Double-ring guide electromagnetic valve with anti-eccentric wear redundant structure

Abstract

The utility model relates to solenoid valve technical field especially relates to a double ring guide solenoid valve with prevent deviation redundant structure, include: valve body, valve seat, diaphragm mechanism includes the diaphragm subassembly that opens the air hole, the pilot seat of setting in the air hole, and the diaphragm subassembly has membrane hole, static core mechanism includes the diaphragm tube and static core body, moving core mechanism includes moving core body and the guide subassembly of periphery, tension spring connects between moving core body and pilot seat, spring connects between static core body and moving core body, the guide subassembly includes the first guide ring close to static core one end, the second guide ring close to pilot seat, and moving core body and diaphragm tube have the clearance between, the through -hole sets up on the moving core body wall between the second guide ring and pilot seat. The utility model reduces the contact friction of moving core body and diaphragm tube inner wall through the guide subassembly, to improve the service life and reliability of solenoid valve.

Description

Technical Field

[0001] This utility model relates to the field of solenoid valve technology, and in particular to a double-ring guided solenoid valve with an anti-wear redundancy structure. Background Technology

[0002] With the continuous improvement of industrial automation, solenoid valves are key components in fluid control systems. Solenoid valves control the movement of the valve core through electrical signals, thereby achieving precise control of liquid or gas flow. In complex working environments, the performance and reliability of solenoid valves have always been a key concern.

[0003] In existing technology, the moving iron core performs reciprocating motion under the combined action of electromagnetic force and spring force. However, due to the constraint of the diaphragm and the influence of the lateral force of the spring, the moving iron core may tilt, causing contact friction between the stationary iron core and the inner wall of the magnetic shielding tube. This friction not only aggravates the wear of the components but may also cause the moving iron core to jam, affecting the normal operation of the solenoid valve and causing the fluid control to lose accuracy and reliability.

[0004] Therefore, a technical solution is needed to reduce contact friction between the moving iron core and the inner wall of the magnetic shielding tube through structural improvements, in order to improve the service life and reliability of the solenoid valve. Utility Model Content

[0005] In view of at least one of the above technical problems, the present invention provides a double-ring guided solenoid valve with an anti-wear redundancy structure, thereby improving the service life of the solenoid valve through structural improvements.

[0006] According to a first aspect of this utility model, a double-ring guided solenoid valve with an anti-wear redundancy structure is provided, comprising: Valve body, including intake passage and exhaust passage; The valve seat has an internal receiving space and is connected to the valve body; The diaphragm mechanism includes a diaphragm assembly disposed between the valve body and the valve seat, a pilot seat sleeved on the diaphragm assembly, the pilot seat having an air passage connecting the air outlet channel and the receiving space, and the diaphragm assembly also having a membrane hole disposed opposite to the air inlet channel, the diameter of the membrane hole being smaller than that of the air passage. The stationary iron core mechanism includes a magnetic shielding tube connected at one end to the valve seat, and a stationary iron core body disposed at the other end of the magnetic shielding tube, wherein the magnetic shielding tube has a receiving chamber inside. A moving iron core mechanism includes a moving iron core body that can be relatively close to or away from the stationary iron core body within the receiving cavity, and the moving iron core body has a guide assembly on its outer periphery. A tension spring is connected between the moving iron core body and the pilot seat; A spring is connected between the stationary iron core body and the moving iron core body; The coil assembly is disposed on the outer periphery of the magnetic shielding tube; The guiding assembly includes a first guide ring near one end of the stationary iron core body and a second guide ring near the pilot seat, and there is a gap between the moving iron core body and the magnetic shielding tube.

[0007] In some embodiments of this utility model, the diaphragm assembly includes a diaphragm fixedly connected between the valve body and the valve seat, a cover plate concentrically arranged with the diaphragm and relatively close to the side of the moving iron core body, and a gasket concentrically arranged with the diaphragm and relatively close to the valve body. The cover plate includes a fitting portion that fits with the diaphragm and a bending portion that bends toward the moving iron core body. The diaphragm hole is disposed outside the fitting portion.

[0008] In some embodiments of this utility model, the pilot seat includes a riveting section, the diaphragm assembly is sleeved in the riveting section and riveted to fix it, and the riveting section is riveted to fit against the gasket.

[0009] In some embodiments of this utility model, a through air passage is provided inside the moving iron core body, and a through hole is provided on the wall of the moving iron core body to connect the through air passage and the receiving chamber. The through hole is provided on the wall of the moving iron core body between the second guide ring and the pilot seat. The end of the moving iron core body facing the pilot seat also has a mounting groove, and a glue plug is installed in the mounting groove.

[0010] In some embodiments of this utility model, the end of the pilot seat facing the moving iron core body also has a tapered section, and the diameter of the tapered section port is smaller than the diameter of the rubber plug.

[0011] In some embodiments of this utility model, the end of the moving iron core body facing the stationary iron core body has a receiving groove, the receiving groove has a buffer post, and one end of the spring is sleeved on the buffer post.

[0012] In some embodiments of this utility model, the stationary iron core body has a boss at one end facing the moving iron core body, the buffer post can be relatively close to or far away from the boss in the direction of the buffer post, the buffer post abuts against the boss, and the other end of the tension spring is sleeved on the outer periphery of the boss.

[0013] In some embodiments of this utility model, the moving core body between the first guide ring and the stationary core body is an inwardly tapered section, the section between the first guide ring and the second guide ring is a body section, and the distance between the inwardly tapered section and the magnetic shielding tube is 1.5 times the distance between the body section and the magnetic shielding tube.

[0014] In some embodiments of this utility model, the second guide ring and the pilot seat include a first stage close to the second guide ring and a second stage far away from the second guide ring. The distance between the first stage and the magnetic shielding tube is 1.5 times the distance between the body segment and the magnetic shielding tube, and the distance between the second stage and the magnetic shielding tube is 2.5 times the distance between the body segment and the magnetic shielding tube.

[0015] In some embodiments of this utility model, there are gaps between the first guide ring and the second guide ring and the magnetic shielding tube.

[0016] The beneficial effects of this utility model are as follows: Through the double-ring guidance of the first and second guide rings, the moving iron core body is always controlled on a precise guiding trajectory during movement, ensuring that the moving iron core body will not tilt or deviate significantly even under the constraint of the diaphragm mechanism and the lateral force of the spring. The gap between the moving iron core body and the magnetic shielding tube can further reduce friction and provide the moving iron core body with a certain space for movement adjustment, thereby avoiding the risk of possible jamming. Through the coil assembly, diaphragm mechanism and pilot seat, not only can the moving iron core body be driven more efficiently, but the fluid switching can also be controlled through the position of the air vent. At the same time, it ensures that the overall structure still has high stability under high-frequency operation, so that the solenoid valve in this utility model has significant improvements in terms of lifespan, reliability and fluid control accuracy. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the structure of the double-ring guided solenoid valve with anti-wear redundancy structure in an embodiment of this utility model; Figure 2 This is a cross-sectional view of the internal structure of the double-ring guided solenoid valve with anti-wear redundancy structure in the open state in an embodiment of this utility model. Figure 3 This is a cross-sectional view of the internal structure of the double-ring guided solenoid valve with anti-wear redundancy structure in the closed state in an embodiment of this utility model. Figure 4 This is a cross-sectional view of the stationary iron core mechanism and the moving iron core mechanism in the embodiments of this utility model; Figure 5This is a cross-sectional view of the stationary iron core mechanism in an embodiment of this utility model; Figure 6 This is a cross-sectional view of the moving iron core mechanism in an embodiment of this utility model; Figure 7 This is a cross-sectional view of the diaphragm assembly in an embodiment of the present invention; Figure 8 As an embodiment of this utility model Figure 4 Enlarged structural diagram at point A; Figure 9 As an embodiment of this utility model Figure 4 Enlarged schematic diagram of the structure at point B.

[0019] Reference numerals: 1. Valve body; 11. Inlet passage; 12. Outlet passage; 2. Valve seat; 21. Receiving space; 3. Diaphragm mechanism; 31. Diaphragm assembly; 31b. Diaphragm orifice; 31c. Diaphragm sheet; 31d. Cover plate; 31d1. Fitting part; 31d2. Bending part; 31e. Gasket; 32. Pilot seat; 32a. Air passage; 32b. Riveting section; 32c. First fixing groove; 32d. Conical section; 4. Static iron core mechanism; 41. Magnetic shielding tube; 42. Static iron core body; 43. Receiving space 44. Chamber; 45. Boss; 46. Gap; 5. Moving iron core mechanism; 51. Moving iron core body; 51a. Through air passage; 51b. Through hole; 51c. Inner section; 51d. Body section; 51e. First stage; 51f. Second stage; 52. Guide assembly; 52a. First guide ring; 52b. Second guide ring; 53. Plug; 54. Mounting groove; 55. Second fixing groove; 56. Receiving groove; 57. Buffer column; 6. Tension spring; 7. Spring; 8. Coil assembly. Detailed Implementation

[0020] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present utility model. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments.

[0021] It should be noted that when an element is referred to as being "fixed to" another element, it can be directly attached to the other element or there may be an intervening element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0022] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0023] like Figures 1 to 9 The double-ring pilot solenoid valve with anti-wear redundancy structure shown includes: Valve body 1 includes an air inlet passage 11 and an air outlet passage 12; Valve seat 2 has an internal receiving space 21 and is connected to valve body 1; The diaphragm mechanism 3 includes a diaphragm assembly 31 disposed between the valve body 1 and the valve seat 2, a pilot seat 32 sleeved on the diaphragm assembly 31, the pilot seat 32 having an air passage 32a communicating with the air outlet channel 12 and the receiving space 21, and the diaphragm assembly 31 also having a membrane hole 31b disposed opposite to the air inlet channel 11, the diameter of the membrane hole 31b being smaller than that of the air passage 31a; The stationary iron core mechanism 4 includes a magnetic shielding tube 41 connected to the valve seat 2 at one end, and a stationary iron core body 42 disposed at the other end of the magnetic shielding tube 41. The magnetic shielding tube 41 has a receiving chamber 43 inside. The moving iron core mechanism 5 includes a moving iron core body 51 that can be relatively close to or away from the stationary iron core body 42 within a receiving chamber 43, and the moving iron core body 51 has a guide assembly 52 on its outer periphery. Tension spring 6 connects the moving iron core body 51 and the pilot seat 32; Spring 7 is connected between the stationary iron core body 42 and the moving iron core body 51; Coil assembly 8 is disposed on the outer periphery of magnetic shielding tube 41; The guide assembly 52 includes a first guide ring 52a near one end of the stationary iron core body 42 and a second guide ring 52b near the pilot seat 32. A gap 46 exists between the moving iron core body 51 and the magnetic shielding tube 41. It should be noted that the first guide ring 52a and the second guide ring 52b may be made of wear-resistant and / or self-lubricating materials.

[0024] like Figure 3As shown, in the initial state, the solenoid valve is closed, and the moving iron core body 51 moves away from the stationary iron core body 42 under the action of the spring 7, and is held close to the pilot seat 32 by the tension spring 6. At this time, the air inlet channel 11 and the air outlet channel 12 are disconnected. When the coil assembly 8 is energized, the electromagnetic force acts on the stationary iron core body 42, attracting the moving iron core body 51 to move towards the stationary iron core body 42. During the movement, the double-ring guide structure composed of the first guide ring 52a and the second guide ring 52b effectively constrains the moving iron core body 51, so that its movement path always remains stable and without deviation. As the moving iron core body 51 moves, the air vent 32a opens, and the air vent 32a on the pilot seat 32 connects with the receiving space 21. A pressure difference is generated above and below the diaphragm assembly 31, which reduces the pressure between the diaphragm assembly 31 and the receiving space 21. Because the diameter difference between the membrane hole 31b on the diaphragm assembly 31 and the air passage 32a on the pilot seat 32 is large, the pressure of the gas in the air inlet channel 11 increases, thereby pushing the diaphragm assembly 31 to rise, opening the main valve port, and allowing fluid to flow in from the air inlet channel 11 and flow out through the air outlet channel 12, thus realizing the valve opening function.

[0025] like Figure 2 As shown, when the coil is de-energized, the electromagnetic force of the stationary iron core body 42 disappears, and the moving iron core body 51 returns to the pilot seat 32 under the dual action of the spring 7 and the tension spring 6, disengaging from the stationary iron core body 42. The accommodating space 21 above the diaphragm assembly 31 recovers pressure, causing the diaphragm assembly 31 to fall back under air pressure, closing the main valve port and cutting off the fluid channel. The precise guidance of the first guide ring 52a and the second guide ring 52b ensures that the movement trajectory of the moving iron core body 51 remains stable during the opening and closing process, avoiding deviation and tilting, effectively reducing friction with the inner wall of the magnetic shielding tube 41, and achieving smooth operation, high efficiency and durability.

[0026] This invention utilizes a double-ring guide system (first guide ring 52a, second guide ring 52b) to ensure that the moving iron core body 51 remains on a precise guiding trajectory throughout its movement. This prevents significant tilting or deviation of the moving iron core body 51 even under the constraint of the diaphragm mechanism 3 and the lateral force of the spring 7. The gap 46 between the moving iron core body 51 and the magnetic shielding tube 41 further reduces friction and provides the moving iron core body 51 with a certain amount of adjustment space, thus avoiding potential jamming risks. Through the coil assembly 8, diaphragm mechanism 3, and pilot seat 32, the moving iron core body 51 can be driven more efficiently, while ensuring that the overall structure maintains high stability under high-frequency operation. This significantly improves the lifespan, reliability, and fluid control accuracy of the solenoid valve in this invention.

[0027] The main function of the diaphragm assembly 31 is to isolate and seal the fluid passage. Most diaphragm assemblies 31 are single-layer structures, but during use, problems such as uneven stress, deformation, or wear can lead to a decrease in sealing performance, thereby affecting the valve's opening and closing status and the accuracy of fluid control. Figure 7 As shown, in some embodiments of this utility model, the diaphragm assembly 31 includes a diaphragm 31c fixedly connected between the valve body 1 and the valve seat 2, a cover plate 31d concentrically arranged with the diaphragm 31c and relatively close to the moving iron core body 51, and a gasket 31e concentrically arranged with the diaphragm 31c and relatively close to the valve body 1. The cover plate 31d includes a fitting portion 31d1 that fits with the diaphragm 31c, and a bending portion 31d2 that bends toward the moving iron core body 51. The diaphragm hole is disposed outside the fitting portion 31d1. The concentric arrangement of diaphragm 31c, cover plate 31d, and gasket 31e forms a diaphragm assembly 31 with multi-layer support performance, improving the system's durability and sealing effect. Diaphragm 31c is fixedly connected between valve body 1 and valve seat 2, becoming the main body of diaphragm assembly 31 and realizing the basic functions of fluid isolation and sealing. Gasket 31e provides stronger support through tight fit and further enhances the sealing and pressure resistance of diaphragm 31c. Diaphragm 31c and cover plate 31d are arranged concentrically. Cover plate 31d is relatively close to the side of moving iron core body 51 and undertakes the key structural optimization function, especially playing an important role in withstanding the impact of high-frequency moving iron core body 51. The fitting portion 31d1 of the cover plate 31d is connected to the diaphragm 31c to ensure that the two will not separate during operation, thereby maintaining a stable sealing effect. The bent portion 31d2 of the cover plate 31d extends towards the moving iron core body 51, further guiding the movement of the moving iron core body 51 and buffering the offset, reducing the risk of uneven force on the diaphragm 31c due to inaccurate movement of the moving iron core body 51.

[0028] In the above technical solution, to ensure a tighter connection between the diaphragm 31c, the cover plate 31d, and the gasket 31e, and to avoid the risk of gas leakage during operation, such as... Figure 7As shown, the pilot seat 32 includes a riveting section 32b. The diaphragm assembly 31 is fitted inside the riveting section 32b and riveted in place. The riveting section 32b is riveted until it fits against the gasket 31e. The function of the riveting section 32b is not only to provide a stable installation position for the diaphragm assembly 31, but more importantly, to form a reliable mechanical fixation between the diaphragm assembly 31 and the pilot seat 32 through riveting. By riveting, the riveting section 32b is finally fitted against the gasket 31e position in the diaphragm assembly 31, preventing the diaphragm assembly 31c from loosening or deforming due to pressure changes or continuous vibration during operation, thereby ensuring the long-term stability of the seal. In the specific installation process, the cover plate 31d, diaphragm 31c, and gasket 31e are first passed through the riveting section 32b, and then pressure is applied to the riveting section 32b to form a tight connection between the pilot seat 32 and the cover plate 31d, and between the diaphragm 31c and the gasket 31e.

[0029] In some embodiments of this utility model, such as Figure 3 , Figure 4 As shown, the moving iron core body 51 has a through-flow passage 51a inside, and a through hole 51b connecting the through-flow passage 51a and the receiving chamber 43 is formed on the wall of the moving iron core body 51. The through hole 51b is located on the wall of the moving iron core body 51 between the second guide ring 52b and the pilot seat 32. The end of the moving iron core body 51 facing the pilot seat 32 also has a mounting groove 54, in which a rubber plug 53 is installed. The mounting groove 54 provides a stable and accurate positioning, ensuring that the rubber plug 53 remains in the predetermined position during the movement of the moving iron core body 51. This not only enhances the sealing effect between the moving iron core body 51 and the pilot seat 32, but also avoids the influence of high-frequency movement or vibration on the position of the rubber plug 53, ensuring precise fluid control. The through-flow passage 51a connects the through-flow passage 51a and the receiving chamber 43, allowing the internal fluid to flow during the movement of the moving iron core body 51, preventing the moving iron core body 51 from being unable to move due to the lack of internal fluid flow.

[0030] In some embodiments of this utility model, such as Figure 7 As shown, the end of the pilot seat 32 facing the moving iron core body 51 also has a tapered section 32d, the diameter of which is smaller than the diameter of the rubber plug 53. The tapered section 32d, with its cone-shaped form and smaller diameter than the rubber plug 53, enhances the airtightness, increasing the smoothness of the airflow path and effectively reducing the impact of airflow on the moving iron core body 51 during the switching of the air passage 32a. It also refines the interaction between the gas and the moving iron core body 51. This not only reduces the tilting and friction of the moving iron core body 51 during movement but also enhances the overall stability of the system.

[0031] To reduce the impact of the collision between the moving iron core body 51 and the stationary iron core body 42 on wear, such as Figure 4 , Figure 6 As shown, the end of the moving iron core body 51 facing the stationary iron core body 42 has a receiving groove 56, and a buffer post 57 is located inside the receiving groove 56. One end of the spring 7 is sleeved on the buffer post 57. The buffer post 57 can more effectively absorb and buffer kinetic energy, reducing the impact of vibration and shock on the component. The buffer post 57 optimizes the smoothness of the moving iron core during reset and prevents direct collisions when the moving iron core body 51 and the stationary iron core body 42 come into contact. The design of the buffer post 57, in conjunction with the sleeve of the spring 7, makes the distribution of elastic force more uniform, and the movement of the moving iron core body 51 becomes smoother and more fluid, thereby improving the response speed and reset accuracy of the solenoid valve.

[0032] like Figure 4 , Figure 5 As shown, the stationary iron core body 42 has a boss 44 at one end facing the moving iron core body 51. The buffer post 57 can be relatively close to or away from the boss 44, and the buffer post 57 abuts against the boss 44. There is a gap 45 between the stationary iron core body 42 and the moving iron core body 51. The other end of the spring 7 is sleeved on the outer periphery of the boss 44. This structure allows the moving iron core body 51 to be auxiliaryly buffered by the buffer post 57 during movement, so that kinetic energy is effectively absorbed and direct impact is reduced. The buffer post 57 and the boss 44 can precisely abut at the end of the movement of the moving iron core body 51, further reducing wear and noise between the moving iron core body 51 and the stationary iron core body 42. The gap 45 between the stationary iron core body 42 and the moving iron core body 51 ensures a safe buffer distance between them during operation. The other end of the spring 7 is sleeved on the outer periphery of the boss 44, which allows the moving iron core body 51 to quickly separate from the stationary iron core body 42 when the coil assembly 8 is de-energized, improving the closing response time of the solenoid valve.

[0033] The movement of the moving iron core body 51 may tilt or jam due to inaccurate guidance or excessive friction. This limits the rapid response and stable performance of the solenoid valve, and also exacerbates component wear, affecting service life and control accuracy. Figure 8As shown, the moving core body 51 between the first guide ring 52a and the stationary core body 42 is an inwardly tapered section 51c, and the section between the first guide ring 52a and the second guide ring 52b is the body section 51d. The distance between the inwardly tapered section 51c and the magnetic shielding tube 41 is 1.5 times the distance between the body section 51d and the magnetic shielding tube 41. The inwardly tapered section 51c between the first guide ring 52a and the stationary core body 42 has a smaller outer diameter to reduce the frictional contact area. The distance between the inwardly tapered section 51c and the magnetic shielding tube 41 is set to 1.5 times the distance between the body section 51d and the magnetic shielding tube 41, which makes the moving core body 51 more evenly stressed when it is close to the stationary core body 42. This avoids unstable lateral movement or tilting of the moving core body 51, improves the smoothness and accuracy of the movement, and allows the moving core body 51 to obtain a better guiding effect during movement, reducing eccentric wear caused by radial force imbalance.

[0034] Similarly, avoid wear on the other end, such as Figure 9 As shown, the second guide ring 52b and the pilot seat 32 include a first stage 51e closer to the second guide ring 52b and a second stage 51f farther away from the second guide ring 52b. The distance between the first stage 51e and the magnetic shielding tube 41 is 1.5 times the distance between the main body section 51d and the magnetic shielding tube 41, and the distance between the second stage 51f and the magnetic shielding tube 41 is 2.5 times the distance between the main body section 51d and the magnetic shielding tube 41. Through the two stepped structures between the second guide ring 52b and the pilot seat 32, fine-grained adjustments are made to the axial clearance 46, providing layered guiding support for the movement of the moving iron core body 51. The first stage 51e is close to the second guide ring 52b, and its distance from the magnetic shielding tube 41 is set to 1.5 times the distance between the main body section 51d and the magnetic shielding tube 41, ensuring that the moving iron core body 51 can obtain a relatively tight guiding constraint when it is close to the second guide ring 52b, reducing the possibility of lateral displacement at this position. The second stage 51f is further away from the second guide ring 52b, and the distance between it and the magnetic shielding tube 41 is further increased to 2.5 times the distance between the main body section 51d and the magnetic shielding tube 41, providing more spacious movement space for the moving iron core body 51, so as to allow it to fully absorb energy at the end of the action and ensure the stability of fluid switching.

[0035] In existing technologies, the guide ring and the magnetic shielding tube 41 are often fitted together to limit the lateral movement of the moving iron core body 51 by reducing wobbling. However, an overly tight connection can easily lead to increased direct friction between the guide ring and the magnetic shielding tube 41, resulting in rapid wear of the components. Both the first guide ring 52a and the second guide ring 52b have a gap 46 between themselves and the magnetic shielding tube 41. The gap 46 allows the moving iron core body 51 a certain amount of adjustment space during movement. When subjected to the combined action of electromagnetic force and spring force, it can effectively adapt to changes in system force, ensuring that the moving iron core body 51 maintains a stable movement state under the constraint of the guide ring. When the moving iron core body 51 wobbles or deviates within the left-right range, the first guide ring 52a and the second guide ring 52b prevent the moving iron core body 51 from contacting the magnetic shielding tube 41 within the tube. The first guide ring 52a and the second guide ring 52b isolate the contact between the two, thereby preventing uneven wear of the solenoid valve.

[0036] Those skilled in the art should understand that this utility model is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of this utility model. Various changes and modifications can be made to this utility model without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claimed utility model. The scope of protection of this utility model is defined by the appended claims and their equivalents.

Claims

1. A double ring pilot solenoid valve having a bias wear prevention redundant structure, characterized by, include: Valve body, including intake passage and exhaust passage; The valve seat has an internal receiving space and is connected to the valve body; The diaphragm mechanism includes a diaphragm assembly disposed between the valve body and the valve seat, a pilot seat sleeved on the diaphragm assembly, the pilot seat having an air passage connecting the air outlet channel and the receiving space, and the diaphragm assembly also having a membrane hole disposed opposite to the air inlet channel, the diameter of the membrane hole being smaller than that of the air passage. The stationary iron core mechanism includes a magnetic shielding tube connected at one end to the valve seat, and a stationary iron core body disposed at the other end of the magnetic shielding tube, wherein the magnetic shielding tube has a receiving chamber inside. A moving iron core mechanism includes a moving iron core body that can be relatively close to or away from the stationary iron core body within the receiving cavity, and the moving iron core body has a guide assembly on its outer periphery. A tension spring is connected between the moving iron core body and the pilot seat; A spring is connected between the stationary iron core body and the moving iron core body; The coil assembly is disposed on the outer periphery of the magnetic shielding tube; The guiding assembly includes a first guide ring near one end of the stationary iron core body and a second guide ring near the pilot seat, and there is a gap between the moving iron core body and the magnetic shielding tube.

2. The dual ring pilot solenoid valve having a bias wear prevention redundant structure according to claim 1, characterized by, The diaphragm assembly includes a diaphragm fixedly connected between the valve body and the valve seat, a cover plate concentrically arranged with the diaphragm and relatively close to the side of the moving iron core body, and a gasket concentrically arranged with the diaphragm and relatively close to the valve body. The cover plate includes a fitting portion that fits with the diaphragm and a bending portion that bends toward the moving iron core body. The diaphragm hole is located outside the fitting portion.

3. The dual ring pilot solenoid valve having a bias wear prevention redundant structure according to claim 2, characterized by, The pilot seat includes a riveting section, the diaphragm assembly is sleeved in the riveting section and riveted to fix it, and the riveting section is riveted to fit against the gasket.

4. The double-ring guided solenoid valve with anti-wear redundancy structure according to claim 1, characterized in that, The moving iron core body has a through air passage inside, and a through hole is formed on the wall of the moving iron core body to connect the through air passage and the receiving chamber. The through hole is set on the wall of the moving iron core body between the second guide ring and the pilot seat. The end of the moving iron core body facing the pilot seat also has a mounting groove, and a glue plug is installed in the mounting groove.

5. The double-ring guided solenoid valve with anti-wear redundancy structure according to claim 4, characterized in that, The pilot seat also has a tapered section at one end facing the moving iron core body, and the diameter of the tapered section port is smaller than the diameter of the rubber plug.

6. The dual ring pilot solenoid valve having a bias wear prevention redundant structure according to claim 1, characterized in that, The moving iron core body has a receiving groove at one end facing the stationary iron core body, and a buffer post is provided in the receiving groove. One end of the spring is sleeved on the buffer post.

7. The dual ring pilot solenoid valve having a bias wear prevention redundant structure according to claim 6, characterized by, The stationary iron core body has a boss at one end facing the moving iron core body. The buffer post can be relatively close to or far away from the boss in the direction of the boss. The buffer post abuts against the boss. The other end of the tension spring is sleeved on the outer periphery of the boss.

8. The dual ring pilot solenoid valve having a bias wear prevention redundant structure according to claim 1, characterized in that, The moving core body between the first guide ring and the stationary core body is an inward-curving section, and the body section between the first guide ring and the second guide ring is a body section. The distance between the inward-curving section and the magnetic shielding tube is 1.5 times the distance between the body section and the magnetic shielding tube.

9. The dual ring pilot solenoid valve having a bias wear prevention redundant structure according to claim 8, characterized by, The second guide ring and the pilot seat include a first stage close to the second guide ring and a second stage far from the second guide ring. The distance between the first stage and the magnetic shielding tube is 1.5 times the distance between the body segment and the magnetic shielding tube, and the distance between the second stage and the magnetic shielding tube is 2.5 times the distance between the body segment and the magnetic shielding tube.

10. The dual ring pilot solenoid valve having a bias wear prevention redundant structure according to claim 1, characterized in that, Both the first guide ring and the second guide ring have gaps between themselves and the magnetic shielding tube.

Images