WO2012126368A1 - Two-way electromagnetic valve - Google Patents

Abstract

Disclosed is a two-way electromagnetic valve, which comprising a valve seat (1) provided with a main valve port (11) and a valve chamber. A piston (2) is provided in the valve chamber, and the valve chamber is divided into an upper chamber (12) and a lower chamber (13) by the piston (2). A pilot valve port (21) is provided in the upper end of the piston (2). A flowing gap (14) is provided between the circumferential sidewall of the piston (2) and the corresponding inner wall of the valve chamber. A first branch are provided in the piston, which can connect one-way the upper chamber (12) to an end of a transverse joint pipe (31), and a second branch which can connect one-way the upper chamber (12) to an end of a vertical joint pipe (32). A third branch which can connect one-way the end of the vertical joint pipe (32) to the upper chamber (12) is also provided in the piston. The structure of the two-way electromagnetic valve can reduce the number of components, simplify the assembly process and reduce the manufacturing cost.

Description

 A two-way solenoid valve is claimed in the Chinese Patent Application No. 201110069844.8, the entire disclosure of which is incorporated herein by reference. In this application. Technical field

 The invention relates to the technical field of electromagnetic valves, and in particular to a two-way electromagnetic valve. Background technique

 General solenoid valves, due to structural constraints, can only be circulated and cut off in one direction. In an air conditioning system, particularly a heat pump system, the flow direction of the refrigerant during cooling and heating is reversed, so that a general single-energized magnetic valve needs to be used in conjunction with a one-way valve. However, the two-way solenoid valve can realize double-conducting and cut-off, so it can be directly used in the system pipeline without using the one-way valve, so it has obvious cost advantages.

 In the prior art, a two-way solenoid valve is disclosed in the Japanese Patent Laid-Open No. Hei 6-110780. For details, please refer to FIG. 1 and FIG. 2. FIG. 1 is a schematic structural view of a two-way electromagnetic valve in the prior art; 1 is a schematic structural view of a first check valve and a second check valve of the two-way solenoid valve of FIG. 1; FIG. 3 is a partial structure of a piston, a first check valve and a second check valve of the two-way electromagnetic valve of FIG. schematic diagram.

 The working process of the prior art two-way solenoid valve is as follows:

Positive closed state: As shown in Fig. 1 and Fig. 3, when the coil 4'4 of the solenoid valve is not energized, when the cross tube 3'2 is connected to the high pressure refrigerant, the high pressure refrigerant enters the piston through the balance hole 2'3 of the piston 2'. Internally, the high-pressure refrigerant opens the first pilot port 2Ί sealed by the first check valve 5Ί, enters the upper chamber 1'2 of the valve seat 1' above the piston 2', and the high-pressure refrigerant fills the entire upper chamber 1'2; When the second check valve 5'2 seals the second pilot valve port 2'2 under the action of the high pressure refrigerant in the upper chamber 1'2, the upper chamber 1'2 is a high pressure end; The force area of the piston 2' in the cavity 1'2 is larger than the force receiving area of the piston 2' in the lower chamber 1'3 of the valve seat 1', and since the vertical end of the vertical tube 3 is the low pressure end, under the action of the pressure difference , the piston 2' closes the main valve port 1 of the seat Γ, and the solenoid valve is closed. Positive opening state: As shown in Fig. 1 and Fig. 3, when the solenoid valve coil 4'4 is energized, the moving iron core 4'2 in the sleeve 4Ί moves upward under the action of the solenoid valve force, and the static iron core 4 '3 pull-in, the moving iron core 4'2 moves upwards after an idle stroke, the support body 5' is moved upwards, and the support body 5' drives the second check valve 5'2 to open the second pilot valve port 2'2; At this time, the high-pressure refrigerant passes through the second pilot port 2'2, and then the check valve core 2'4 is opened, and enters the 管-end of the vertical pipe, because the flow area of the balance hole 2'3 on the piston 2' is smaller than the second The flow area of the pilot port 2'2, so that the pressure in the upper chamber 1 '2 drops, forming a low pressure end, at this time the lower chamber 1 '3 is a high pressure end, under the action of the pressure difference, the piston 2' moves upward, opens The main valve port is 1Ί and the solenoid valve is open.

 Reverse closed state: When the coil 4'4 is not energized, as shown in Fig. 1 and Fig. 3, when the cross pipe 3'2 passes the high pressure refrigerant, the high pressure refrigerant passes through the one-way spool 2'4 inside the piston 2' The small hole enters the second pilot valve port 2'2, and opens the second pilot valve port 2'2 sealed by the second check valve 5'2, into the upper chamber 1'2, at which time the high pressure refrigerant fills the entire upper chamber 1'2, and because the first check valve 5Ί closes the first pilot port 2Ί under the action of the high pressure refrigerant in the upper chamber 1'2, the upper chamber 1'2 forms a high pressure end; at this time, the upper chamber 1'2 And the vertical pipe 3Ί-end is a high-pressure end, but the force area of the piston 2' in the upper chamber 1'2 is larger than the force-receiving area of the piston 2' determined by the vertical pipe 3Ί-end main valve port 1Ί, and The cavity 1'3 and the cross-over pipe 3'2-end are low-pressure ends, so that under the action of the pressure difference, the piston 2' closes the main valve port 1Ί, and the solenoid valve is closed.

 Reverse open state: When the coil 4'4 is energized, as shown in Fig. 1 and Fig. 3, the moving iron core 4'2 moves upward under the action of the electromagnetic valve force, and is sucked with the static iron core 4'32, and the dynamic core iron After the 4'2 moves upward for an idle stroke, the support body 5' is moved upward, and the support body 5' drives the first check valve 5Ί to open the first pilot valve port 2Ί, and the high pressure refrigerant in the upper chamber 1'2 passes through the first The pilot port 2Ί and the balance hole 2'3 flow into the cross-section 3'2-end; at this time, since the flow area of the small hole on the one-way spool 2'4 is smaller than the flow area of the balance hole 2'3, The pressure in the chamber 1 '2 drops, forming a low pressure end. At this time, the 竖-end of the vertical tube 3 is still a high pressure end. Under the action of the pressure difference, the piston 2' moves upward, opens the main valve port 1 Ί, and the solenoid valve opens.

 However, the above-described prior art solenoid valve has the following disadvantages:

First, in order to realize the bidirectional opening or closing of the solenoid valve, the piston 2' is provided with two pilot ports: a first pilot port 2Ί and a second pilot port 2'2, and correspondingly, a support body 5' is provided. Two check valves: the first check valve 5Ί and the second check valve 5'2, resulting in more parts and complicated structure; Secondly, in order to ensure that the two check valves are respectively engaged with the corresponding pilot ports, it is necessary to prevent the support body 5' from rotating in the circumferential direction; in view of this, as shown in FIG. 2, it is necessary to provide two on the support body 5'. The positioning rods 5'3 are correspondingly provided with two positioning holes on the piston that cooperate with the positioning rods 5'3, thereby preventing the rotation of the support body 5'. However, this kind of structural design not only leads to more parts, but also has difficulty in processing, complicated assembly process and high manufacturing cost;

 Third, it can be seen from the above two defects that the prior art solenoid valve components are numerous, the assembly process is complicated, and the assembly is difficult, so that the reliability of the work is relatively poor. Summary of the invention

 The technical problem to be solved by the present invention is to provide a two-way electromagnetic valve. The structural design of the two-way electromagnetic valve can significantly reduce the number of components, the assembly process, reduce the manufacturing cost, and improve the reliability of the work. .

 In order to solve the above technical problem, the present invention provides a two-way electromagnetic valve including a valve seat provided with a main valve port and a valve chamber, wherein the valve chamber is provided with a piston that cooperates with the main valve port, and the piston separation chamber The valve chamber is an upper chamber and a lower chamber, and an upper end portion of the piston is provided with a guide opening opened or closed by a pilot valve member; the two-way electromagnetic wide includes a cross tube communicating with the lower chamber, and passing a vertical pipe communicating with the lower chamber; a circumferential gap between the circumferential side wall of the piston and an inner wall of the corresponding valve cavity; the piston is provided with the valve port a first branch that is openable from the upper chamber to the end of the cross tube, and a second branch that can be single-passed from the upper chamber to the end of the vertical tube; the piston is further provided a third branch that can be unidirectionally guided to the upper chamber by one end of the vertical pipe; a flow area determined by the guide opening and the second branch is larger than a flow area of the flow gap, the pilot valve The flow area determined by the mouth and the first branch is greater than Three branch flow area.

 Preferably, the piston further has an open channel communicating with the open port in the axial direction, and the open port is respectively connected to the first branch and the second branch through the open channel Single-pass.

Preferably, the first branch includes a first radial hole, one end of the first radial hole is in communication with the pilot valve passage, and the other end thereof is connected to a second radial hole having a larger opening diameter; a radial sealing surface is disposed between the two radial holes and the first radial hole, and the second radial hole is provided with a sealing surface a radial sealing body facing the sealing surface; a radial stopping member is disposed at one end of the second radial hole away from the radial sealing surface, and the radial stopping member is provided to communicate with the second radial hole a radial through hole with one end of the cross tube.

 Preferably, the second radial hole is a circular hole, the small diameter end of the circular hole is connected to the radial sealing surface, and the large diameter end is connected with a third radial hole having a larger diameter, the radial stop The component is assembled in the third radial bore.

 Preferably, the second branch includes an axial cavity communicating with the open channel, and a first axial sealing surface is disposed between the axial cavity and the pilot passage, the axial cavity a first axial sealing body sealing the first axial sealing surface is disposed in the body; a first axial stopping member is disposed at an end of the axial cavity away from the first axial sealing surface, and the first The axial stop member is provided with a first axial through bore that communicates the axial cavity with one end of the riser tube.

 Preferably, the first axial sealing body is a one-way valve core, and the one-way valve core is provided with a wide core radial hole and a wide core axial hole communicating with each other, the wide core radial hole and the The axial cavity is in communication, and the spool axial bore is in communication with the first axial through bore.

 Preferably, one end of the axial cavity away from the first axial sealing surface is connected with a first axial hole having a larger diameter, the piston is provided with a riveting portion, and the first axial stopping member passes The rivet is riveted into the first axial bore.

 Preferably, the third branch includes a second axial hole communicating with one end of the vertical pipe, and the other end of the second axial hole communicates with a third axial hole having a larger diameter; a second axial sealing surface is disposed between the hole and the third axial hole, and a second axial sealing body sealing the second axial sealing surface is disposed in the third axial hole; the third axial hole a second axial stopping member is disposed at one end away from the second axial sealing surface, and the second axial stopping member is provided with a second axial through hole communicating with the third axial hole and the upper cavity .

 Preferably, the piston is further provided with an inclined hole, and the second axial hole communicates with one end of the vertical pipe through the inclined hole.

 Preferably, the guide member comprises a sleeve connected to the wide seat, the sleeve is provided with a moving iron core, and one end of the movable iron core is connected with a pilot valve for sealing or opening the pilot valve port. The ball has the other end connected to the static iron core through an elastic member, and the outer portion of the sleeve is provided with a coil.

Preferably, the first branch includes a radial pipe, and the radial pipe is provided with a radial sealing surface And a radial sealing body matched with the radial sealing surface; a guiding seat for moving the radial sealing body along a radial direction of the piston is further disposed in the radial pipeline, and the guiding seat is provided A guide seat passage connecting one end of the cross pipe and the radial pipe.

 Preferably, the radial duct includes a first radial hole and a second radial hole having a larger aperture, the radial sealing surface being formed in the first radial hole and the second radial hole The guide seat is disposed in the second radial hole and guides to support the radial sealing body to move along the radial direction of the piston to seal or open the radial sealing surface.

 Preferably, the guide seat is a cylinder having an opening at one end, and the radial sealing body is disposed in a cavity of the cylinder of the cylinder, the cylinder having the opening facing the radial sealing surface, The radial sealing body opens or closes the radial sealing surface; the guiding seat passage is formed on a circumferential side wall of the cylinder and communicates with the cylindrical cavity and the second radial hole The tube gap.

 Preferably, the barrel notch further extends to the bottom sealed end of the barrel such that there is a conduction gap between the bottom sealed end of the barrel and the inner wall of the second radial hole.

 Preferably, the cylinder is interference fit in the second radial bore with its circumferential side wall.

 Preferably, the inner wall of the valve seat is provided with a valve seat guiding section, and a circumferential guiding outer wall of the piston is provided with a piston guiding section that cooperates with the valve seat guiding section; an outer diameter is opened below the piston guiding section a small pipe mounting section, the first branch includes a radial pipe, the radial pipe is opened on the pipe installation section; and a lower groove is further formed in a lower portion of the valve seat guiding section And when the piston opens the main wide opening, the radial pipeline as a whole is within a range directly facing the annular groove.

 Preferably, the two-way electromagnetic wide includes an elastic member, and a step is formed between the piston guiding section and the pipe mounting section; the elastic component is sleeved on a circumferential outer portion of the lower portion of the piston, and is elastically supported Between the step and the inner bottom wall of the valve seat.

On the basis of the prior art, the circumferential side wall of the piston of the two-way electromagnetic valve provided by the present invention has a flow gap between the corresponding inner wall of the valve cavity; the piston is provided with the guide a first branch that communicates with the valve port and can be unidirectionally guided from the upper chamber to one end of the cross tube, and a second branch that can be unidirectionally guided from the upper chamber to the end of the vertical tube; Providing a third branch that can be unidirectionally guided from one end of the vertical pipe to the upper cavity; a flow area determined by the pilot port and the second branch is larger than a flow area of the flow gap, Pilot valve port and station The flow area determined by the first branch is larger than the flow area of the third branch.

 When the coil of the two-way solenoid valve is not energized, when the high pressure refrigerant enters the lower chamber of the valve chamber by the cross tube, the first branch is closed, and the refrigerant enters the upper chamber above the piston through the flow gap, in the role of high pressure refrigerant and gravity. Next, the pilot valve member closes the pilot valve port. At this time, since the upper chamber and the lower chamber are both high pressure ends, and because the force receiving area of the piston in the upper chamber is larger than the force receiving area of the piston in the lower chamber, and because the end of the vertical tube is low pressure The end, thus the piston moves downward under the pressure difference, closing the main valve port. When the coil of the two-way solenoid valve is energized, under the action of the magnetic field, the pilot valve member opens the pilot valve port, and the high-pressure refrigerant in the upper chamber flows into the low-pressure vertical pipe through the pilot valve port and the second branch, due to the pilot valve port and The flow area determined by the second branch is larger than the flow area of the flow gap, so that the pressure in the upper chamber is lowered to form a low pressure end, and the lower chamber is a high pressure end, and the piston is pressed upward by the pressure difference between the lower chamber and the upper chamber. Exercise, open the main valve port, and the solenoid valve opens. When the coil is de-energized, the magnetic field disappears and the pilot valve member is reset to close the pilot port. At this time, the refrigerant in the upper chamber no longer flows through the pilot port and the second branch to the end of the vertical pipe, so the pressure in the upper chamber rises until The pressure of the high pressure refrigerant at one end of the cross tube is equal; at this time, the upper chamber and the lower chamber of the piston are both high pressure ends, but the force receiving area of the piston in the upper chamber is larger than the force receiving area of the piston in the lower chamber, and because one end of the vertical tube is At the low pressure end, the piston moves downwards under the pressure difference, closing the main valve port and closing the solenoid valve.

When the coil of the two-way solenoid valve is not energized, when the high-pressure refrigerant enters from one end of the vertical pipe, the second branch is closed, and the high-pressure refrigerant enters the upper chamber through the third branch, and the pilot valve member is closed under the action of high-pressure refrigerant and gravity. The pilot valve port, the upper chamber and the vertical pipe are both high-pressure ends, but the force receiving area of the piston in the upper chamber is larger than the force receiving area of the piston determined by the main valve port at one end of the vertical pipe, and because the one end and the lower cavity of the cross pipe are At the low pressure end, the piston closes the main valve port and the solenoid valve closes under the pressure difference. When the coil is energized, under the action of the magnetic field, the pilot valve member opens the pilot valve port, and the high pressure refrigerant in the upper chamber flows through the pilot valve port and the first branch to the low pressure cross tube end, due to the pilot port and the first The flow area determined by the branch is larger than the flow area of the third branch, so the pressure in the upper chamber is lowered, which is called the low pressure end. At this time, under the action of the pressure difference, the piston moves upward, the main valve port is opened, and the solenoid valve is opened. . When the coil is de-energized, the magnetic field disappears and the pilot valve member is reset to close the pilot valve port. At this time, the high-pressure refrigerant in the upper chamber can no longer flow through the pilot valve port and the first branch to the low-pressure cross-connecting tube, so the pressure rises and forms. a high pressure end equal to one end of the vertical pipe, but since the force receiving area of the piston in the upper chamber is larger than the force receiving area of the piston determined by the main valve port at one end of the vertical pipe, And because one end of the cross pipe and the lower cavity are low pressure ends, the piston closes the main valve port under the action of the pressure difference, and the solenoid valve is closed.

 Compared with the prior art two pilot valve ports and two check valves, the two-way solenoid valve of the present invention is provided with only one pilot valve port and pilot valve member, thereby reducing the number of components and assembling the assembly. In addition, since the invention does not adopt the structural design of the two check valves, the structure of the support body is omitted, and the structure of the two positioning rods which are prevented from rotating by the support body is also eliminated, and accordingly, The structure of the two positioning holes is also omitted on the piston, thereby not only reducing the number of components, but also reducing the processing difficulty and assembly difficulty; since the two-way solenoid valve of the invention has fewer components, the assembly process is less difficult, Therefore, the reliability of its work is correspondingly improved.

 In summary, the two-way electromagnetic valve provided by the invention can significantly reduce the number of components, the assembly process, reduce the manufacturing cost, and improve the reliability of the work. DRAWINGS

 1 is a schematic structural view of a two-way electromagnetic valve in the prior art;

 Figure 2 is a schematic view showing the structure of the first check valve and the second check valve of the two-way solenoid valve of Figure 1; Figure 3 is a view of the piston of the two-way solenoid valve of Figure 1, the first check valve and the second check valve Schematic diagram of local structure;

 4 is a schematic structural view of a two-way electromagnetic valve according to an embodiment of the present invention;

 Figure 5 is a schematic view showing the structure of the piston of the two-way electromagnetic valve of Figure 4;

 6 is a schematic structural view of a two-way electromagnetic valve according to another embodiment of the present invention;

 Figure 7 is a schematic structural view of the piston of the two-way solenoid valve of Figure 6;

 Figure 8 is a front plan view of the piston of Figure 7;

 Figure 9 is a schematic structural view of the cylinder of the piston of Figure 7;

 FIG. 10 is a schematic structural view of a two-way electromagnetic valve according to still another embodiment of the present invention. Wherein, the correspondence between the reference numerals and the component names in FIGS. 1 to 3 is:

 Γ valve seat; 1 Ί main valve port; Γ 2 upper chamber; Γ 3 lower chamber;

2'piston; 2Ί first pilot port; 2'2 second pilot port; 2'3 balance hole; 2'4 check valve; 3'2 transverse pipe; 3Ί vertical pipe;

 4Ί casing; 4'2 moving iron core; 4'3 static iron core; 4'4 coil;

 5' support; 5Ί first check valve; 5'2 second check valve; 5'3 positioning rod.

 The correspondence between the reference numerals and the part names in Figures 4 to 10 is:

 1 valve seat; 11 main valve port; 12 upper cavity; 13 lower cavity; 14 flow gap; 15 valve seat guiding section;

16 annular groove;

 2 piston; 21 pilot valve port; 22 pilot valve passage; 26 rivet joint; 27 piston guide section; 28 pipe installation section; 29 steps;

 231 first radial hole; 232 second radial hole; 233 radial sealing surface; 234 radial sealing body; 235 radial stopping member; 235a radial through hole; 236 third radial hole; 237 cylinder; 237a barrel lumen; 237b tube gap; 237c conduction gap;

241 axial cavity; 242 first axial sealing surface; 243 first axial stopping member; 243a first axial through hole; 244 one-way spool; 244a spool radial hole; 244b spool axial hole ; 245 first axial hole;

 251 oblique hole; 252 second axial hole; 253 third axial hole; 254 second axial sealing surface; 255 second axial sealing body; 256 second axial stopping member; 256a second axial through hole ;

 31 transverse pipe; 32 vertical pipe;

 41 casing; 42 moving iron core; 43 pilot valve sphere; 44 elastic parts; 45 static iron core; 46 coil. ; wide sealing plug 47;

 5 elastic components.

detailed description

 The core of the present invention is to provide a two-way solenoid valve whose structural design can significantly reduce the number of components, the assembly process, reduce the manufacturing cost, and on the other hand, improve the reliability of the work.

In order to make those skilled in the art better understand the technical solutions of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. Referring to FIG. 4 and FIG. 5, FIG. 4 is a schematic structural view of a two-way electromagnetic valve according to an embodiment of the present invention; and FIG. 5 is a schematic structural view of a piston of the two-way electromagnetic valve of FIG.

 In one embodiment, as shown in FIG. 4, the two-way electromagnetic valve provided by the present invention comprises a valve seat 1, the valve seat 1 is provided with a valve cavity, a main valve port 11 is formed in the valve cavity, and the valve cavity is A piston 2 is provided which closes or opens the main valve port 11; as shown in Fig. 4, the piston 2 separates the valve chamber into an upper chamber 12 above the piston 2 and a lower chamber 13 below the piston 2, and in the upper chamber 12 The upper end portion of the piston 2 is provided with a pilot valve port 21 which is opened or closed by a pilot valve member of the two-way solenoid valve; as shown in FIG. 4, the two-way solenoid valve further includes a cross tube 31 and a vertical tube 32. The cross pipe 31 communicates with the lower chamber 13, and the vertical pipe 32 communicates with the main valve port 11 and communicates with the lower chamber 13 when the main valve port 11 is opened.

 As shown in FIG. 4 and FIG. 5, on the basis of the above prior art, a circumferential gap between the circumferential side wall of the piston 2 and the corresponding inner wall of the valve chamber has a flow gap 14; When the first port and the second branch of the valve port 21 are connected, and the pilot port 21 is opened, the first branch of the upper chamber 12 is routed to the end of the cross tube 31 (ie, the refrigerant can pass through the first branch) The upper chamber 12 flows to the end of the cross tube 31, but not to the end chamber 12 through the cross tube 31, and the second portion of the upper chamber 12 is guided to the end of the vertical tube 32 (i.e., the refrigerant can pass through the second branch). The upper chamber 12 is routed to the end of the vertical tube 32, but not to the end chamber 12 by the vertical tube 32; as shown in Fig. 4 and Fig. 5, the piston 2 is further provided with a vertical tube 32-end to the chamber 12 The third branch of the guide passage (that is, the refrigerant can flow through the third branch to the upper chamber 12 through the third branch, but not from the upper chamber 12 to the end of the vertical tube 32); at the same time, the pilot port 21 and the The flow area determined by the second branch is larger than the flow area of the flow gap 14, the pilot port 21 and the The determined first branch flow area larger than the through flow area of the third branch.

When the coil 46 of the two-way solenoid valve is not energized, when the high pressure refrigerant enters the lower chamber 13 of the valve chamber by the cross tube 31, the first branch is closed, and the refrigerant enters the upper chamber 12 above the piston 2 through the flow gap 14 Under the action of high pressure refrigerant and gravity, the pilot valve member closes the pilot valve port 21, at this time, since the upper chamber 12 and the lower chamber 13 are both high pressure ends, and because the force receiving area of the piston 2 in the upper chamber 12 is larger than that in the lower chamber 13 The force receiving area of 2, and because the end of the vertical pipe 32 is the low pressure end, the piston 2 moves downward under the pressure difference, and the main valve port 11 is closed. When the coil 46 of the two-way solenoid valve is energized, under the action of the magnetic field, the pilot valve member opens the pilot valve port 21, and the high pressure cold in the upper chamber 12 The medium flows into the low-pressure vertical pipe 32-end through the pilot valve port 21 and the second branch, and the flow area determined by the pilot port 21 and the second branch is larger than the flow area of the flow gap 14, so that the upper chamber 12 is The pressure drops to form a low pressure end, and the lower chamber 13 is a high pressure end. The piston moves upward under the pressure difference between the lower chamber 13 and the upper chamber 12, opening the main valve port 11 and opening the solenoid valve. When the coil is de-energized, the magnetic field disappears, and the pilot valve member is reset to close the pilot port 21, at which time the refrigerant in the upper chamber 12 no longer flows through the pilot port 21 and the second branch to the end of the riser tube 32, thus the upper chamber 12 The pressure in the rise rises until the pressure of the high pressure refrigerant at the end of the cross pipe 31 is equal; at this time, the upper chamber 12 and the lower chamber 13 of the piston are both high pressure ends, but the force area of the piston 2 in the upper chamber 12 is larger than that in the lower chamber 13 The force receiving area of the piston 2, and because the end of the vertical pipe 32 is the low pressure end, the piston 2 moves downward under the action of the pressure difference, the main valve port 11 is closed, and the solenoid valve is closed.

 When the coil 46 of the two-way solenoid valve is not energized, when the high pressure refrigerant enters from the end of the vertical pipe 32, the second branch is closed, and the high pressure refrigerant enters the upper chamber 12 through the third branch, and the pilot valve member is in the high pressure refrigerant and gravity. The pilot valve port 21 is closed, and the upper chamber 12 and the vertical tube 32 are both high-pressure ends, but the force receiving area of the piston 2 in the upper chamber 12 is larger than the piston 2 determined by the vertical tube 32-end main valve port 11. The force receiving area, and because the cross pipe 31-end and the lower cavity 13 are low-pressure ends, the piston 2 closes the main valve port 11 under the action of the pressure difference, and the solenoid valve is closed. When the coil 46 is energized, under the action of the magnetic field, the pilot valve member opens the pilot valve port 21, and the high-pressure refrigerant in the upper chamber 12 flows through the pilot valve port 21 and the first branch to the low-pressure cross-connector 31-end, due to the pilot valve The flow area determined by the port 21 and the first branch is larger than the flow area of the third branch, so that the pressure in the upper chamber 12 is lowered to form a low pressure end. At this time, under the action of the pressure difference, the piston 2 moves upward, opening the main Valve port 11, the solenoid valve is open. When the coil 46 is de-energized, the magnetic field disappears, the pilot valve member is reset to close the pilot port 21, and the high-pressure refrigerant in the upper chamber 12 can no longer flow through the pilot port 21 and the first branch to the low-pressure cross-connector 31-end. Therefore, the pressure rises to form a high pressure end equal to the end of the vertical pipe 32, but since the force receiving area of the piston in the upper chamber 12 is larger than the force receiving area of the piston 2 determined by the vertical pipe 32-end main valve port 11, and The cross tube 31-end and the lower chamber 13 are low-pressure ends, so that under the action of the pressure difference, the piston 2 closes the main valve port 11, and the solenoid valve is closed.

Compared with the structural design of the two pilot valve ports and the two check valves of the prior art, the two-way solenoid valve of the present invention is provided with only one pilot valve port 21 and a pilot valve member, thereby reducing the number of parts and components. Assembly process; in addition, since the present invention does not adopt the structural design of two check valves, The structure of the support body is omitted, and the structure of the two positioning rods for preventing the rotation of the support body is also eliminated, and accordingly, the structure of the two positioning holes is omitted on the piston, thereby not only reducing the parts and components. The number is reduced, and the processing difficulty and the assembly difficulty are reduced. Since the two-way solenoid valve of the present invention has fewer components and the assembly process is less difficult, the reliability of the work is correspondingly improved.

 In summary, the two-way electromagnetic valve provided by the invention can significantly reduce the number of components, the assembly process, reduce the manufacturing cost, and improve the reliability of the work.

 In the above embodiment, a specific design of the pilot valve member can be made. As shown in FIG. 4, the pilot valve member includes a sleeve 41, a movable iron core 42, a pilot valve ball 43, an elastic member 44, a static iron core 45, and a coil 46; the sleeve 41 is coupled to the valve seat 1, and the movable iron core 42 One end of the guide valve ball 43 is opened or closed, and the other end is connected to the static iron core 45 via an elastic member 44, and the coil 46 is disposed outside the sleeve 41. When the coil 46 is energized, under the action of the magnetic field, the movable iron core 42 overcomes the elastic force of the elastic member 44 and moves toward the end of the static iron core 45, thereby driving the pilot valve ball 43 to open the pilot valve port 21; when the coil is de-energized, The magnetic field disappears. At this time, under the action of the elastic force of the elastic member 44, the movable iron core 42 is reset, and the pilot valve ball 43 is caused to close the pilot valve port 21.

 In the above embodiment, in order to facilitate the communication between the pilot port 21 and the first branch and the second branch, the piston 2 may further be provided with a guide channel 22 communicating with the guide opening 21 in the axial direction. The pilot valve port 21 communicates with the first branch and the second branch through the guide channel 22, respectively.

 It should be noted that, in the above embodiment, the first branch of any structure can only be single-passed from the upper chamber 12 to the transverse tube 31 when the pilot valve opening 21 is opened, and should be in the present invention. At the same time, regardless of the second branch of the structure, it can only be single-passed from the upper chamber 12 to the vertical tube 32 when the pilot valve opening 21 is opened, and should also be within the scope of protection of the present invention. within.

Specifically, a structure of the first branch can be specifically designed. As shown in FIG. 5, the first branch includes a first radial hole 231 and a second radial hole 232. The first radial hole 231-end communicates with the pilot valve passage 22, and the other end and the second radial direction. The hole 232 is connected to each other; a radial sealing surface 233 is disposed between the second radial hole 232 and the first radial hole 231, and a radial sealing body 234 for sealing the radial sealing surface 233 is disposed in the second radial hole 232. The radial sealing body 234 may specifically be a ball; the end of the second radial hole 232 away from the radial sealing surface 233 is provided with a radial stopping member 235, a radial stopping portion The member 235 is provided with a radial through hole 235a that communicates with the second radial hole 232 and the end of the cross tube 31. In operation, the high pressure refrigerant enters the first radial bore 231 from the pilot passage 22 and then opens the radial seal 234 into the second radial bore 232, thereby passing through the radial through bore 235a of the radial stop member 235. Enter the end of the cross tube 31.

 Specifically, in order to improve the reliability of the sealing of the radial sealing body 234 and the stability of the radial movement, the second radial hole 232 may be a circular hole, and the small diameter end of the circular hole has an aperture slightly larger than that of the radial sealing body 234. And a radial sealing surface 233 is connected to the radial sealing surface 233; further, as shown in FIG. 5, the large diameter end of the circular hole is connected with a third radial hole 236 having a larger opening diameter, and the radial stopping member 235 is assembled to the third In the radial bore 236, in particular, the radial stop member 235 can be interference fit into the third radial bore 236.

 Further, in the above embodiment, it is also possible to make a specific design for the second branch. For example, as shown in FIG. 5, the second branch includes an axial cavity 241 communicating with the pilot passage 22, and a first axial sealing surface 242 is disposed between the axial cavity 241 and the pilot passage 22. a first axial sealing body sealing the first axial sealing surface 242 is disposed in the axial cavity 241; a first axial stopping component is disposed at an end of the axial cavity 241 away from the first axial sealing surface 242 243, and the first axial stopping member 243 is provided with a first axial through hole 243a that communicates with the axial cavity 241 and the end of the vertical pipe 32.

 Specifically, as shown in FIG. 5, the first axial sealing body may be a one-way spool 244, and the one-way spool 244 is provided with a spool radial hole 244a and a spool axial hole 244b communicating with each other, the spool The radial bore 244a is in communication with the axial cavity 241, and the spool axial bore 244b is in communication with the first axial through bore 243a. During operation, the high pressure refrigerant enters the open channel 22 from the pilot port 21, and then seals the first axial sealing surface 242 from the one-way spool 244, enters the axial cavity 241, and then the high pressure refrigerant passes through the spool The radial bore 244a and the spool axial bore 244b are then passed through the first axial through bore 243a of the first axial stop member 243 into the end of the riser tube 32.

 Specifically, as shown in FIG. 5, in order to improve the reliability of the connection of the first axial stopping member 243, one end of the axial cavity 241 away from the first axial sealing surface 242 may be connected with a first axial direction having a larger opening diameter. The hole 245 and the piston 2 are provided with a rivet portion 26, and the first axial stop member 243 is riveted into the first axial hole 245 by the rivet portion 26.

Furthermore, it should be noted that, in the above embodiment, the third branch of any structure can only be unidirectionally connected from the vertical pipe 32 to the upper cavity 12, and should be protected by the present invention. Within the scope.

 Specifically, a third branch structure can be specifically designed. For example, as shown in FIG. 5, the third branch includes a second axial hole 252 and a third axial hole 253. One end of the second axial hole 252 is connected to the end of the vertical pipe 32, and the other end is The three axial holes 253 are in communication, and the diameter of the third axial hole 253 is larger than the diameter of the second axial hole 252; further, as shown in FIG. 5, between the second axial hole 252 and the third axial hole 253 a second axial sealing surface 254 is disposed, and a second axial sealing body 255 is disposed in the third axial hole 253 for sealing the second axial sealing surface 254, and the second axial sealing body 255 can seal the spherical body; Furthermore, as shown in FIG. 5, a second axial stop member 256 is disposed at one end of the third axial hole 253 away from the second axial sealing surface 254, and the second axial stop member 256 is provided with a communication first. The three axial holes 253 and the second axial through holes 256a of the upper chamber 12.

 Specifically, as shown in FIG. 4 and FIG. 5, in order to facilitate the communication of the second axial hole 252 with one end of the vertical pipe 32, the piston 2 may further be provided with an inclined hole 251, and the second axial hole 252 may pass through the inclined hole 251 and the vertical Take the 32-end connection.

 When working, as shown in FIG. 4 and FIG. 5, the high-pressure refrigerant enters the inclined hole 251 from the end of the vertical pipe 32, and breaks the sealing of the second axial sealing surface 255 by the second axial sealing body 255, and enters the second. The axial bore 252, in turn, enters the upper chamber 12 through the second axial through bore 256a of the second axial stop member 256.

 Finally, it should be noted that in the first branch, the first radial hole 231, the radial sealing surface 233, the radial sealing body 234, the second radial hole 232 and the radial stopping member 235 actually constitute The first one-way valve structure, the first one-way valve structure makes the first branch single-pass; in the second branch, the axial cavity 241, the first axial sealing surface 242, the one-way spool 244 and the first axial stop member 243 actually constitutes a second intermediate check valve structure, the second one-way valve structure such that the second branch is single-conducting; in the third branch, the second axial direction The aperture 252, the second axial sealing surface 254, the second axial sealing body 255, the third axial bore 253 and the second axial stop member 256 actually constitute a third one-way valve structure, the third The one-way valve structure allows the third branch to be single-passed.

Obviously, the above-mentioned first one-way valve structure, the second one-way valve structure and the third one-way valve structure can be interchanged on the premise of satisfying the function of the one-way conduction, that is, the first branch can be adopted The second one-way valve structure or the third one-way valve structure, the second branch may adopt the first one-way valve structure or the third one-way valve structure, and the third branch may Adopting the first type a one-way valve structure or the second one-way valve structure; of course, the first branch, the second branch or the third branch may also adopt other structures under the premise of satisfying the function of the single-pass The one-way valve, this one-way valve of other constructions should obviously also be within the scope of the present invention. In addition, on the basis of the above technical solutions, further improvements can be made. For example, please refer to FIG. 6 to FIG. 9. FIG. 6 is a schematic structural view of a two-way electromagnetic valve according to another embodiment of the present invention; FIG. 7 is a schematic structural view of a piston of the two-way electromagnetic valve of FIG. Figure 2 is a schematic view of the structure of the cylinder of the piston of Figure 7.

 As shown in FIG. 7 and FIG. 8, it is important to note that the first branch includes a radial conduit having a radial sealing surface 233 and a radial engagement with the radial sealing surface 233. a sealing body 234; a guiding seat for moving the radial sealing body 234 in the radial direction of the piston 2 is further disposed in the radial pipe, and the guiding seat is provided with a guiding seat connecting the transverse pipe 31-end and the radial pipe aisle.

 In operation, in the first branch, when the radial sealing body 234 opens the radial sealing surface 233, through the guiding seat passage, the upper chamber 12 is unidirectionally guided through the radial pipe and the transverse pipe 31. When the radial sealing surface 233 is closed to the sealing body 234, the first branch is closed. In the above structure, since the guide seat radially guides the radial seal body 234 to move in the radial direction of the piston 2, it is possible to prevent the radial seal body 234 from being displaced downward by the action of gravity, thereby avoiding The appearance of the radial sealing body 234 sealing the radial sealing surface 233 is not strict, the sealing performance is improved, leakage is prevented, and the overall energy efficiency of the refrigeration equipment is improved.

 Further, a specific design of the radial conduit of the first branch can also be made. Figure 7 and Figure

As shown in FIG. 8, the radial pipe includes a first radial hole 231 and a second radial hole 232 having a larger diameter, and a radial sealing surface 233 is formed between the first radial hole 231 and the second radial hole 232. The guide seat is disposed in the second radial hole 232 and guides to support the radial sealing body 234 to move in the radial direction of the piston 2 to seal or disengage the radial sealing surface 233. In this configuration, the radial sealing surface 233 can be conveniently designed by the step between the first radial hole 231 and the second radial hole 232 having a larger opening diameter, and the structure is also relatively simple, and the processing cost is low. .

It should be noted that any guide seat structure can guide the radial tube through the guide seat channel as long as the radial sealing body 234 can be radially guided while the radial sealing body 234 opens the radial sealing surface 233. The road should be within the scope of the present invention. As an example, a guide seat structure may be specifically designed. For example, please refer to FIG. 7, FIG. 8 and FIG. 9. The guide seat is a cylinder 237 having an opening at one end, and the radial seal body 234 is disposed on the cylinder. In the barrel lumen 237a of the 237, the cylinder 237 faces the radial sealing surface 233 with its opening so that the radial sealing body 234 opens or closes the radial sealing surface 233; the guiding seat passage is opened on the circumferential side of the cylinder 237 The cylindrical gap 237b of the cylindrical inner chamber 237a and the second radial hole 232 is communicated with the wall.

 In the above structure, as shown in Figs. 7 and 8, the radial sealing body 234 is inserted into the cylindrical cavity 237a through the opening of the cylinder 237, through which the radial sealing body 234 can be better aligned. Perform radial guidance. In addition, the opening of the cylinder 237 faces the radial sealing surface 233, and the radial sealing body 234 moves in the direction of the radial sealing surface 233 in the cylinder cavity 237a, thereby sealing the radial sealing surface 233 away from the The radial sealing surface 233 is moved to open the radial sealing surface 233. Moreover, as shown in FIG. 9, the guide seat passage is a cylindrical notch 237b which is opened on the circumferential side wall of the cylinder 237 and communicates the barrel inner chamber 237a and the second radial hole 232, when the radial sealing body 234 is separated from the opening. When the radial sealing surface 233 is radial, one end of the transverse pipe passes through the second radial hole 232, the cylindrical notch 237b, the cylindrical cavity 237a and the radial sealing surface 233, thereby achieving the conduction of the radial pipe, and further The conduction of the first branch is achieved. In summary, the structural design of the cylinder 237 is capable of radially guiding the radial sealing body 234 on the one hand and facilitating the conduction of the radial piping on the other hand.

 Further, as shown in FIGS. 7 to 9, the barrel notch 237b further extends to the bottom sealed end of the cylinder 237 so that the bottom sealing end of the cylinder 237 and the inner wall of the second radial hole 232 have a conduction gap 237c. . One end of the traverse tube communicates with the second radial hole 232 through the conduction gap 237c, and further communicates with the barrel notch 237b. Moreover, the cylinder 237 is interference-fitted into the second radial bore 232 with its circumferential side wall, which is simple in reliability and low in cost. In any of the above technical solutions, further improvements can be made. For example, please refer to FIG. 10. FIG. 10 is a schematic structural diagram of a two-way electromagnetic valve according to another embodiment of the present invention.

As shown in FIG. 10, the inner wall of the valve seat 1 is provided with a valve seat guiding section 15, and the outer circumferential wall of the piston 2 is provided with a piston guiding section 27 which cooperates with the valve seat guiding section 15; the piston guiding section 27 is opened below the piston guiding section 27. The pipe installation section 28 has a small diameter, the first branch includes a radial pipeline, and the radial pipeline is opened on the pipeline installation section 28; the lower part of the valve seat guide section 15 is further provided with an annular groove 16 and a piston When the main valve port is opened, the radial line as a whole is in the range in which the annular groove 16 faces. Specifically, the specific meaning of "the radial duct as a whole is in the range in which the annular groove 16 is directly facing" has the following meanings as follows:

 As shown in FIG. 10, when the piston 2 opens the main valve port 11, the piston 2 moves upward, and accordingly, the radial pipe (including the first radial hole 231 and the second radial hole 232) also moves upward. The line does not pass over the uppermost end of the annular groove 16, i.e., the uppermost end of the annular groove 16 is always higher than the uppermost end of the radial pipe.

 When the piston 2 opens the main valve port 11, the piston 2 will rotate circumferentially under the push of the refrigerant fluid. At this time, it is possible to turn the radial pipe to the left side in FIG. 10, that is, away from the cross pipe 31. On one side, at this time, the outlet end of the radial pipe may increase the pressure of the refrigerant at the portion due to the narrow space, so that the radial sealing body 234 in the radial pipe will close the radial sealing surface 233 again. Further, the piston 2 vibrates in the axial direction, generating vibration noise, and is also disadvantageous for flow stability.

 In the present invention, since the radial pipe as a whole is in the range in which the annular groove 16 is facing, when the piston 2 is rotated so that the radial pipe is turned to the side away from the transverse pipe 31, The open end of the radial pipe still corresponds to the annular groove 16, and the space of the portion is large enough to facilitate the flow of the refrigerant, thereby avoiding the occurrence of local high pressure, thereby preventing the radial sealing body 234 from closing the radial seal again. The face 233 can prevent the piston 2 from vibrating and ensure the stability of the flow rate.

 In addition, as shown in FIG. 10, the two-way solenoid valve further includes an elastic member 5, and a step 29 is formed between the piston guiding portion 27 and the pipe mounting portion 28; the elastic member 5 is sleeved on the circumferential outer portion of the lower portion of the piston 2, and is elastic Supported between the step 29 and the inner bottom wall of the valve seat. In this configuration, the elastic member 5 can balance the gravity of the piston, and under the action of the pressure difference between the upper chamber and the lower chamber, the piston 2 can be opened relatively easily and is not easily closed, thereby further preventing the piston 2 from vibrating up and down. And guarantee the stability of the flow.

 In addition, it should be noted that the present invention does not limit the structure of the sealing member under the pilot valve, and the pilot valve sealing member may be the sealing ball 43 as shown in FIG. 4 and FIG. 10, or may be as shown in FIG. The guide opening sealing plug 47.

The two-way solenoid valve provided by the present invention has been described in detail above. Application in this article It is a method for helping to understand the present invention and its core idea. It should be noted that those skilled in the art can make various modifications and changes to the present invention without departing from the spirit and scope of the invention.

Claims

Rights request  A two-way solenoid valve comprising a valve seat (1) provided with a main valve port (11) and a valve chamber, wherein the valve chamber is provided with a piston (2) cooperating with the main valve port (11), The piston (2) separates the valve chamber into an upper chamber (12) and a lower chamber (13), and an upper end portion of the piston (2) is provided with a pilot valve port (21) that is opened or closed by a pilot valve member. The two-way solenoid valve further includes a cross pipe (31) communicating with the lower chamber (13), and a vertical pipe (32) connectable to the lower chamber (13) through the main valve port (11); The utility model is characterized in that: a circumferential gap between the circumferential side wall of the piston (2) and a corresponding inner wall of the valve chamber has a flow gap (14); the piston (2) is provided with a valve port ( 21) a first branch that is communicable and unidirectional from the upper chamber (12) to one end of the transverse tube (31), and a single one that can be terminated from the upper chamber (12) to the vertical tube (32) a second branch of the guide; the piston (2) is further provided with a third branch that can be unidirectionally guided to the upper chamber (12) by the vertical tube (32); (21) and the second branch Given flow area is greater than the flow gap (14) of the flow area, the pilot valve port (21) of the first branch and the determined flow area larger than the flow area of the third branch.  The two-way solenoid valve according to claim 1, wherein the piston (2) further has a pilot passage (22) communicating with the pilot port (21) in the axial direction, the guide The valve port (21) is unidirectionally guided to the first branch and the second branch respectively through the open channel (22).  The two-way solenoid valve according to claim 2, wherein the first branch includes a first radial hole (231), the first radial hole (231)-end and the guide width The channel (22) is in communication, and the other end thereof is connected with a second radial hole (232) having a larger aperture; a diameter is provided between the second radial hole (232) and the first radial hole (231) a radial sealing body (234) sealing the radial sealing surface (233) is provided in the sealing surface (233), the second radial hole (232); the second radial hole (232) is away from the One end of the radial sealing surface (233) is provided with a radial stopping member (235), and the radial stopping member (235) is provided to communicate with the second radial hole (232) and the transverse tube ( 31) - Radial through hole (235a) at the end. The two-way solenoid valve according to claim 3, wherein the second radial hole (232) is a circular hole, and the small diameter end of the circular hole is connected to the radial sealing surface (233), which is large A third radial hole (236) having a larger opening diameter is connected to the radial end, and the radial stopping member (235) is assembled to The third radial bore (236).  The two-way solenoid valve according to any one of claims 2 to 4, wherein the second branch includes an axial cavity (241) communicating with the open channel (22), the axis A first axial sealing surface (242) is disposed between the cavity (24) and the pilot valve passage (22), and the first axial sealing surface is sealed in the axial cavity (241) ( a first axial sealing body of 242); a first axial stopping member (243) is disposed at an end of the axial cavity (241) away from the first axial sealing surface (242), and the first The axial stop member (243) is provided with a first axial through hole (243a) that communicates with the axial cavity (241) and the end of the vertical pipe (32).  The two-way solenoid valve according to claim 5, wherein the first axial sealing body is a one-way valve core (244), and the one-way valve core (244) is provided with a valve core that communicates with each other. Radial hole And a wide core axial hole (244b) communicating with the axial cavity (241), the wide core axial hole (244b) and the first The axial through holes (243a) are in communication.  The two-way solenoid valve according to claim 5, wherein one end of the axial cavity (241) away from the first axial sealing surface (242) is connected with a first axial direction having a larger aperture a hole (245), the piston (2) is provided with a riveting portion (26), and the first axial stopping member (243) is riveted to the first axial hole through the riveting portion (26) ).  The two-way solenoid valve according to any one of claims 1 to 4, wherein the third branch includes a second axial hole (252) communicating with the end of the vertical pipe (32), And the other end of the second axial hole (252) communicates with a third axial hole (253) having a larger opening diameter; and the second axial hole (252) and the third axial hole (253) are provided with a first a second axial sealing surface (254), and a third axial sealing body (255) sealing the second axial sealing surface (254); and the third axial hole (253) a second axial stopping member (256) is disposed at one end away from the second axial sealing surface (254), and the second axial stopping member (256) is provided with a third axial hole (253) a second axial through hole (256a) with the upper chamber (12).  The two-way solenoid valve according to claim 8, wherein the piston (2) is further provided with an inclined hole (251), and the second axial hole (252) passes through the inclined hole (251) It is in communication with the end of the vertical pipe (32). The two-way solenoid valve according to any one of claims 1 to 4, characterized in that the pilot valve member comprises a sleeve (41) connected to the valve seat (1), the sleeve ( 41) Built-in a moving iron core (42), one end of the movable iron core (42) is connected with a pilot ball (43) sealing or opening the pilot valve port (21), and the other end of the movable iron core (42) is connected by an elastic member (44) The static iron core (45) is provided with a coil (46) outside the sleeve (41).  The two-way solenoid valve according to claim 1, wherein the first branch includes a radial pipe, and the radial pipe is provided with a radial sealing surface (233) and is sealed with the radial a surface (233) mating radial sealing body (234); a guide seat for moving the radial sealing body (234) in a radial direction of the piston (2), and The guide seat is provided with a guide seat passage connecting the end of the cross pipe (31) to the radial pipe.  The two-way solenoid valve according to claim 11, wherein the radial pipe includes a first radial hole (231) and a second radial hole (232) having a larger diameter, the radial direction a sealing surface (233) is formed on the step between the first radial hole (231) and the second radial hole (232); the guiding seat is disposed on the second radial hole (232) And guiding and supporting the radial sealing body (234) to move along the radial direction of the piston (2) to seal or open the radial sealing surface (233).  The two-way solenoid valve according to claim 12, wherein the guide seat is a cylinder (237) having an opening at one end, and the radial sealing body (234) is disposed at the cylinder (237) In the barrel lumen (237a), the cylinder (237) faces the radial sealing surface (233) with its opening such that the radial sealing body (234) opens or closes the radial seal a surface (233); the guide seat passage is formed on a circumferential side wall of the cylinder (237) and communicates with the barrel gap of the barrel inner chamber (237a) and the second radial hole (232) (237b).  The two-way solenoid valve according to claim 13, wherein said barrel notch (237b) further extends to a bottom sealed end of said cylinder (237) such that a bottom sealed end of said cylinder (237) There is a conduction gap (237c) between the inner wall of the second radial hole (232).  The two-way solenoid valve according to claim 13, wherein the cylinder (237) is interference-fitted in the second radial bore (232) with its circumferential side wall. The two-way solenoid valve according to any one of claims 1 to 15, characterized in that the inner wall of the valve seat (1) is provided with a valve seat guiding section (15), the circumference of the piston (2) a piston guiding section (27) engaging with the valve seat guiding section (15) is disposed on the outer wall; a pipe mounting section (28) having a smaller outer diameter is disposed below the piston guiding section (27), The first leg includes a radial pipe, the radial pipe is opened on the pipe mounting section (28); the valve seat guiding section (15) The lower portion is further provided with an annular groove (16), and when the piston (2) opens the main valve port (11), the radial pipe as a whole is in the range directly facing the annular groove (16) Inside.  The two-way solenoid valve according to claim 16, wherein the two-way solenoid valve further comprises an elastic member (5), between the piston guiding portion (27) and the pipe mounting portion (28) Forming a step (29); the elastic member (5) is sleeved on a circumferential outer portion of the lower portion of the piston (2), and is elastically supported on the step (29) and the insole of the valve seat (1) Between the walls.