. The multi-lip seal ring 12 can be made of fluororubber (FKM) with a hardness of 60±5 Shore A. The lip edges are mirror-polished to a roughness Ra of ≤0.4 μm. Silicone grease is used as the lubricant, filling 80% of the cavity volume.

[0032] Among them, the sealing inner lip 122 is in contact with the push rod 5, and an inner sealing cavity 124 is formed between the two sealing inner lips 122; the sealing outer lip 121 is in contact with the base 1, and an outer sealing cavity 123 is formed between the two sealing outer lips 121; at the same time, an upper sealing cavity 125 is provided between the upper sealing outer lip 121 and the sealing inner lip 122, and a lower sealing cavity 126 is provided between the lower sealing outer lip 121 and the sealing inner lip 122. The above four sealing cavities provide the sealing outer lip 121 and the sealing inner lip 122 with sufficient deformation space; the thin-walled sealing outer lip 121 and the sealing inner lip 122 can withstand greater gas pressure in both upper and lower directions, and the friction between them and the push rod 5 is relatively small.

[0033] In this embodiment, the outside of the multi-lip sealing ring 12 is filled with lubricating grease between the two sealing outer lips 121 and / or between the two sealing inner lips 122, and the structure of the multi-lip sealing ring 12 is effectively utilized to fill the lubricating grease. By filling the lubricating grease, the dynamic friction and static friction between the multi-lip sealing ring 12 and the push rod 5 can be further reduced. Due to the effect of the lubricating grease, the dynamic friction coefficient is reduced from 0.3 to below 0.1, and the difference between static friction and dynamic friction is reduced to within 10%.

[0034] In this embodiment, a limit ring 13 connected to the base 1 is provided on the lower side of the multi-lip seal ring 12. The limit ring 13 can limit the axial position of the multi-lip seal ring 12 and also limit the leakage of lubricating grease.

[0035] In this embodiment, the push rod 5 includes a tube sleeve base 50 and a push rod portion 52 axially arranged on the top of the tube sleeve base 50. The top of the tube sleeve base 50 is provided with multiple through holes 54. The push rod portion 52 can guide the movement of the push rod 5. The through holes 54 allow the gas at the valve port 8 to enter the inner cavity of the solenoid valve on the upper side of the push rod 5, thereby achieving the up and down balance of the push rod 5 and reducing the resistance to the up and down movement of the push rod 5.

[0036] In this embodiment, a sliding bearing 11 is installed between the outer side of the tappet 5 and the base 1. This guides the vertical movement of the sliding bearing 11, reducing friction, noise, and electromagnetic forces. The sliding bearing 11 is made of a bronze-based self-lubricating material (containing 20% graphite) with a surface porosity of 15%-20%, which stores lubricating oil. The sliding bearing 11 is interference-fitted into the inner bore of the base 1, with a clearance of 0.02-0.04 mm between the inner bore and the tappet, providing boundary lubrication.

[0037] In this embodiment, a guide seat 61 extending into the interior of the tube sleeve base 50 is provided in the middle of the base 6, and a reset spring 10 is installed between the upper side of the guide seat 61 and the top of the tube sleeve base 50. A guide ridge 62 is provided on the outer side of the guide seat 61 along the axial direction, and a guide groove 55 matching the guide ridge 62 is provided on the inner side wall of the tube sleeve base 50. The guide seat 61 can limit the reset spring 10, and the guide ridge 62 can match the guide groove 55 to prevent the push rod 5 from deflecting when moving, thereby increasing friction and noise.

[0038] On the second aspect, the present application also includes a normally open solenoid valve for a double-cavity empty spring, including the end face sealing valve port structure described in the first aspect, the normally open solenoid valve also includes an outer shell 15, a skeleton 16 is installed inside the outer shell 15, and an enameled wire 4 is wound around the outer side of the skeleton 16, a magnetic isolation tube 17 is installed in the middle inner hole of the skeleton 16, and an axially movable moving iron core 2 is provided inside the magnetic isolation tube 17, the upper end of the outer shell 15 is installed with an electrical interface 3 connected to the skeleton 16, the upper end of the push rod 5 passes through the base 1 and is against the moving iron core 2, and a buffer part 14 is provided between the upper end of the moving iron core 2 and the top of the magnetic isolation tube 17. Through the compact design, it can be installed between the main cavity and the auxiliary cavity of the double-cavity empty spring, and the stiffness of the double-cavity empty spring can be flexibly adjusted. When the enameled wire 4 is energized, the moving iron core 2 can be moved downward, pushing the push rod 5 to press down and close the valve port 8.

[0039] In the normally open solenoid valve, the inner cavity on the upper side of the push rod 5 and the inner cavities at the upper and lower ends of the moving iron core 2 are connected, and can be collectively referred to as the valve inner cavity; the inner cavity of the push rod 5 is connected to the valve port 8, collectively referred to as the air intake chamber, and the air intake chamber is connected to the main chamber of the air spring; the side port 7 is located in the side cavity of the solenoid valve, and the side cavity is connected to the sub-cavity of the air spring; when the solenoid valve is energized and open, the valve inner cavity, the air intake chamber and the side cavity are connected to each other, and the end face sealing structure can achieve maximum gas circulation and a larger flow rate; after the solenoid valve is closed, the valve inner cavity is connected to the air intake chamber, and the auxiliary sealing line of the aforementioned multi-lip sealing ring 12 has the same outer diameter as the main sealing line of the valve port of the push rod 5, and the gas pressure balance can be maintained without additional electromagnetic force, reducing the electromagnetic force and power consumption; and after closing, it can be opened by the spring force of the smaller reset spring 10; the side cavity is not connected to the valve inner cavity, and the setting of the aforementioned push rod step surface can achieve effective sealing of the side port with a larger pressure.

[0040] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative position relationship, movement status, etc. between the various components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.

[0041] In addition, the terms "first," "second," and so on, used in this utility model are for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, features specified as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of this utility model, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0042] In this utility model, unless otherwise specified or limited, the terms "connection" and "fixation" should be understood in a broad sense. For example, "fixation" can mean fixed connection, detachable connection, or integration; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; internal communication between two elements or interaction between two elements, unless otherwise specified. For those skilled in the art, the specific meanings of the above terms in this utility model can be understood according to specific circumstances.

[0043] In addition, the technical solutions between the various embodiments of the present invention can be combined with each other, but it must be based on the fact that ordinary technicians in this field can implement it. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by this utility model.

Claims

1. An end face sealing valve port structure, comprising a base (6) and a base (1) arranged on the upper side of the base (6), a tappet (5) movable up and down is arranged between the base (1) and the base (6), a valve port (8) is arranged in the middle of the lower side of the base (6), and a side port (7) is arranged on the side of the base (6), characterized in that: A main seal (9) is installed on the upper side of the bottom of the base (6) around the valve port (8). When the lower end of the push rod (5) contacts the main seal (9), the communication between the valve port (8) and the side port (7) is cut off. A multi-lip seal ring (12) is installed between the radial outer side of the push rod (5) and the base (1). A circle of side pressure step portion (53) with a diameter larger than the diameter of the outer wall of the push rod (5) is provided on the outer side of the lower end of the push rod (5).

2. The end face sealing valve port structure according to claim 1, characterized in that: The lower end surface of the tappet (5) is provided with a circle of pointed flanges (51), and the pointed flanges (51) are in contact with the main sealing member (9).

3. The end face sealing valve port structure according to claim 2, characterized in that: The main seal (9) is a rubber seal formed integrally with the base (6) by vulcanization, and a convex rib (91) is provided on the lower side of the main seal (9) and is combined with the base (6).

4. The end face sealing valve port structure according to claim 1, characterized in that: The cross section of the multi-lip sealing ring (12) is X-shaped, a pair of sealing outer lips (121) are provided on the radial outer side of the multi-lip sealing ring (12), and a pair of sealing inner lips (122) are provided on the radial inner side of the multi-lip sealing ring (12).

5. The end face sealing valve port structure according to claim 4, characterized in that: The exterior of the multi-lip sealing ring (12) is filled with lubricating grease between the two sealing outer lips (121) and / or between the two sealing inner lips (122).

6. The end face sealing valve port structure according to claim 4, characterized in that: A limit ring (13) connected to the base (1) is provided on the lower side of the multi-lip sealing ring (12).

7. The end face sealing valve port structure according to claim 1, characterized in that: The push rod (5) comprises a pipe sleeve base (50) and a push rod portion (52) axially arranged on the top of the pipe sleeve base (50), and a plurality of through holes (54) are arranged on the top of the pipe sleeve base (50).

8. The end face sealing valve port structure according to claim 7, characterized in that: A sliding bearing (11) is also installed between the outer side of the tappet (5) and the base (1).

9. The end face sealing valve port structure according to claim 7, characterized in that: A guide seat (61) extending into the interior of the tube sleeve base (50) is provided in the middle of the base (6), a return spring (10) is installed between the upper side of the guide seat (61) and the top of the tube sleeve base (50), a guide ridge (62) is provided on the outer side of the guide seat (61) along the axial direction, and a guide groove (55) matching the guide ridge (62) is provided on the inner side wall of the tube sleeve base (50).

10. A normally open solenoid valve for a double-chamber empty spring, comprising the end face sealing valve port structure according to any one of claims 1 to 9, characterized in that: The normally open solenoid valve further comprises a shell (15), a frame (16) is installed inside the shell (15), an enameled wire (4) is wound around the outside of the frame (16), a magnetic isolation tube (17) is installed in the middle inner hole of the frame (16), an axially movable moving iron core (2) is provided inside the magnetic isolation tube (17), an electrical interface (3) connected to the frame (16) is installed at the upper end of the shell (15), the upper end of the push rod (5) passes through the base (1) and abuts against the moving iron core (2), and a buffer (14) is provided between the upper end of the moving iron core (2) and the top of the magnetic isolation tube (17).

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