Two-position two-way electromagnetic valve

Abstract

A valve body is provided with an air inlet, an air outlet and a valve port, the two-position two-way electromagnetic valve further comprises a sleeve, a static iron core, a movable iron core and a coil, the static iron core is fixedly arranged in the sleeve, the movable iron core is arranged above the static iron core in a sliding mode, a valve element assembly and an ejector rod are movably arranged in the static iron core, and the movable iron core abuts against the valve element assembly through the ejector rod. A second spring is arranged between the valve element assembly and the valve body, and the axial displacement stroke of the valve element assembly relative to the static iron core is L1. The valve element assembly comprises a valve element seat and a valve element, the axial displacement stroke of the valve element relative to the valve element seat is L2, a first gap is formed between the valve element seat and the static iron core, a first cavity is formed in the valve element seat, a first spring is arranged in the first cavity and abuts against the valve element, the first cavity is communicated with the air inlet, and the first gap is increased when the valve element seat moves downwards. The flow of air entering the first cavity is increased, the valve element seat moves upwards, the first gap is reduced, the flow of air entering the first cavity is reduced, the coil power requirement is lowered through the sectional stroke, and the power-on time is prolonged.

Description

Technical Field

[0001] This utility model relates to the field of solenoid valve technology, and in particular to a two-position two-way solenoid valve. Background Technology

[0002] In existing technologies, the spool stroke of a 2-position 2-way solenoid valve typically corresponds to the distance between the spool and the valve port. The spool stroke is directly related to the displacement stroke of the moving iron core. Specifically, in existing technologies, if the maximum distance between the spool and the valve port is assumed to be L, the moving iron core must also move a distance L to achieve the corresponding operation. This maximum distance not only directly determines the maximum opening of the valve port, but the maximum opening of the valve port further affects the flow rate of the solenoid valve. To achieve a larger flow output, the valve port opening is usually set to be relatively large, which inevitably requires a corresponding increase in the spool stroke. This is because the spool stroke and the moving iron core stroke are usually corresponding. A larger moving iron core stroke means that the coil driving the moving iron core needs more power. Increased coil power inevitably leads to a higher temperature rise, preventing the solenoid valve from continuously operating for extended periods to avoid overheating damage or performance issues. Therefore, improvements are necessary. Utility Model Content

[0003] The purpose of this utility model is to address the shortcomings and deficiencies of the existing technology by providing a two-position two-way solenoid valve with a simple and reasonable structure and convenient operation. The segmented design shortens the stroke of the moving iron core, reduces the coil power requirement, effectively reduces temperature rise, extends the solenoid valve energizing time, and improves working efficiency and stability.

[0004] To achieve the above objectives, the present invention adopts the following technical solution:

[0005] A two-position two-way solenoid valve according to the present utility model includes a valve body and a pilot valve assembly. An air inlet and an air outlet are provided on the valve body, and a valve port for connecting the air inlet and the air outlet is provided inside the valve body. The pilot valve assembly includes a sleeve, a stationary iron core, a movable iron core, and a coil. The coil is wound around the outer periphery of the sleeve. The stationary iron core is fixedly arranged inside the sleeve. The movable iron core is slidably arranged above the stationary iron core. A valve core assembly and a push rod are movably arranged inside the stationary iron core. The movable iron core abuts against the valve core assembly through the push rod. A second spring is provided between the lower end of the valve core assembly and the valve body. The second spring makes the valve core assembly always have a tendency to move upward. The axial displacement stroke of the valve core assembly relative to the stationary iron core is L1. The valve core assembly includes a valve core seat and a valve core. The valve core seat is movably arranged inside the stationary iron core and abuts against the push rod. The valve core is movably arranged inside the valve core seat and is in sealing cooperation with the valve port. The axial displacement stroke of the valve core relative to the valve core seat is L2. A first gap is formed between the valve core seat and the stationary iron core. A first chamber is provided between the upper end surface of the valve core and the valve core seat. A first spring is provided inside the first chamber. The first spring abuts against the valve core and makes the valve core always have a tendency to move downward. The first chamber is connected to the air inlet through the first gap. When the valve core seat moves downward, at least part of the first gap will become larger, so that the air flow rate entering the first chamber increases. When the valve core seat moves upward, at least part of the first gap will become smaller, so that the air flow rate entering the first chamber decreases.

[0006] Further, a first air guide passage for connecting the first chamber and the first gap is provided on the valve core seat.

[0007] Further, a second gap is formed between the push rod and the stationary iron core. A second air guide passage is provided on the stationary iron core. A second chamber is provided between the stationary iron core and the movable iron core. A third gap for connecting the second air guide passage and the second chamber is provided between the stationary iron core and the sleeve.

[0008] Further, a first installation groove for installing the valve core is provided at the lower end of the valve core seat.

[0009] Further, a first limiting step and a second limiting step for cooperating with the valve core are provided inside the first installation groove. The valve core can slide between the first limiting step and the second limiting step. The upper end surface of the valve core is in limiting cooperation with the first limiting step. A third limiting step is provided on the outer side wall of the valve core. The third limiting step is in limiting cooperation with the second limiting step.

[0010] Further, the cross-sectional area of the upper end surface of the valve core is larger than the cross-sectional area of the lower end surface of the valve core.

[0011] Further, the valve core is arranged in an inverted "convex" shape.

[0012] Furthermore, the outer diameter of the sleeve is designed to be 10-12 mm.

[0013] Furthermore, the outer diameter of the sleeve is designed to be 11 mm.

[0014] Furthermore, the lower end of the stationary iron core is provided with a fourth limiting step that cooperates with the valve core seat limiting step.

[0015] The beneficial effects of this utility model are as follows: The two-position two-way solenoid valve described in this utility model is a normally open valve. When not energized, the valve port remains open, and when energized, the valve port is closed. The present invention discloses a two-position two-way solenoid valve with a segmented stroke. When the solenoid valve is energized, the moving iron core moves downward and controls the valve core assembly to overcome the spring force of the second spring, resulting in an axial displacement of L1 relative to the stationary iron core. The valve core assembly includes a valve core seat and a valve core. The valve core seat is movably disposed within the stationary iron core and abuts against the push rod. The valve core is movably disposed within the valve core seat and seals against the valve port. When the coil is energized and the valve core seat moves downward, at least a portion of the first gap formed between the valve core seat and the stationary iron core will increase, thereby increasing the airflow into the first chamber and increasing the air pressure acting on the upper surface of the valve core. The valve core experiences an axial displacement of L2 relative to the valve core seat. This segmented stroke design cleverly shortens the moving iron core's travel, allowing the coil power to be designed to be relatively small. This not only effectively reduces the coil's temperature rise but also extends the solenoid valve's energizing time, improving overall working efficiency and stability.

[0016] The selection of the outer diameter design parameters of the sleeve is closely related to the pressure bearing capacity of the solenoid valve. Specifically, if the solenoid valve is expected to bear higher pressure, the force of the tower spring must be increased. When the force of the tower spring increases, the electromagnetic coil is required to generate a stronger magnetic force in the energized state to overcome the elastic force of the tower spring. However, in the prior art, the outer diameter of the sleeve is generally designed to be 9 mm. This size limits the increase of magnetic force, which in turn limits the force of the tower spring, thus limiting the pressure bearing capacity of the solenoid valve. In view of this, this embodiment increases the outer diameter of the sleeve to 10 to 12 mm, preferably 11 mm, which effectively increases the magnetic force generated by the electromagnetic coil and increases the force of the tower spring. Based on this improvement, the pressure bearing capacity of the solenoid valve is also significantly improved, meeting the requirements of higher working pressure. Attached Figure Description

[0017] Figure 1 This is a cross-sectional structural diagram of the present invention when it is powered on;

[0018] Figure 2 yes Figure 1 Enlarged structural diagram at point A;

[0019] Figure 3 This is a cross-sectional structural diagram of the present invention when power is off;

[0020] Figure 4 yes Figure 3 A magnified structural diagram at point B in the middle.

[0021] Figures 1-4 In the middle: 1. Valve body; 11. Air inlet; 12. Air outlet; 13. Valve port; 14. Second spring; 2. Pilot valve assembly; 21. Sleeve; 211. Second mounting groove; 22. Stationary iron core; 221. Valve core seat; 2211. First mounting groove; 22111. First limiting step; 22112. Second limiting step; 2212. Valve core; 22121. Third limiting step; 2213. First chamber; 22131. First spring; 2214. First air guide channel; 2215. Mounting step; 222. Push rod; 223. Second air guide channel; 224. Fourth limiting step; 23. Moving iron core; 24. Coil; 3. Second chamber; 4. Pressure plate; 5. O-ring; 6. Locking nut; 7. First gap; 8. Second gap; 9. Third gap. Detailed Implementation

[0022] The present invention will be further described below with reference to the accompanying drawings.

[0023] like Figures 1-4The diagram shows a two-position two-way solenoid valve, comprising a valve body 1 and a pilot valve assembly 2. The valve body 1 has an inlet 11 and an outlet 12. A valve port 13 is provided inside the valve body 1 to connect the inlet 11 and the outlet 12. The pilot valve assembly 2 is used to open or close the valve port 13. The pilot valve assembly 2 includes a sleeve 21, a stationary iron core 22, a moving iron core 23, and a coil 24. The coil 24 is wound around the outer circumference of the sleeve 21. The stationary iron core 22 is fixedly disposed inside the sleeve 21. The moving iron core 23 is slidably disposed above the stationary iron core 22. A valve is movably disposed within the stationary iron core 22. The valve core assembly and push rod 222 are connected. The moving iron core 23 abuts against the valve core assembly via the push rod 222. A second spring 14 is abutted between the lower end of the valve core assembly and the valve body 1. The second spring 14 ensures that the valve core assembly always has an upward movement tendency, causing the valve core 2212 to open the valve port 13. That is, in the state of no power, the valve port 13 is normally open. The axial displacement stroke of the entire valve core assembly relative to the stationary iron core 22 is L1. The valve core assembly includes a valve core seat 221 and a valve core 2212. The valve core seat 221 is movably disposed within the stationary iron core 22 and abuts against the push rod 222. The valve core 2212 is movably disposed within the stationary iron core 22 and abuts against the push rod 222. The valve core seat 221 is sealed to the valve port 13. The axial displacement stroke of the valve core 2212 relative to the valve core seat 221 is L2. A first gap 7 is formed between the valve core seat 221 and the stationary iron core 22. A first chamber 2213 is provided between the upper end face of the valve core 2212 and the valve core seat 221. A first spring 22131 is provided in the first chamber 2213. The first spring 22131 abuts against the valve core 2212, causing the valve core 2212 to always have a downward movement tendency. Preferably, in this embodiment, the valve core seat 221 is provided with a connection for communicating with the first chamber. The first air passage 2214 of the first chamber 2213 and the first gap 7 are connected to the air inlet 11 via the first air passage 2214 and the first gap 7. When the coil 24 is energized and the valve core seat 221 moves downward, at least a part of the first gap 7 will become larger, thereby increasing the air flow rate into the first chamber 2213 and increasing the air pressure acting on the upper end face of the valve core 2212. When the coil 24 is de-energized and the valve core seat 221 moves upward, at least a part of the first gap 7 will become smaller, thereby decreasing the air flow rate into the first chamber 2213 and decreasing the air pressure acting on the upper end face of the valve core 2212.

[0024] The two-position two-way solenoid valve described in this utility model is a normally open valve. When not energized, the valve port 13 remains open; when energized, the valve port 13 closes. This two-position two-way solenoid valve employs a segmented stroke. When the solenoid valve is energized, the moving iron core 23 moves downward and, through the push rod 222, controls the valve core assembly to overcome the elastic force of the second spring 14, resulting in an axial displacement of L1 relative to the stationary iron core 22. The valve core assembly includes a valve core seat 221 and a valve core 2212. The valve core seat 221 is movably disposed within the stationary iron core 22 and abuts against the push rod 222. The valve core 2212 is movably disposed within the valve core seat 221 and seals against the valve port 13. When the coil 24 is energized, the valve core seat 221 moves downward. At least a portion of the first gap 7 formed between the 1 and the stationary iron core 22 will increase, thereby increasing the airflow into the first chamber 2213 and increasing the air pressure acting on the upper surface of the valve core 2212. The axial displacement stroke of the valve core 2212 relative to the valve core seat 221 is L2. Through this segmented stroke design, the moving stroke of the moving iron core 23 is cleverly shortened, so that the power required by the coil 24 can be designed to be relatively small. This not only effectively reduces the temperature rise of the coil 24, but also extends the energizing time of the solenoid valve, improving the overall working efficiency and stability.

[0025] Preferably, in this embodiment, a second gap 8 is formed between the push rod 222 and the stationary iron core 22, a second air guide channel 223 is provided on the stationary iron core 22, a second chamber 3 is provided between the stationary iron core 22 and the moving iron core 23, a third gap 9 is provided between the stationary iron core 22 and the sleeve 21 for connecting the second air guide channel 223 and the second chamber 3, and the moving iron core 23 and the sleeve 21 are in a clearance fit to allow gas to pass through. Specifically, the gas at the air inlet 11 first enters the second chamber 3 through the first gap 7, the second gap 8, the second air guide channel 223 and the third gap 9. In addition, a portion of the gas enters the upper region of the moving iron core 23 through the gap between the moving iron core 23 and the sleeve 21, which can play a role in balancing the pressure.

[0026] Preferably, in this embodiment, the lower end of the valve core seat 221 is provided with a first mounting groove 2211 for mounting the valve core 2212. Preferably, in this embodiment, the first mounting groove 2211 is provided with a first limiting step 22111 and a second limiting step 22112 that cooperate with the valve core 2212. The valve core 2212 can slide axially between the first limiting step 22111 and the second limiting step 22112. The upper end face of the valve core 2212 is limited and cooperates with the first limiting step 22111. The outer side wall of the valve core 2212 is provided with a third limiting step 22121, which cooperates with the second limiting step 22112, thereby limiting the displacement stroke of the valve core 2212.

[0027] Preferably, in this embodiment, the cross-sectional area of ​​the upper end face of the valve core 2212 is larger than the cross-sectional area of ​​the lower end face of the valve core 2212, resulting in a larger pressure-bearing area on the upper end face of the valve core 2212 compared to the lower end face. Preferably, in this embodiment, the valve core 2212 is arranged in an inverted "convex" shape, allowing it to better adapt to different contact surfaces during installation and use, effectively improving its pressure-bearing performance and sealing effect.

[0028] Preferably, in this embodiment, the lower end of the stationary iron core 22 is provided with a fourth limiting step 224 that cooperates with the valve core seat 221 to limit the movement distance of the valve core seat 221 within the stationary iron core 22.

[0029] Preferably, in this embodiment, the lower end of the valve core seat 221 is provided with an installation step 2215, one end of the second spring 14 abuts against the installation step 2215, and the other end of the second spring 14 abuts against the valve body 1. The installation step 2215 provides a stable support surface, which facilitates the installation of the second spring 14. Preferably, the second spring 14 is a pagoda spring.

[0030] Preferably, in this embodiment, the outer diameter of the sleeve 21 is designed to be 10-12 mm. Preferably, in this embodiment, the outer diameter of the sleeve 21 is designed to be 11 mm. The selection of this design parameter is closely related to the pressure-bearing capacity of the solenoid valve. Specifically, if the solenoid valve is expected to bear higher pressure, the force of the pagoda spring must be increased. When the force of the pagoda spring increases, the electromagnetic coil 24 is required to generate a stronger magnetic force in the energized state to overcome the elastic force of the pagoda spring. However, in the prior art, the outer diameter of the sleeve 21 is generally designed to be 9 mm. This size limits the increase of magnetic force, and thus limits the force of the pagoda spring, thereby limiting the pressure-bearing capacity of the solenoid valve. In view of this, this embodiment increases the outer diameter of the sleeve 21 to 10-12 mm, preferably 11 mm, which effectively increases the magnetic force generated by the electromagnetic coil 24. The force of the pagoda spring can be increased. Based on this improvement, the pressure-bearing capacity of the solenoid valve is also significantly improved, meeting the requirements of higher working pressure.

[0031] The increased outer diameter of the sleeve 21 means a corresponding increase in the cross-sectional area of ​​the magnetic circuit. A larger magnetic circuit area allows for a wider path for magnetic flux, resulting in less flux loss and enabling more magnetic flux to pass through, thus generating a stronger magnetic force. Preferably, the sleeve 21 is made of copper, a non-magnetic material that cannot be magnetized. This means that during the operation of the solenoid valve, the sleeve 21 will not be magnetized by the magnetic field generated by the coil 24, thereby preventing interference with the magnetic field distribution inside the solenoid valve and ensuring the accuracy of the magnetic circuit design and magnetic force control. Copper also has excellent thermal conductivity, which helps to reduce the internal temperature of the solenoid valve and prevent performance degradation or damage due to overheating.

[0032] Preferably, in this embodiment, a pressure plate 4 is fixedly connected between the valve body 1 and the pilot valve assembly 2 to ensure the stability of the connection between the valve body 1 and the pilot valve assembly 2 and to prevent loosening or displacement caused by external factors.

[0033] Preferably, in this embodiment, an O-ring 5 is provided between the valve body 1 and the sleeve 21 to ensure the sealing performance between the valve body 1 and the sleeve 21. The sleeve 21 is provided with a second mounting groove 211 that corresponds to and cooperates with the O-ring 5 to facilitate the installation of the O-ring 5.

[0034] The working principle of this utility model is as follows: When the solenoid valve is not energized, the valve core assembly abuts against the fourth limiting step 224 of the stationary iron core 22 under the elastic force of the second spring 14 (pagoda spring). The downward force on the valve core 2212 comes from the elastic force of the first spring 22131, the gravity of the valve core 2212 itself, and the air pressure of the first chamber 2213. At the same time, the upward force on the valve core 2212 comes from the air pressure at the air inlet 11. Although the pressure-bearing area of ​​the upper end face of the valve core 2212 is greater than that of the lower end face of the valve core 2212, due to... The first gap 7 formed between the valve core seat 221 and the stationary iron core 22 is very small, resulting in a very small airflow into the first chamber 2213 and a very small air pressure acting on the upper surface of the valve core 2212. The upward force on the valve core 2212 is greater than the downward force on the valve core 2212, causing the valve core 2212 to abut against the first limiting step 22111, separating the valve core 2212 from the valve port 13, and opening the valve port 13. When the solenoid valve is energized, the moving iron core 23 moves downward and controls the valve core assembly to overcome the elastic force of the second spring 14 and move downward by a preset stroke L1 through the push rod 222. When the valve core seat 221 moves downward, at least a portion of the first gap 7 will increase, resulting in an increased airflow into the first chamber 2213 and an increased air pressure acting on the upper surface of the valve core 2212. The downward force on the valve core 2212 originates from the elastic force of the first spring 22131, the weight of the valve core 2212 itself, and the air pressure in the first chamber 2213. Simultaneously, the upward force on the valve core 2212 originates from the air pressure at the air inlet 11, and the pressure-bearing area on the upper surface of the valve core 2212 is greater than the pressure-bearing area on the lower surface of the valve core 2212. The upward force on valve core 2212 is less than the downward force on valve core 2212. The valve core 2212 moves downward by a stroke L2 relative to valve core seat 221. At this time, valve core 2212 abuts against the second limit step 22112, and valve core 2212 seals with valve port 13, and valve port 13 is closed. By adopting a segmented stroke design, the movement stroke of moving iron core 23 is cleverly shortened, so that the power required by coil 24 can be designed to be relatively small. This not only effectively reduces the temperature rise of coil 24, but also extends the energizing time of solenoid valve, improving the overall working efficiency and stability.

[0035] The above description is only a preferred embodiment of the present utility model. Therefore, all equivalent changes or modifications made to the structure, features and principles described in the claims of the present utility model patent application are included in the scope of the present utility model patent application.

Claims

1. A two-position two-way solenoid valve, comprising a valve body (1) and a pilot valve assembly (2), wherein the valve body (1) is provided with an air inlet (11) and an air outlet (12), and the valve body (1) is provided with a valve port (13) for connecting the air inlet (11) and the air outlet (12), characterized in that: The pilot valve assembly (2) includes a sleeve (21), a stationary iron core (22), a moving iron core (23), and a coil (24). The coil (24) is wound around the outer periphery of the sleeve (21). The stationary iron core (22) is fixedly disposed inside the sleeve (21). The moving iron core (23) is slidably disposed above the stationary iron core (22). A valve core assembly and a push rod (222) are movably disposed inside the stationary iron core (22). The moving iron core (23) abuts against the valve core assembly through the push rod (222). A second spring (14) is provided between the lower end of the valve core assembly and the valve body (1). The second spring (14) causes the valve core assembly to always have an upward movement tendency. The axial displacement stroke of the valve core assembly relative to the stationary iron core (22) is L1. The valve core assembly includes a valve core seat (221) and a valve core (2212). The valve core seat (221) is movably disposed in the stationary iron core (22) and abuts against the push rod (222). The valve core (2212) is movably disposed in the valve core seat (221). Furthermore, it is sealed and fitted with the valve port (13). The axial displacement stroke of the valve core (2212) relative to the valve core seat (221) is L2. A first gap (7) is formed between the valve core seat (221) and the stationary iron core (22). A first chamber (2213) is provided between the upper end face of the valve core (2212) and the valve core seat (221). A first spring (22131) is provided in the first chamber (2213). The first spring (22131) and the valve core (2212) are sealed together. The valve core (2212) is always inclined to move downwards. The first chamber (2213) is connected to the air inlet (11) through the first gap (7). When the valve core seat (221) moves down, at least part of the first gap (7) will become larger, which will increase the air flow rate into the first chamber (2213). When the valve core seat (221) moves up, at least part of the first gap (7) will become smaller, which will decrease the air flow rate into the first chamber (2213).

2. The two-position two-way solenoid valve according to claim 1, characterized in that: The valve core seat (221) is provided with a first air passage (2214) for connecting the first chamber (2213) and the first gap (7).

3. A two-position two-way solenoid valve according to claim 1, characterized in that: A second gap (8) is formed between the top rod (222) and the stationary iron core (22). A second air guide channel (223) is provided on the stationary iron core (22). A second chamber (3) is provided between the stationary iron core (22) and the moving iron core (23). A third gap (9) is provided between the stationary iron core (22) and the sleeve (21) for connecting the second air guide channel (223) and the second chamber (3).

4. A two-position two-way solenoid valve according to claim 1, characterized in that: The lower end of the valve core seat (221) is provided with a first mounting groove (2211) for mounting the valve core (2212).

5. A two-position two-way solenoid valve according to claim 4, characterized in that: A first limiting step (22111) and a second limiting step (22112) that cooperate with the valve core (2212) are provided in the first installation groove (2211). The valve core (2212) can slide between the first limiting step (22111) and the second limiting step (22112). The upper end surface of the valve core (2212) is in limiting cooperation with the first limiting step (22111). A third limiting step (22121) is provided on the outer side wall of the valve core (2212), and the third limiting step (22121) is in limiting cooperation with the second limiting step (22112).

6. A two-position two-way solenoid valve according to claim 1, characterized in that: The cross-sectional area of the upper end surface of the valve core (2212) is larger than the cross-sectional area of the lower end surface of the valve core (2212).

7. A two-position two-way solenoid valve according to claim 1, characterized in that: The valve core (2212) is arranged in an inverted "convex" shape.

8. A two-position two-way solenoid valve according to claim 1, characterized in that: The outer diameter of the sleeve (21) is designed to be 10 to 12 millimeters.

9. A two-position two-way solenoid valve according to claim 8, characterized in that: The outer diameter of the sleeve (21) is designed to be 11 millimeters.

10. A two-position two-way solenoid valve according to claim 1, characterized in that: A fourth limiting step (224) that is in limiting cooperation with the valve core seat (221) is provided at the lower end of the static iron core (22).

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