A solenoid valve body and a two-way solenoid valve

Abstract

The present application provides a solenoid valve body and a two-way solenoid valve, including a moving iron core component, a stationary iron core component, a first spring and a second spring located between the two. When the moving iron core component moves close to and engages with the stationary iron core component, the first spring and the second spring are compressed. When closing the valve, only the first spring is compressed; the stiffness of the second spring is greater than that of the first spring; the second spring sheathes the first spring, and there is a radial distance between the second spring and the first spring. The moving iron core component has a first end face facing the stationary iron core component, and a stepped counterbore is provided on the first end face. One end of the first spring abuts against the bottom wall of the stepped counterbore, and one end of the second spring abuts against the stepped surface of the stepped counterbore. The stiffness of the first spring in the present application can be reduced, and the requirement for the electromagnetic force provided by the coil component is reduced, so the structural size of the coil component can be reduced; and the two springs are not prone to interference and friction.

Description

Technical Field

[0001] The present invention relates to the technical field of fluid control, and particularly relates to a solenoid valve body and a two-way solenoid valve. Background Art

[0002] A two-way solenoid valve can achieve two-way flow, that is, it can enter from one interface and flow out from another interface, or it can flow in the reverse direction.

[0003] The two-way solenoid valve includes a moving iron core and a static iron core. When the coil component is energized, an electromagnetic force is generated, and the moving iron core moves towards the static iron core and moves away from the valve port to open the valve port; when the coil component is de-energized, the electromagnetic force disappears, and the moving iron core moves away from the static iron core under the restoring force of the spring, so as to approach the valve port to block the valve port and achieve valve closing. When switching from valve opening to valve closing, according to the different flow directions, the fluid on the high-pressure side may give a reverse acting force to the moving iron core, and the restoring force of the spring needs to overcome this reverse acting force. The spring needs to be designed with sufficient stiffness to ensure the smooth progress of valve closing; when the valve is closed, the spring still remains in a compressed state to press the moving iron core component against the valve port position. Then, when switching from valve closing to valve opening, the electromagnetic force of the coil component needs to overcome the restoring force of the spring. Due to the large stiffness of the spring, the coil component needs to be designed with a larger size, which is not conducive to the miniaturization of the structure of the two-way solenoid valve. Summary of the Invention

[0004] The present application provides a solenoid valve body, which includes a moving iron core component, a static iron core component, and a first spring and a second spring located between the two. When the moving iron core component moves close to and attracts the static iron core component, the first spring and the second spring are compressed. When the valve is closed, only the first spring is compressed; the stiffness of the second spring is greater than that of the first spring;

[0005] Moreover, the second spring sheathes the first spring, and there is a radial distance between the second spring and the first spring. The moving iron core component has a first end face facing the static iron core component, and a stepped counterbore is provided on the first end face. One end of the first spring abuts against the bottom wall of the stepped counterbore, and one end of the second spring abuts against the stepped surface of the stepped counterbore.

[0006] In a specific embodiment, the static iron core component has a second end face facing the moving iron core component, and a limiting hole is provided on the second end face. The other end of the first spring abuts against the bottom wall of the limiting hole.

[0007] In a specific embodiment, the other end of the second spring can abut against the second end face of the static iron core component.

[0008] In a specific embodiment, when the valve is closed, the first end face and the second end face have a first preset distance in the axial direction, and the second spring and the second end face of the static iron core have a second preset distance in the axial direction. The ratio range of the second preset distance to the first preset distance is 1 / 3 - 2 / 3.

[0009] In a specific embodiment, in the limiting hole and the stepped counterbore, the inner wall of the opening position of at least one of them is a tapered wall.

[0010] In a specific embodiment, the diameter of the first spring is smaller than the small hole diameter of the stepped counterbore and the diameter of the limiting hole, and the difference ranges are both 0.1mm - 0.2mm.

[0011] In a specific embodiment, the difference range of the diameter of the second spring and the diameter of the first spring is 0.4mm - 0.6mm.

[0012] In a specific embodiment, the diameter of the second spring is smaller than the large hole diameter of the stepped counterbore, and the difference range is 0.1mm - 0.2mm.

[0013] In a specific embodiment, the stiffness of the second spring is 4 - 6 times that of the first spring.

[0014] The present application also provides a two-way solenoid valve, including the solenoid valve body described in any one of the above, and further including a coil component.

[0015] By providing the second spring in the solenoid valve body of the present application, a large restoring force to overcome the inlet pressure can be provided at the beginning of the conversion from valve opening to valve closing. The stiffness setting of the first spring only needs to meet the requirement of providing a satisfactory valve closing force when the valve is closed, that is, the stiffness of the first spring can be reduced. And at the beginning of the conversion from valve closing to valve opening, since the second spring is not compressed, the elastic force overcome by the electromagnetic force only includes the elastic force of the first spring, and there is no need to overcome the elastic force of the second spring. In this way, the requirement for the electromagnetic force provided by the coil component is reduced, so the structural size of the coil component can be reduced, and the space occupancy rate of the solenoid valve body and the manufacturing cost of the solenoid valve body can be reduced. And by providing the stepped counterbore to limit and arrange the first spring and the second spring, the interference and friction between the two springs can be prevented, making the arrangement of the two springs possible, and ensuring the reliability of the solenoid valve body and extending its service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 It is a schematic structural diagram of the solenoid valve body in the embodiment of the present application;

[0017] Figure 2 For Figure 1 the schematic diagram of the valve seat core component in

[0018] Figure 3 is Figure 1 a schematic diagram of the moving iron core component;

[0019] Figure 4 is Figure 1 a schematic diagram of the solenoid valve body in the open valve state;

[0020] Figure 5 is Figure 1 an enlarged view of part A;

[0021] Figure 6 is Figure 1 an enlarged view of part B;

[0022] Figure 7 is Figure 1 a schematic diagram of the static iron core component.

[0023] Figure 1-7 The reference numerals in the figure are as follows:

[0024] 1 - valve seat core component; 11 - valve seat core; 111 - sealing surface; 11a - channel; 12 - valve seat core sleeve;

[0025] 2 - valve seat component; 21 - valve seat; 22 - sleeve;

[0026] 3 - moving iron core component; 3a - moving iron core body; 3b - sealing component; 31 - stepped counterbore; 311 - large hole; 312 - small hole; 311a - first conical wall; 312a - second conical wall; 32 - first end face;

[0027] 4 - static iron core component; 41 - limiting hole; 411 - bottom wall; 41a - third conical wall; 42 - second end face;

[0028] 5 - first spring;

[0029] 6 - second spring. Detailed implementation manners

[0030] In order to enable those skilled in the art to better understand the solution of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific implementation manners.

[0031] Please refer to Figure 1 , Figure 1 which is a schematic structural diagram of the solenoid valve body in the embodiment of the present application, Figure 1 and the solenoid valve body in it is in the closed valve state.

[0032] This embodiment provides a solenoid valve body, which includes a valve seat core component 1, a valve seat component 2, a moving iron core component 3, a static iron core component 4, and a first spring 5 and a second spring 6 located between the moving iron core component 3 and the static iron core component 4. As Figure 1As shown, the valve seat component 2 specifically includes a valve seat 21 and a sleeve 22. The valve seat core component 1 includes a valve seat core 11 and a valve seat core sleeve 12. A part of the static iron core component 4 is inserted into the sleeve 22 and fixed to the sleeve 22. A part of the valve seat core sleeve 12 is inserted into the valve seat 21 and fixed. That is, the static iron core component 4, the valve seat component 2, and the valve seat core component 1 are coaxially connected and fixed. The moving iron core component 3 is located inside the valve seat component 2 and the valve seat core component 1.

[0033] Please see again Figure 2 、 3 , Figure 2 is Figure 1 a schematic diagram of the valve seat core component 1 in Figure 3 is Figure 1 a schematic diagram of the moving iron core component 3 in

[0034] The valve seat core 11 is provided with an axially penetrating channel 11a. The upper opening of the channel 11a is a valve port. The upper end face of the valve seat core 11 forms a sealing surface 111. The moving iron core component 3 is specifically a split structure, including a moving iron core main body 3a and a sealing component 3b. The lower end of the moving iron core main body 3a is provided with a T-shaped end. The sealing component 3b is provided with a T-shaped hole for sleeving and positioning with the T-shaped end. The sealing component 3b can be a sealing plug structure made of an elastic material to have better sealing performance. When the end face of the sealing component 3b at the lower end of the moving iron core component 3 presses against the sealing surface 111 of the valve seat core 11, the valve port can be blocked. When the end face of the sealing component 3b separates from the sealing surface 111, the valve port opens.

[0035] This solenoid valve body is used in combination with a coil component (not shown in the figure). The coil component is usually arranged around the solenoid valve body. When the coil component is energized, a magnetic field is formed around the solenoid valve body. The moving iron core component 3 can move in the direction close to the static iron core component 4 under the action of electromagnetic force. In Figure 1 it moves axially upward. The moving iron core component 3 drives its sealing component 3b to separate from the valve port, and the valve port opens and is in the Figure 4 open valve state shown in Figure 4 is Figure 1 a schematic diagram of the solenoid valve body in the open valve state in Figure 1 When the coil component is de-energized, the magnetic field formed by the coil component disappears. The moving iron core component 3 moves away from the static iron core component 4 and moves downward under the restoring force of the first spring 5 and the second spring 6, driving its sealing component 3b to approach and finally press against the sealing surface 111 of the valve seat core component 1, realizing the blocking of the valve port, and thus being in the

[0036] Figure 2In this case, the valve seat core component 1 is provided with an opening 12a, which is specifically arranged in the valve seat core sleeve 12. In this embodiment, the solenoid valve body is the valve body of a two-way solenoid valve. Then, the fluid can enter the cavity of the valve seat core component 1 through the opening 12a, and when the valve port is opened, it flows to the channel 11a of the valve seat core component 1. Or, the fluid can also enter from the channel 11a and, when the valve port is opened, flow into the cavity of the valve seat sleeve 12 of the valve seat component 1 of the valve core and flow out through the opening 12a, that is, bidirectional flow is realized.

[0037] It should be emphasized that the springs providing the restoring force to drive the moving iron core component 3 to move close to the valve port in this embodiment include a first spring 5 and a second spring 6. And when the coil component is energized, the moving iron core component 3 moves towards the static iron core component 4 and engages with the static iron core component 4. That is, after the moving iron core component 3 moves to the maximum stroke towards the static iron core component 4, both the first spring 5 and the second spring 6 are compressed, and the compression amount is the largest, as Figure 4 shown. When the coil component is de-energized to close the valve, only the first spring 5 is compressed to provide the elastic force for closing the valve, while the second spring 6 is not compressed and is in a free state, as Figure 1 shown, and the upper end face of the second spring 6 does not contact other components. And, the stiffness of the second spring 6 is set to be greater than the stiffness of the first spring 5.

[0038] Please continue to refer to Figure 1 、 4 and, in combination with Figure 5 understand that Figure 5 is Figure 1 the enlarged view of part A in

[0039] As described above, in this embodiment, the first spring 5 and the second spring 6 are independently arranged, and during the axial movement of the moving iron core component 3, their compression states are not the same. To ensure that the first spring 5 and the second spring 6 play their respective functions without interfering with each other, as Figure 5 shown, the diameter of the second spring 6 is larger than the diameter of the first spring 5. The second spring 6 is sleeved outside the first spring 5, and there is a radial distance between the second spring 6 and the first spring 5 to limit the mutual interference and friction between the first spring 5 and the second spring 6 during the deformation process. The difference range of the diameters of the second spring 6 and the first spring 5 can be 0.4 mm - 0.6 mm. Of course, according to requirements such as the model size and compression deformation amount of the spring, this difference range can also be adjusted.

[0040] Furthermore, as Figure 2 shown, the moving iron core component 3 has a first end face 32 facing the static iron core component 4, and the first end face 32 is provided with a stepped counterbore 31. Figure 5In this case, one end of the first spring 5 abuts against the bottom wall 314 of the stepped counterbore 31, and one end of the second spring 6 abuts against the stepped surface 313 of the stepped counterbore 31. That is, the first spring 5 is restricted within the small hole 312 of the stepped counterbore 31, and the second spring 6 is restricted within the large hole 311 of the stepped counterbore 31, so as to further ensure that the first spring 5 and the second spring 6 maintain a necessary radial distance and do not interfere with each other.

[0041] In addition, the first spring 5 has a relatively small stiffness and needs to be compressed all the time. Therefore, it is set to have more turns and a longer length. At this time, if the diameter of the first spring 5 is set to be smaller, the small hole 312 of the stepped counterbore 31 can serve as the limiting cavity for the first spring 5. In this way, the stepped counterbore 31 machined on the moving iron core component 3 occupies a small space and will not affect the magnetic flux area of the moving iron core component 3. As Figure 4 shown, the upper end of the moving iron core component 3 has a step. The moving iron core body 3a of the moving iron core component 3 is divided into a large-diameter part 3a1 and a small-diameter part 3a2. The large-diameter part 3a1 is fitted with the inner wall of the sleeve of the valve seat assembly 2, and the small-diameter part 3a2 is fitted with the inner wall of the valve seat of the valve seat component 2 and the inner wall of the sleeve of the valve core seat component 1. The large hole 311 of the stepped counterbore 31 is opened in the large-diameter part 3a1 of the moving iron core component 3, and the small hole of the stepped counterbore 31 is opened in the small-diameter part 3a2 of the moving iron core component 3. Such a distribution further avoids or reduces the influence on the magnetic flux area of the moving iron core component 3.

[0042] In this embodiment, the first spring 5 and the second spring 6 are provided. In the initial state, no spring force of the second spring 6 acts on the moving iron core component 3, and only the first spring 5 is compressed. When the coil component is energized instantaneously, the coil component generates an electromagnetic force. Under the action of the electromagnetic force, the moving iron core component 3 overcomes the restoring force of the first spring 5 and moves upward to approach the static iron core component 4. The moving iron core component 3 continues to move upward. The static iron core component 4 has a second end face 42 facing the moving iron core component 3. When the moving iron core component 3 moves a certain stroke, the upper end face of the second spring 6 starts to contact the second end face 42 of the static iron core component 4. As the moving iron core component 3 moves upward, the distance between the moving iron core component 3 and the static iron core component 4 decreases, and the electromagnetic force becomes larger. Moreover, during the upward movement of the moving iron core component 3, under the action of the electromagnetic force, it has a certain kinetic energy. Therefore, under the action of the increasing electromagnetic force and kinetic energy, the moving iron core component 3 can overcome the acting forces generated by the first spring 5 and the second spring 6 at the same time and continue to move upward until the first end face 32 of the moving iron core component 3 abuts against the second end face 42 of the static iron core component 4, being in the valve-opening state.

[0043] When the passage 11a of the valve seat core component 1 serves as the inlet, the pressure inside the passage 11a is high, and when the solenoid valve body is in the open valve state, at the moment when the coil component is powered off, the electromagnetic force on the solenoid valve body disappears. The moving iron core component 3 moves downward under the combined action of the first spring 5 and the second spring 6, overcoming the upward force of the high-pressure fluid at the inlet acting on the moving iron core component 3. When the downward moving stroke is equal to the compression amount of the second spring 6 and continues to move downward, the upper end surface of the second spring 6 will separate from the second end surface 42 of the static iron core component 4. At the moment of separation, the acting force of the second spring 6 disappears. At this time, relying only on the acting force of the first spring 5 is actually not enough to overcome the reverse acting force of the inlet pressure acting on the moving iron core component 3. However, the moving iron core component 3 can obtain a large acceleration during the just movement process and has obtained a large kinetic energy. Therefore, under the action of the kinetic energy and the first spring 5, the moving iron core component 3 continues to move, overcoming the reverse acting force upward of the moving iron core component 3 until its sealing component 3b contacts the sealing surface 111 of the valve port, closing the valve port.

[0044] When closing the valve, reference can be made to Figure 6 for understanding. Figure 6 It is Figure 1 the enlarged view of part B in

[0045] At this time, the area of the high-pressure side of the passage 11a acting on the sealing component 3b is the area S1 of the valve port. When the valve port is open, the area of the high-pressure side fluid acting on the sealing component 3b is the area S2 of the lower end surface of the sealing component 3b. Obviously, S2 is greater than S1. Therefore, after the sealing component 3b closes the valve, although the moving iron core component 3 stops moving and the kinetic energy is eliminated, since the force-bearing area is reduced to S1, the compression elastic force of only the first spring 5 can overcome the fluid reaction force on the high-pressure side, enabling the sealing component 3b to reliably press against the valve port to achieve sealing.

[0046] It can be seen that in this embodiment, due to the introduction of the second spring 6, a large restoring force to overcome the inlet pressure can be provided at the beginning of the conversion from the open valve to the closed valve. The stiffness setting of the first spring 5 only needs to meet the requirement of providing a closing force when closing the valve, that is, the stiffness of the first spring 5 can be reduced. At the beginning of the conversion from the closed valve to the open valve, since the second spring 6 is not compressed, the elastic force overcome by the electromagnetic force only includes the elastic force of the first spring 5 and does not need to overcome the elastic force of the second spring 6. In this way, the requirement for the electromagnetic force provided by the coil component is reduced, so the structural size of the coil component can be reduced, and the space occupancy rate of the solenoid valve body and the manufacturing cost of the solenoid valve body can be reduced. By setting the stepped counterbore 31 to limit the arrangement of the first spring 5 and the second spring 6, interference and friction between the two springs can be prevented, making the arrangement of the two springs possible and ensuring the reliability of the solenoid valve body and extending its service life.

[0047] When the fluid enters from the opening 12a and flows out from the channel 11a, the channel 11a is the low-pressure side. When switching from the open valve to the closed valve, there is no need to overcome the reverse force of the high-pressure fluid. The above settings still meet the requirements, that is, the setting method of this embodiment meets the two-way flow requirements. Of course, the solenoid valve body in this embodiment is not limited to a two-way solenoid valve, and a one-way solenoid valve can also be applicable.

[0048] Further, as Figure 7 shown, Figure 7 is Figure 1 a schematic diagram of the middle static iron core component 4.

[0049] The static iron core component 4 has a second end face 42 facing the moving iron core component 3. The second end face 42 is provided with a limiting hole 41. The other end of the first spring 5 abuts against the bottom wall of the limiting hole 41, that is, the two ends of the first spring 5 respectively abut against the bottom wall 313 of the stepped counterbore 31 and the bottom wall 411 of the limiting hole 41. This can better limit the position of the first spring 5 and prevent it from interfering and rubbing with the second spring 6. Moreover, the first spring 5 is always in a compressed state during the operation of the solenoid valve body, and the two-end limit is more conducive to the stability of its position.

[0050] In this embodiment, one end of the second spring 6 abuts against the step surface 314 of the stepped counterbore 31, and the other end can abut against the second end face 42 of the static iron core component 4 when the valve is opened. The second spring 6 only abuts against the static iron core component 4 after a certain stroke of opening the valve. Making it directly abut against the second end face 42 of the static iron core component 4 can meet the positioning requirements and the processing is relatively simple. Of course, a ring groove structure can also be provided on the second end face 42 of the static iron core component 4 to limit the abutting limit of the static iron core component 4 in the open valve state.

[0051] As Figure 1 shown, in this embodiment, the first end face 32 of the moving iron core component 3 and the second end face 42 of the static iron core component 4 have a first preset distance L1 in the axial direction. The upper end face of the second spring 6 and the second end face 42 of the static iron core component 4 have a second preset distance L2 in the axial direction. Among them, the ratio range of the second preset distance L2 to the first preset distance L1 is 1 / 3 - 2 / 3. The second preset distance L2 is less than the first preset distance L1 to ensure that the upper end face of the second spring 6 protrudes from the first end face 32 of the moving iron core component 3, ensuring that the second spring 6 is not entirely located in the stepped counterbore 31, so that it can abut against the second end face 42 of the static iron core component 4. The second preset distance L2 being 1 / 3 - 2 / 3 of the first preset distance can ensure that after the moving iron core component 3 moves upward a certain distance, the upper end face of the second spring 6 can contact the second end face 42 of the static iron core component 4.

[0052] As shown in the figure, among the limiting hole 41 and the stepped counterbore 31, the inner wall at the opening position of at least one of them is a tapered wall. The limiting hole 41 has one opening, and both the large hole 311 and the small hole 312 of the stepped counterbore 31 have opening positions, and the first tapered wall 311a, the second tapered wall 312a, and the third tapered wall 41a are respectively provided. The first spring 5 and the second spring 6 will be frequently compressed and deformed, generating an axial displacement. The tapered wall is provided to reduce the wear at the opening position during the deformation process of the first spring 5 and the second spring 6.

[0053] In this embodiment, the diameter of the first spring 5 is smaller than the aperture of the small hole 312 of the stepped counterbore 31 and the aperture of the limiting hole 41, and the difference range can be 0.1 mm - 0.2 mm. This difference range is the design clearance between the first spring 5 and the stepped counterbore 31 and the limiting hole 41. When the spring is compressed, the outer diameter will increase. This difference range can allow the compression deformation of the first spring 5 and also meet the limiting function of the stepped counterbore 31 and the limiting hole 41 on the first spring 5. If the difference is too large, the limiting of the first spring 5 is unstable and it is easy to shake. If the difference is too small, it may affect the compression deformation of the first spring 5. The compression amount of the first spring 5 in this embodiment is relatively small, the change in the outer diameter is very small, and the design clearance is relatively small. Similarly, the diameter of the second spring 6 is smaller than the aperture of the large hole 311 of the stepped counterbore 31, and the difference range is 0.1 mm - 0.2 mm. It is mentioned above that the difference range between the diameter of the second spring 6 and the diameter of the first spring 5 can be 0.4 mm - 0.6 mm. When the difference in the spring diameter takes a large value, the above-mentioned design clearance also takes a large value. When the difference in the spring diameter takes a small value, the design clearance also takes a small value.

[0054] In addition, in this embodiment, the stiffness of the second spring 6 can be 4 - 6 times that of the first spring 5. When the coil component is powered off and the electromagnetic force disappears, a sufficient large restoring force is provided to overcome the reverse acting force of the fluid on the moving iron core component 3. Then, on the premise of providing the closing valve elastic force, the stiffness of the second spring 3 is designed to be as small as possible, and the size of the coil component can be minimized.

[0055] In this article, specific examples are used to elaborate on the principle and implementation manner of the present invention. The description of the above embodiments is only used to help understand the method of the present invention and its core idea. It should be noted that for those of ordinary skill in the art in this technical field, without departing from the principle of the present invention, several improvements and modifications can be made to the present invention, and these improvements and modifications also fall within the protection scope of the claims of the present invention.

Claims

1. A solenoid valve body, characterized in that, It includes a moving iron core component and a stationary iron core component, as well as a first spring and a second spring located therebetween. When the moving iron core component moves closer to and engages with the stationary iron core component, the first spring and the second spring are compressed. When closing the valve, only the first spring is compressed; the stiffness of the second spring is greater than that of the first spring. Moreover, the second spring sheathes the first spring, and there is a radial spacing between the second spring and the first spring. The moving iron core component has a first end face facing the stationary iron core component, and a stepped counterbore is provided on the first end face. One end of the first spring abuts against the bottom wall of the stepped counterbore, and one end of the second spring abuts against the stepped surface of the stepped counterbore.

2. The solenoid valve body according to claim 1, wherein, The stationary iron core component has a second end face facing the moving iron core component, and a limiting hole is provided on the second end face. The other end of the first spring abuts against the bottom wall of the limiting hole.

3. The solenoid valve body according to claim 2, wherein, The other end of the second spring can abut against the second end face of the stationary iron core component.

4. The solenoid valve body according to claim 3, characterized in that, When closing the valve, there is a first preset distance in the axial direction between the first end face and the second end face, and there is a second preset distance in the axial direction between the second spring and the second end face of the stationary iron core. The ratio range of the second preset distance to the first preset distance is 1 / 3 - 2 / 3.

5. The solenoid valve body according to claim 2, characterized in that Among the limiting hole and the stepped counterbore, the inner wall of the opening position of at least one of them is a tapered wall.

6. The electromagnetic valve body according to claim 2, wherein, The diameter of the first spring is smaller than the small hole diameter of the stepped counterbore and the diameter of the limiting hole, and the difference ranges are both 0.1 mm - 0.2 mm.

7. The solenoid valve body according to any one of claims 1-6, characterized in that, The difference range of the diameter of the second spring and the diameter of the first spring is 0.4 mm - 0.6 mm.

8. The solenoid valve body according to any one of claims 1-6, characterized in that, The diameter of the second spring is smaller than the large hole diameter of the stepped counterbore, and the difference range is 0.1 mm - 0.2 mm.

9. The solenoid valve body according to any one of claims 1-6, characterized in that, The stiffness of the second spring is 4 - 6 times that of the first spring.

10. A two-way solenoid valve, characterized in that, It includes the solenoid valve body according to any one of claims 1 - 9, and further includes a coil component disposed around the solenoid valve body.

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