A cylindrical spring seat structure for an electromagnetic valve

Abstract

This utility model belongs to the field of automotive hydraulic control technology, and in particular to a cylindrical spring seat structure for a solenoid valve. It includes a magnetic core shaft and a return spring, which is sleeved on the surface of the magnetic core shaft. A boss is integrally formed at the end of the magnetic core shaft, forming a cylindrical spring seat that supports the return spring. A positioning protrusion is provided on the end face of the boss, which limits the radial displacement of the return spring. A first sealing ring and a second sealing ring are sleeved on the surface of the magnetic core shaft. This cylindrical spring seat structure for a solenoid valve completely eliminates spring misalignment: the cylindrical boss forms a large-area surface contact with the spring end ring, providing stable radial support. Combined with the physical limitation of the central positioning protrusion, it structurally prevents radial misalignment of the spring, ensuring coaxiality between the spring and the magnetic core shaft, eliminating frictional fluctuations caused by misalignment, and ensuring high consistency in key performance parameters such as the solenoid valve's pull-in and release forces and response time, thereby improving product quality and operational reliability.

Description

Technical Field

[0001] This utility model belongs to the field of automotive hydraulic control technology, specifically relating to a cylindrical spring seat structure for a solenoid valve. Background Technology

[0002] In automotive transmission hydraulic systems, solenoid valves are core components for hydraulic control, and their reliability directly affects the transmission's shifting performance and overall operational stability. Currently, the cylindrical spring seat of the solenoid valve typically uses a structure where a precision locking steel ball is fixed to the rear yoke sleeve via interference fitting. While this structure provides initial spring fixation, it suffers from several technical drawbacks: 1. Complex process and high manufacturing cost: Additional purchase of precision locking steel ball standard parts is required, increasing material costs; high-precision blind holes need to be machined at the end of the valve core rod to control the interference fit, with strict tolerance requirements, making machining difficult and costly; special riveting equipment and high-precision tooling are required during assembly to ensure the pressing quality, and the riveting pressure is difficult to control. Too little pressure can easily cause the locking steel ball to loosen, while too much pressure may damage parts or the rod body. Strict process control and quality inspection are required, which prolongs the production cycle and increases management costs.

[0003] II. Poor Reliability and Consistency: The quality of interference fit is affected by many factors such as material properties, machining accuracy, and riveting pressure, resulting in significant dispersion. Some products may have problems such as insufficient preload (loosening) or stress concentration (creating crack sources), leading to a low product yield. Moreover, the structural instability can easily affect the reliability of the solenoid valve during long-term use. At the same time, the locking steel ball and the spring are in spherical contact, and the spring is prone to deflection around the fulcrum, causing fluctuations in key performance parameters such as the solenoid valve's pull-in and release force and response time, affecting the consistency of product performance.

[0004] Third, limited service life: uneven loading of the spring will cause uneven force distribution, resulting in bending stress and abnormal wear. This not only shortens the service life of the spring itself, but may also increase the risk of valve core jamming, thereby affecting the overall service life of the solenoid valve. It cannot meet the requirements of new energy vehicles for long service life and high stability of the transmission hydraulic system.

[0005] To address the aforementioned issues, this application proposes a cylindrical spring seat structure for a solenoid valve. Utility Model Content

[0006] To address the aforementioned problems in the existing technology, this utility model provides a cylindrical spring seat structure for an electromagnetic valve, which has the characteristic of eliminating frictional fluctuations caused by off-center loading.

[0007] To achieve the above objectives, this utility model provides the following technical solution: a cylindrical spring seat structure for an electromagnetic valve, including a magnetic core shaft, and further comprising: A return spring is sleeved on the surface of a magnetic core shaft. A boss is integrally formed at the end of the magnetic core shaft. The boss forms a cylindrical spring seat that supports the return spring. A steel ball is provided on one side of the cylindrical spring seat. The end face of the boss is provided with a positioning protrusion, which is used to limit the radial displacement of the return spring; The surface of each magnetic core shaft is fitted with a first sealing ring and a second sealing ring.

[0008] Preferably, the boss is cylindrical, and the positioning protrusion is located at the center of the boss's end face. This further clarifies that the boss is cylindrical and the positioning protrusion is located at the center of the boss's end face. This makes the structure of the cylindrical spring seat more specific and defined, which helps to improve the stability and accuracy of the return spring installation, ensures that the return spring can extend and retract along the central axis during operation, avoids tilting or offset, and thus better performs the function of the return spring.

[0009] Preferably, the positioning protrusion is any one of a cylindrical, frustum-shaped, or conical shape. The shape of the positioning protrusion is specifically defined, with three possible shapes listed: cylindrical, frustum-shaped, or conical. These shapes of positioning protrusions can effectively limit the radial displacement of the return spring. Furthermore, different shapes may be suitable for different working scenarios and design requirements, providing more options for the design and manufacture of cylindrical spring seats, increasing the adaptability and practicality of the patent.

[0010] Preferably, the outer diameter of the positioning protrusion is adapted to the inner diameter of the end coil of the return spring, thus clarifying the adaptation relationship between the outer diameter of the positioning protrusion and the inner diameter of the end coil of the return spring. This ensures that the positioning protrusion can be accurately inserted into the end coil of the return spring, thereby better limiting the radial displacement of the return spring, preventing the return spring from shaking or disengaging during operation, and improving the fitting accuracy and stability between the cylindrical spring seat and the return spring.

[0011] An electromagnetic valve includes an electromagnetic component and a hydraulic component, wherein the electromagnetic component and the hydraulic component are connected by a flange feature protruding from the end of an electrode shoe component and bent to close.

[0012] Preferably, the electromagnetic assembly includes a magnetic housing, a rear yoke sleeve, a first bearing component, a second bearing component, a magnetic core, a solenoid assembly, a protective cover end, a pole shoe assembly end, a first pole shoe, a second pole shoe, a first PIN pin, a second PIN pin, an injection-molded gasket, a PIN pin protective cover, and a dust cover. The magnetic housing is composed of a valve housing assembly formed by metal stamping. The magnetic core is riveted to a magnetic core shaft. The solenoid assembly is made of a nylon skeleton wound with copper wire. The pole shoe assembly is formed by a metal-processed pole shoe and a secondary injection-molded part. The first and second PIN pins are made of copper and formed by stamping. The first and second PIN pins are joined to the solenoid by riveting and welding.

[0013] Preferably, the hydraulic assembly includes a valve sleeve assembly, a sealing ring assembly, a locking steel ball, a valve core, a valve core support seat, and a valve sleeve support seat. The valve sleeve assembly is formed by injection molding a valve sleeve filter screen and a valve sleeve through interference riveting. The valve core support seat controls pressure and flow by riveting with the valve core at a fixed height. The valve sleeve support seat is assembled with the end of the pole shoe assembly by interference riveting.

[0014] Preferably, the valve sleeve assembly has an axial oil inlet chamber, a first radial control oil chamber, a second radial control oil chamber, and a radial oil discharge chamber. The medium oil is pressurized by the gearbox oil supply system. When energized, the medium oil enters from the inlet chamber; when de-energized, excess medium oil is discharged from the radial oil discharge chamber. This further clarifies the internal oil chamber structure of the valve sleeve assembly and the flow path of the medium oil. By defining these structures and flow paths, the working principle of the hydraulic assembly is made clearer, enabling accurate control of the inlet, outlet, and flow of the medium oil, realizing the hydraulic control function of the solenoid valve, and ensuring that the solenoid valve can work normally when energized and de-energized, controlling the pressure and flow of the hydraulic system.

[0015] Compared with the prior art, the beneficial effects of this utility model are: 1. The cylindrical spring seat structure of this solenoid valve fundamentally improves performance and reliability, completely eliminating spring off-center loading. Surface contact support: The end face of the cylindrical boss forms a large-area, stable surface contact with the spring end ring, providing excellent radial support force. Mechanically, this eliminates the possibility of radial spring misalignment. Physical radial limiting: The positioning protrusion at the top is embedded inside the spring end ring, forming a double protection mechanism that physically restricts the radial movement of the outermost ring of the spring. This ensures that the spring maintains coaxiality with the valve core rod at any working stroke, significantly improving product performance consistency: Eliminating frictional fluctuations caused by off-center loading ensures high consistency in key performance parameters such as solenoid valve pull-in and release forces, and response time, improving product quality and reliability, and extending service life: The spring always operates under ideal conditions of uniform force, avoiding bending stress and reducing abnormal wear, thereby significantly reducing the risk of spring jamming of the valve core and extending the overall service life of the solenoid valve.

[0016] 2. The cylindrical spring seat structure of this solenoid valve significantly optimizes the structure and process, reduces costs, optimizes the process flow, improves production efficiency, and greatly reduces overall costs and management costs: it reduces the need for supplier management, incoming material inspection (IQC inspection of steel balls), and online process control (SPC monitoring of riveting pressure), thereby reducing quality control costs.

[0017] 3. The cylindrical spring seat structure of this solenoid valve significantly improves the production yield and quality, and reduces the performance scrap rate: Since it fundamentally solves the main problem of off-center loading that leads to inconsistent performance and failure, the performance scrap rate in the final testing stage is greatly reduced, resulting in high quality consistency: The consistency of machining is far higher than that of riveting processes, which are affected by various factors (pressure, grease, bore diameter tolerance, ball diameter tolerance), making the product quality more stable and reliable.

[0018] 4. The cylindrical spring seat structure of this solenoid valve enhances structural strength and connection reliability, avoiding the risk of loosening: The one-piece molded structure avoids the risk of fretting wear and loosening that may occur under long-term vibration and impact loads due to the interference fit of the steel ball, making the connection more reliable and permanent.

[0019] Other additional advantages and benefits of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0020] The accompanying drawings are provided to further illustrate the present invention and form part of the specification. They are used together with the embodiments of the present invention to explain the present invention, but do not constitute a limitation thereof. In the drawings: Figure 1 This is a side sectional view of the present invention; Figure 2 This is a cross-sectional view illustrating the oil cavity in this utility model; Figure 3 This is a schematic diagram of the installation of the cylindrical spring seat in this utility model.

[0021] In the diagram: 1. Valve sleeve filter screen; 2. First sealing ring; 3. First pole shoe; 4. Protective cover end; 5. Pole shoe assembly end; 6. Valve housing assembly; 7. Solenoid assembly; 8. Injection molded gasket; 9. PIN needle protective cover; 11. Dust cover; 12. First PIN needle; 13. Second PIN needle; 14. Cylindrical spring seat; 15. Rear yoke sleeve; 16. First bearing component; 17. Return spring; 18. Magnetic core; 19. Magnetic core shaft; 20. Second pole shoe; 21. Second bearing component; 22. Valve core support seat; 23. Valve sleeve; 24. Valve sleeve support seat; 25. Valve core; 26. Second sealing ring; 27. Locking steel ball; 28. Steel ball; 30. Flange features; 31. Axial oil inlet chamber; 32. First radial control oil chamber; 33. Second radial control oil chamber; 34. Radial oil discharge chamber. Detailed Implementation

[0022] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0023] This utility model provides a technical solution: Embodiment 1:

[0024] Combination Figure 1-3 A cylindrical spring seat structure for an electromagnetic valve, including a magnetic core shaft 19, and further comprising: A return spring 17 is sleeved on the surface of a magnetic core shaft 19. A boss is integrally formed at the end of the magnetic core shaft 19. The boss forms a cylindrical spring seat 14 that supports the return spring 17. A steel ball 28 is provided on one side of the cylindrical spring seat 14. The end face of the boss is provided with a positioning protrusion, which is used to limit the radial displacement of the return spring 17; The surface of the magnetic core shaft 19 is fitted with a first sealing ring 2 and a second sealing ring 26.

[0025] Furthermore, the boss is cylindrical, and the positioning protrusion is located at the center of the boss's end face, further clarifying that the boss is cylindrical and the positioning protrusion is located at the center of the boss's end face. This makes the structure of the cylindrical spring seat 14 more specific and defined, which helps to improve the stability and accuracy of the return spring 17 installation, ensuring that the return spring 17 can extend and retract along the central axis during operation, avoiding tilting or offset, and thus better fulfilling the function of the return spring 17.

[0026] Furthermore, the shape of the positioning protrusion can be any one of cylindrical, frustum-shaped, or conical. The shape of the positioning protrusion is specifically defined, with three possible shapes listed. These shapes of positioning protrusions can effectively limit the radial displacement of the return spring 17. At the same time, different shapes may be suitable for different working scenarios and design requirements, providing more options for the design and manufacture of the cylindrical spring seat 14, increasing the adaptability and practicality of the patent.

[0027] Furthermore, the outer diameter of the positioning protrusion is matched with the inner diameter of the end coil of the return spring 17, clarifying the matching relationship between the outer diameter of the positioning protrusion and the inner diameter of the end coil of the return spring 17. This ensures that the positioning protrusion can be accurately inserted into the end coil of the return spring 17, thereby better limiting the radial displacement of the return spring 17, preventing the return spring 17 from shaking or disengaging during operation, and improving the fitting accuracy and stability between the cylindrical spring seat 14 and the return spring 17.

[0028] Example 2:

[0029] Based on Embodiment 1, a further solenoid valve is obtained, including an electromagnetic component and a hydraulic component, wherein the electromagnetic component and the hydraulic component are connected by a flange feature 30 protruding from the end of the pole shoe component 5 and bent and closed.

[0030] Furthermore, the electromagnetic assembly includes a magnetic housing, a rear yoke sleeve 15, a first bearing component 16, a second bearing component 21, a magnetic core 18, a solenoid assembly 7, a protective cover end 4, a pole shoe assembly end 5, a first pole shoe 3, a second pole shoe 20, a first pin 12, a second pin 13, an injection-molded gasket 8, a pin protective cover 9, and a dust cover 11. The magnetic housing is composed of a metal stamped valve housing assembly 6. The magnetic core 18 is riveted to a magnetic core shaft 19. The solenoid assembly 7 is made of a nylon skeleton wound with copper wire. The pole shoe assembly is formed by a metal-processed pole shoe and a secondary injection-molded part. The first pin 12 and the second pin 13 are made of copper and are stamped. The first pin 12 and the second pin 13 are joined to the solenoid by riveting and welding.

[0031] Furthermore, the hydraulic components include a valve sleeve 23 assembly, a sealing ring assembly, a locking steel ball 27, a valve core 25, a valve core support seat 22, and a valve sleeve support seat 24. The valve sleeve 23 assembly is formed by injection molding of the valve sleeve filter screen 1 and the valve sleeve 23 through interference riveting. The valve core support seat 22 controls the pressure and flow by riveting with the valve core 25 at a fixed height. The valve sleeve support seat 24 is assembled with the end 5 of the pole shoe assembly by interference riveting.

[0032] Furthermore, the valve sleeve 23 assembly is equipped with an axial oil inlet chamber 31, a first radial control oil chamber, a second radial control oil chamber 33, and a radial oil discharge chamber. The medium oil is pressurized by the gearbox oil supply system. When energized, the medium oil enters from the inlet chamber; when de-energized, excess medium oil is discharged from the radial oil discharge chamber 34. This further clarifies the internal oil chamber structure of the valve sleeve 23 assembly and the flow path of the medium oil. By defining these structures and flow paths, the working principle of the hydraulic assembly becomes clearer, enabling accurate control of the inlet, outlet, and flow of the medium oil, realizing the hydraulic control function of the solenoid valve, and ensuring that the solenoid valve can operate normally when energized and de-energized, controlling the pressure and flow of the hydraulic system.

[0033] The working principle and usage process of this utility model are as follows: When energized, the solenoid assembly 7 generates a magnetic field. Under the action of the magnetic field force, the magnetic core 18 drives the magnetic core shaft 19 to move. The magnetic core shaft 19 pushes the valve core 25, and the valve core 25 pushes the locking steel ball 27. The medium oil enters from the oil inlet chamber 31. The vehicle gearbox driving magnetic core shaft controls the output current by giving a duty cycle, thereby controlling the electromagnetic force and the movement stroke of the magnetic core shaft 19. The valve core support seat 22 and the valve sleeve support seat 24 cooperate to overflow the gap, realizing precise control of the pressure and flow of the first radial control oil chamber 32 and the second radial control oil chamber 33. When de-energized, the magnetic core 18 is reset under the action of the return spring 17, the valve core 25 and the locking steel ball 27 return to the initial position, and the excess medium oil is discharged from the radial discharge chamber 34, completing one hydraulic control cycle.

[0034] Finally, it should be noted that the above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Although the utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A cylindrical spring seat structure for an electromagnetic valve, comprising a magnetic core shaft (19), characterized in that, Also includes: A reset spring (17) is sleeved on the surface of a magnetic core shaft (19). The end of the magnetic core shaft (19) is integrally formed with a boss. The boss forms a cylindrical spring seat (14) that supports the reset spring (17). A steel ball (28) is provided on one side of the cylindrical spring seat (14). The end face of the boss is provided with a positioning protrusion, which is used to limit the radial displacement of the return spring (17); The surface of the magnetic core shaft (19) is fitted with a first sealing ring (2) and a second sealing ring (26).

2. The cylindrical spring seat structure for an electromagnetic valve according to claim 1, characterized in that, The boss is cylindrical, and the positioning protrusion is located at the center of the end face of the boss.

3. The cylindrical spring seat structure for an electromagnetic valve according to claim 1, characterized in that, The shape of the positioning protrusion can be any one of cylindrical, frustum-shaped, or conical.

4. The cylindrical spring seat structure for a solenoid valve according to claim 1, characterized in that, The outer diameter of the positioning protrusion is adapted to the inner diameter of the end coil of the return spring (17).

5. A solenoid valve, characterized in that, The solenoid valve includes the cylindrical spring seat structure of any one of claims 1-4, and further includes an electromagnetic component and a hydraulic component, wherein the electromagnetic component and the hydraulic component are connected by a flange feature (30) protruding from the end of the pole shoe component (5) and bent to close.

6. The solenoid valve according to claim 5, characterized in that, The electromagnetic assembly includes a magnetic housing, a rear yoke sleeve (15), a first bearing part (16), a second bearing part (21), a magnetic core (18), a solenoid assembly (7), a protective cover end (4), a pole shoe assembly end (5), a first pole shoe (3), a second pole shoe (20), a first PIN pin (12), a second PIN pin (13), an injection-molded gasket (8), a PIN pin protective cover (9), and a dust cover (11). The magnetic housing is made of a metal stamped valve housing assembly (6). The magnetic core (18) is riveted to the magnetic core shaft (19). The solenoid assembly (7) is made of a nylon skeleton wound with copper wire. The pole shoe assembly is formed by a metal-processed pole shoe and a secondary injection-molded part. The first PIN pin (12) and the second PIN pin (13) are made of copper and are stamped. The first PIN pin (12) and the second PIN pin (13) are joined to the solenoid by riveting and welding.

7. The solenoid valve according to claim 6, characterized in that, The hydraulic components include a valve sleeve (23) assembly, a sealing ring assembly, a locking steel ball (27), a valve core (25), a valve core support seat (22), and a valve sleeve support seat (24). The valve sleeve (23) assembly is formed by injection molding of a valve sleeve filter screen (1) and a valve sleeve (23) through interference riveting. The valve core support seat (22) controls the pressure and flow by riveting with the valve core (25) at a fixed height. The valve sleeve support seat (24) is assembled with the end (5) of the pole shoe assembly by interference riveting.

8. The solenoid valve according to claim 7, characterized in that, The valve sleeve (23) assembly is provided with an axial oil inlet chamber (31), a first radial control oil chamber, a second radial control oil chamber (33), and a radial oil discharge chamber. The medium oil forms hydraulic pressure through the gearbox oil supply system. When the power is on, the medium oil enters from the oil inlet chamber. When the power is off, the excess medium oil is discharged from the radial oil discharge chamber (34).

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