Double pulse solenoid valve

Abstract

The present invention discloses a dual-pulse solenoid valve, comprising a pressure-regulating mechanism and a plunger mechanism. The pressure-regulating mechanism comprises a valve body, a pressure-regulating operating portion arranged along a first direction, a pressure-regulating component, a piston seat, a valve stem, and a reset element. The valve body comprises a detachably connected upper valve body and a lower valve body. The upper valve body defines a first chamber, the upper valve body is provided with an overflow port, the lower valve body is provided with a valve seat, the piston seat is provided with an upper valve port, and the valve seat is provided with a lower valve port. The lower valve body is provided with at least a second chamber, an input port, an output port, and an exhaust port. The plunger mechanism comprises a piston rod and a guide sleeve, with a third chamber provided between the guide sleeve and the piston rod. An air path communicating with the third chamber is provided within the pressure-regulating mechanism. The diameter of the air path is smaller than the diameters of the input port and the exhaust port. The pressure in the third chamber is not higher than a set pressure value. When the output port pressure exceeds both the input port pressure and the set pressure value, the upper valve port opens. This application can effectively protect the parking cylinder spring.

Description

Technical Field

[0001] The present invention relates to the technical field of rail transit vehicle parking brakes, and in particular to a double-pulse solenoid valve. Background Art

[0002] When rail transit vehicles need to be securely parked or are without power or compressed air, the parking brake ensures that a fully loaded EMU can park on a slope of 30‰ without rolling. The parking brake is actuated by a parking brake cylinder, which contains a preloaded, high-performance spring. When the cylinder is exhausted, the spring forces the parking brake piston rod to extend. When the cylinder is inflated, the spring compresses, releasing the parking brake.

[0003] Due to the structural characteristics of the parking brake cylinder, the output pressure must be kept below a certain level when inflating the cylinder, as this would damage the high-performance spring within. The parking brake control component is typically a dual-pulse solenoid valve, which controls the charging and discharging of air from the parking (brake) cylinder via pulsed voltage signals across the valve. Existing dual-pulse solenoid valves used for parking control in rail vehicle braking systems only function to charge and discharge air from the parking cylinder.

[0004] Furthermore, to ensure that the parking cylinder's air pressure does not exceed the required level, the brake system can install a pressure reducing valve in the upstream pipeline of the dual-pulse solenoid valve. To limit the impact load on the high-performance spring in the parking cylinder, a throttle valve can be installed between the pressure reducing valve and the dual-pulse solenoid valve pipeline to control the air flow. Therefore, existing rail vehicle braking systems require three types of valve components for parking control, which hinders the lightweight and miniaturization of the braking system.

[0005] Therefore, it is necessary to propose a dual-pulse solenoid valve to solve at least one of the above problems. Summary of the Invention

[0006] In response to the defects of the existing technology, a dual-pulse solenoid valve is provided in an embodiment of the present invention, which not only has a compact overall structure and a small size, but also has the function of regulating pressure and flow, and can effectively protect the parking cylinder spring.

[0007] The specific technical solutions of the embodiments of the present invention are:

[0008] A double-pulse solenoid valve, the double-pulse solenoid valve includes: the double-pulse solenoid valve includes: a pressure regulating mechanism and a plunger mechanism, the pressure regulating mechanism includes: a valve body, a pressure regulating operating part arranged along a first direction, a pressure regulating component, a piston seat, a valve stem, and a reset component, the valve body includes a detachably connected upper valve body and a lower valve body, a first cavity is formed in the upper valve body, an overflow port is provided on the upper valve body, a valve seat is provided in the lower valve body, an upper valve port is provided on the piston seat, and a lower valve port is provided on the valve seat; at least a second cavity is provided in the lower valve body , as well as an input port, an output port and an exhaust port; the plunger mechanism includes: a piston rod, a guide sleeve sleeved outside the piston rod, a third chamber is provided between the guide sleeve and the piston rod; an air path connected to the third chamber is provided in the pressure regulating mechanism; the diameter of the air path is smaller than the diameters of the input port and the exhaust port; the pressure of the third chamber is not higher than the set pressure value; when the output port pressure is greater than the input port pressure and greater than the set pressure value, the upper valve port is opened, and the output port pressure can be discharged from the overflow port through the upper valve port.

[0009] In a preferred embodiment, the upper valve body and the lower valve body are connected by threads, and a first accommodating portion for mounting the piston seat is formed at the matching position of the upper valve body and the lower valve body, and the piston seat can move along the first direction.

[0010] In a preferred embodiment, the upper valve body is provided with an opening for passing the pressure regulating operating part, the pressure regulating operating part passes through the opening and extends into the first cavity, the pressure regulating component is a pressure regulating spring, one end of the pressure regulating spring is connected to the pressure regulating operating part, and the other end is connected to the piston seat, the pressure regulating spring is used to ensure that the output pressure of the dual-pulse solenoid valve is not greater than the set value.

[0011] In a preferred embodiment, an accommodating chamber for accommodating the valve stem and the valve seat is opened in the lower valve body. When the valve stem contacts the valve seat, the accommodating chamber in the lower valve body is divided into a fourth chamber located between the valve seat and the piston seat, and the second chamber. The fourth chamber is connected to the third chamber through the air path. The second chamber is used as an input pressure chamber for connecting to the input port. The input port can be connected to the brake air pressure to supply air to the double-pulse solenoid valve.

[0012] In a preferred embodiment, a second accommodating portion for mounting the valve seat is provided in the lower valve body. When the valve stem moves along the first direction, the valve stem cooperates with the valve seat to realize the opening and closing of the lower valve port.

[0013] In a preferred embodiment, the valve stem is a stepped shaft with variable diameter as a whole, including a first shaft segment with a smaller diameter and a second shaft segment with a larger diameter. A stepped portion is formed at the transition position between the first shaft segment and the second shaft segment. The first shaft segment passes through the lower valve port, and the diameter of the first shaft segment is smaller than the aperture of the lower valve port, and the diameter of the second shaft segment is larger than the aperture of the lower valve port. When the input pressure is greater than the pressure set by the pressure regulating operating part, the stepped portion of the valve stem can contact the lower valve port and close the lower valve port. When the input pressure is less than the pressure set by the pressure regulating operating part, the stepped portion of the valve stem is separated from the lower valve port, and the lower valve port is opened.

[0014] In a preferred embodiment, the lower valve body is provided with a through hole extending along the second direction, the guide sleeve and the piston rod are installed in the through hole, and the plunger mechanism further includes side covers, which are sealingly sleeved on both ends of the guide sleeve.

[0015] In a preferred embodiment, the plunger mechanism further includes a push rod, which is installed in the side cover and can move along the second direction to drive the piston rod to move.

[0016] In a preferred embodiment, the plunger mechanism further includes a coil assembly, a pilot chamber is provided in the side cover, a pilot valve port is provided in the pilot chamber, and a sealing member for closing the pilot valve port is provided. When the coil assembly is energized, the sealing member is separated from the pilot valve port, driving the air pressure to flow through the pilot chamber to the push rod, driving the push rod and the piston rod to move along the second direction.

[0017] In a preferred embodiment, the coil assembly includes a left coil assembly and a right coil assembly, and the push rod includes a right push rod and a left push rod. When the right coil assembly is energized or pressed, the piston rod can move to the left and connect with the output port through the third chamber, and the exhaust port is cut off; when the left coil assembly is energized or pressed, the piston rod can move to the right, the third chamber is cut off from the output port, and the output port is connected with the exhaust port through the guide sleeve.

[0018] The technical solution of the present invention has the following significant beneficial effects:

[0019] The dual-pulse solenoid valve provided in the present application is a dual-pulse solenoid valve with adjustable output pressure. It has a compact structure and reliable functions. It can be used in the pneumatic pipeline of the rail vehicle braking system. Through the internal pressure regulating mechanism, the charging pressure of the parking brake pipeline can be adjusted. It has the characteristics of small charging flow and large exhaust flow. At the same time, the internal pressure regulating mechanism has an overflow function, which can ensure that when the vehicle suddenly loses power or compressed air, the parking cylinder can still be parked smoothly.

[0020] With reference to the following description and drawings, specific embodiments of the present invention are disclosed in detail, indicating the manner in which the principles of the present invention can be employed. It should be understood that the embodiments of the present invention are not limited in scope thereby. Within the spirit and scope of the appended claims, the embodiments of the present invention include many variations, modifications, and equivalents. Features described and / or illustrated with respect to one embodiment may be used in the same or similar manner in one or more other embodiments, combined with features in other embodiments, or substituted for features in other embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The drawings described herein are for illustrative purposes only and are not intended to limit the scope of the present invention in any way. In addition, the shapes and proportional dimensions of the various components in the drawings are merely illustrative and are used to help understand the present invention, and are not intended to specifically limit the shapes and proportional dimensions of the various components of the present invention. Those skilled in the art can select various possible shapes and proportional dimensions to implement the present invention according to specific circumstances under the guidance of the present invention.

[0022] Figure 1 This is a structural schematic diagram of a double-pulse solenoid valve provided in an embodiment of the present application;

[0023] Figure 2 A schematic diagram of the partial structure of a pressure regulating mechanism of a double-pulse solenoid valve provided in an embodiment of the present application;

[0024] Figure 3 This is a schematic diagram of a double-pulse solenoid valve provided in an embodiment of the present application in a first state of parking relief;

[0025] Figure 4 This is a schematic diagram of a double-pulse solenoid valve provided in an embodiment of the present application in a second state of parking application;

[0026] Figure 5 This is a structural diagram of another dual-pulse solenoid valve provided in the embodiment of this application.

[0027] 1. Lower valve body;

[0028] 2. Coil assembly;

[0029] 3. Side cover;

[0030] 4. Ejector rod;

[0031] 5. Guide sleeve;

[0032] 6. Piston rod;

[0033] 7. Sealing ring;

[0034] 8. Reset parts;

[0035] 9. Valve stem;

[0036] 10. Valve seat;

[0037] 11. Piston seat;

[0038] 12. Pressure regulating components;

[0039] 13. Voltage regulating operation unit;

[0040] 14. Upper valve body;

[0041] 15. Input port;

[0042] 16. Output port;

[0043] 17. Exhaust port;

[0044] 18. First cavity;

[0045] 19. Second cavity;

[0046] 24. Fourth cavity;

[0047] 25. Gas path;

[0048] 20. The third cavity;

[0049] 21. a first accommodating portion;

[0050] 22. Second accommodating portion;

[0051] 23. Overflow port;

[0052] V1, upper valve port;

[0053] V2, pilot valve port;

[0054] V3, lower valve port. DETAILED DESCRIPTION

[0055] The technical solution of the present invention will be described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that these embodiments are only used to illustrate the present invention and are not used to limit the scope of the present invention. After reading the present invention, modifications of various equivalent forms of the present invention by those skilled in the art all fall within the scope defined by the claims attached to this application.

[0056] It should be noted that when an element is referred to as being "disposed on" another element, it may be directly on the other element or there may be an element centered thereon. When an element is referred to as being "connected to" another element, it may be directly connected to the other element or there may be an element centered thereon. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only implementations.

[0057] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the art to which this application pertains. The terms used herein in the specification of this application are intended only to describe specific embodiments and are not intended to limit this application. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0058] At present, most of the existing dual-pulse solenoid valve products adopt a plunger valve structure.

[0059] One prior art example: a dual-pulse solenoid valve for rail transit vehicle braking systems, comprising a valve body, a solenoid valve assembly, and a side cover. The valve body has an A end and a B end, each of which houses a solenoid valve assembly. The valve body interior includes a valve stem, a guide sleeve, an O-ring, and a K-ring. The valve stem is mounted in the valve body at both ends via two guide sleeves, with K-rings mounted between the guide sleeves and the valve body. A C-chamber is defined between the two guide sleeves, with O-rings mounted at both ends of the C-chamber. A B-chamber is defined between the A-end of the valve body and the valve stem, connected to the solenoid valve assembly via channel B. A A-chamber is defined between the B-end of the valve body and the valve stem, connected to the solenoid valve assembly via channel A. This dual-pulse solenoid valve is a 2-position, 5-way solenoid valve with a plunger valve structure. It can charge or exhaust air from the parking cylinder via an electronic control signal.

[0060] Prior art 2: A dual-pulse solenoid valve for parking brakes on rail transit locomotives. Specifically, this dual-pulse solenoid valve primarily comprises a valve body, a piston, a guide sleeve, left and right push rods, and includes a release-end solenoid valve and an apply-end solenoid valve. The left and right push rods are located on either side of the piston and are integrally formed with the piston. This dual-pulse solenoid valve is a two-position, three-way solenoid valve with a plunger valve structure. It can charge or exhaust the parking cylinder via an electronic control signal.

[0061] Generally speaking, the existing dual-pulse solenoid valves mostly adopt a plunger valve structure, which can realize the function of filling or exhausting the parking cylinder through an electric control signal, but does not have the function of regulating pressure and flow, and cannot effectively protect the parking cylinder (especially the parking cylinder spring).

[0062] Drawing on years of experience and practice in related industries, the inventors of this application have developed a dual-pulse solenoid valve with adjustable output pressure for rail vehicles. This valve features a compact overall structure and small size, while achieving adjustable output pressure, low charge flow, high discharge flow, and protection for the parking cylinder spring. Furthermore, the valve incorporates an overflow protection feature, ensuring that if the downstream pressure of the valve increases abnormally, the overflow port of the solenoid valve's pressure regulating mechanism will dissipate the excess pressure, thereby protecting the parking cylinder spring.

[0063] Please refer to the comprehensive Figure 1 、 Figure 2 、 Figure 3 、 Figure 4 and Figure 5 In the embodiment of the present application, a double-pulse solenoid valve is provided. The double-pulse solenoid valve mainly includes: a pressure regulating mechanism and a plunger mechanism.

[0064] The pressure regulating mechanism may include: a valve body, a pressure regulating operating portion 13 arranged along the first direction, a pressure regulating component 12, a piston seat 11, a valve stem 9, a reset member 8, and a valve seat 10. The plunger mechanism may include: a side cover 3, a guide sleeve 5, a piston rod 6, and a push rod 4.

[0065] In this embodiment, the valve body includes a detachably connected upper valve body 14 and a lower valve body 1. Specifically, the detachably connected manner can be a threaded connection, so as to facilitate convenient and quick assembly of parts. Of course, the connection method of the upper valve body 14 and the lower valve body 1 is not limited to the above example.

[0066] In the illustrated embodiment of the present application, the upper valve body 14 is located on the upper part of the lower valve body 1, and the upper valve body 14 can be a hollow columnar shape (for example, cylindrical) as a whole. The cavity formed by the hollow part of the upper valve body 14 can be the first cavity 18 in the figure. The first cavity 18 is used as an output cavity, and the output pressure is determined by the input pressure and the set pressure. One end of the upper valve body 14 that cooperates with the lower valve body 1 (the lower end in the figure) is an open end, and the other end (the upper end in the figure) can be provided with an opening for passing the pressure regulating operating part 13. Specifically, the pressure regulating operating part 13 can be in the form of a pressure regulating screw, a pressure regulating nut, etc. Of course, the specific form of the pressure regulating operating part 13 is not limited to the above examples. In the embodiment of the present application, the pressure regulating screw is used as an example for explanation. By rotating the pressure regulating screw, the operator can change the matching pressure regulating component 12 (for example, the compression amount of the pressure regulating spring), that is, adjust the preload force of the pressure regulating component 12. An overflow port 23 may also be provided on the upper valve body 14 for pressure relief.

[0067] In the illustrated embodiment of the present application, the lower valve body 1 is positioned above the upper valve body 14, and a first accommodating portion 21 is formed at the mating position of the lower valve body 1 and the upper valve body 14. The first accommodating portion 21 is used to mount the piston seat 11. Specifically, the first accommodating portion 21 can be in the form of an annular groove. In the longitudinal extension direction of the valve body (hereinafter referred to as the first direction), the height of the groove is greater than the thickness of the piston seat 11, thereby allowing the piston seat 11 to move a certain amount within the groove along the first direction.

[0068] In one embodiment, the pressure regulating screw, the pressure regulating spring, the piston seat 11 , the valve stem 9 , and the return spring are sequentially distributed along the first direction.

[0069] The pressure-regulating spring ensures that the output pressure of the dual-pulse solenoid valve does not exceed the set value. One end of the spring is connected to the pressure-regulating screw, and the other end is connected to the piston seat 11. By rotating the pressure-regulating screw, the compression of the spring can be changed. The greater the compression of the spring, the greater the set output pressure.

[0070] The piston seat 11 is provided with an upper valve port V1 for transmitting the force of the pressure regulating spring to the valve stem 9 . The piston seat 11 can move up and down in the first accommodating portion 21 along the first direction (ie, the height direction in the figure).

[0071] When the pressure on both sides of the piston seat 11 forms a difference and the force acting on the lower surface is greater than the force acting on the upper surface, that is, when the output pressure is greater than the input pressure, the upper valve port V1 can be opened, and the output pressure is connected to the R cavity through this part and is connected to the overflow port 23, thereby causing overflow to occur and the output pressure to drop.

[0072] In this embodiment, the lower valve body 1 can also be cylindrical as a whole, and a housing chamber for accommodating the valve stem 9 and the valve seat 10 is provided in the lower valve body 1. When the valve stem 9 contacts the valve seat 10, the housing chamber in the lower valve body 1 is divided into a fourth chamber 24 located between the valve seat 10 and the piston seat 11, and a second chamber 19 for always connecting to the input port 15. The second chamber 19 serves as an input pressure chamber, and the second chamber 19 can be connected to the brake air pressure through the input port 15 to supply air to the dual-pulse solenoid valve. An air path 25 with a smaller diameter is also provided in the lower valve body 1, wherein one end of the air path 25 is connected to the fourth chamber 24, and the other end is connected to the third chamber 20 provided between the guide sleeve 5 and the piston rod 6. Figure 1 As shown, the specific position of one end of the gas path 25 communicating with the fourth chamber 24 can be located on the plane where the lower valve body 1 contacts the piston seat 11. Figure 5 As shown, a side opening can be opened on the side of the lower valve body 1, and one end of the gas path 25 can be located at the end of the side opening.

[0073] Specifically, a second accommodating portion 22 for accommodating the valve seat 10 may be provided in the middle portion of the lower valve body 1. The second accommodating portion 22 may be in the form of a limiting step formed on the inner wall of the lower valve body 1. The valve stem 9 can move along the first direction, and its maximum movable position is a position where it contacts the second accommodating portion 22.

[0074] The lower valve port V3 is located on the valve seat 10. The valve seat 10 is a relatively fixed component, its outer periphery being fixed within the lower valve body 1. The valve seat 10 cooperates with the valve stem 9 to control the opening and closing of the lower valve port V3. Specifically, the valve stem 9 extends through the lower valve port V3, with a clearance fit between the valve stem 9 and the lower valve port V3, forming an annular gap.

[0075] In this embodiment, the valve stem 9 is moved up and down by the combined force of the pressure-regulating spring, the input pressure, and the reset member 8 (e.g., a return spring), thereby opening and closing the upper valve port V1 or the lower valve port V3. The return spring applies an upward force to the valve stem 9, closing the lower valve port V3.

[0076] Specifically, the valve stem 9 can be in the form of a stepped shaft with variable diameter, comprising a first shaft section with a smaller diameter and a second shaft section with a larger diameter. A stepped portion is formed at the transition between the first and second shaft sections. The first shaft section passes through the lower valve port V3, meaning its diameter is smaller than the aperture of the lower valve port V3. The second shaft section can be positioned by the stepped portion, meaning its diameter is larger than the aperture of the lower valve port V3.

[0077] When the input pressure is greater than the pressure set by the pressure regulating operating part 13, the stepped portion of the valve stem 9 can contact the lower valve port V3, and the lower valve port V3 is closed; when the input pressure is less than the pressure set by the pressure regulating operating part 13, the stepped portion of the valve stem 9 is separated from the lower valve port V3, and the lower valve port V3 is opened, so that the output pressure is not greater than the set pressure value.

[0078] A through hole is provided at the lower portion of the lower valve body 1. The extending direction of the through hole (hereinafter referred to as the second direction) can be perpendicular or nearly perpendicular to the first direction. Of course, the extending direction of the through hole can also be at a certain angle to the first direction. Specifically, in the embodiment illustrated in the present application, the second direction is perpendicular to the first direction. A guide sleeve 5 and a piston rod 6 are installed in sequence in the through hole.

[0079] The piston rod 6 can move along the second direction (ie left and right) under the action of the control pressure. The piston rod 6 is a component that cooperates with the guide sleeve 5 to realize gas path switching.

[0080] The piston rod 6 as a whole may be an axial section extending longitudinally along the second direction. Two grooves are provided at intervals on the outer wall of the piston rod 6 . The grooves are used to cooperate with the guide sleeve 5 to form a third cavity 20 .

[0081] In this embodiment, an input port 15, an output port 16 and an exhaust port 17 are provided at the bottom of the lower valve body 1. The guide sleeve 5 is a component used to isolate the output port 16, the output port 16 and the exhaust port 17 of the dual-pulse solenoid valve to achieve air path switching. Both ends of the guide sleeve 5 protrude from the through hole, and side covers 3 are sealed at both ends of the guide sleeve 5. In addition, the side cover 3 is also connected to the lower valve body 1 in a detachable manner. Specifically, the detachable connection method can be a bolt connection, a screw connection, or the like that can conveniently fix the two and is easy to assemble and disassemble. A push rod 4 that can move back and forth along the second direction is provided inside the side cover 3, and the push rod 4 can drive the piston rod 6 to move along the second direction.

[0082] Among them, the driving force for driving the push rod 4 can be any one or more combinations of manual and electric forms. When the driving force for driving the push rod 4 includes electric form, the double-pulse solenoid valve can include a coil assembly 2, and the coil assembly 2 is mainly used to control the switch of the pilot valve port V2. After the coil assembly 2 is energized, it can drive the push rod 4 to move along the second direction. Specifically, the force used by the coil assembly 2 to drive the push rod 4 to move can be in the form of pneumatic or hydraulic. Take the pneumatic form of the force used by the coil assembly 2 to drive the push rod 4 as an example.

[0083] The side cover 3 is provided with a pilot chamber, which is equipped with a drive flow channel connected to the ejector pin 4. A pilot valve port V2 is provided in the pilot chamber. A sealing member may be provided on the pilot valve port V2. When the coil assembly 2 is energized, the sealing member separates from the pilot valve port V2, opening the pilot valve port V2. Driving air pressure can flow through the pilot chamber and the drive flow channel to the ejector pin 4, thereby driving the ejector pin 4 to move in the second direction.

[0084] Among them, the push rod 4 can specifically be in the form of a variable diameter shaft arranged with a variable diameter along the second direction, forming a limit step at two positions with different diameters, and the end of the driving channel can be set corresponding to the limit step, so that the driving force acts on the limit step, reliably pushing the push rod 4 to move along the second direction.

[0085] When the driving force for driving the push rod 4 is manual, the push rod 4 can be used as a manual control component, and can also enable the valve to switch the gas path in the absence of electricity.

[0086] Specifically, the number of groups of the coil assembly 2, the side cover 3 and the push rod 4 can be two groups, the left side can be the first coil assembly 2, the first side cover 3 and the first push rod 4; the right side can be the second coil assembly 2, the second side cover 3 and the second push rod 4. When the first coil assembly 2 and the second coil assembly 2 are started alternately, the first push rod 4 can be moved to the right and the second push rod 4 can be moved to the left, and the pilot pressure is used to push the piston rod 6 to move to realize the switching of the air path.

[0087] It should be noted that: the position where the airtight seal is required in the above-mentioned dual-pulse solenoid valve can be achieved by setting a sealing structure such as a sealing ring 7. Specifically, the sealing ring 7 can adopt a sealing structure such as an O-ring or a K-ring.

[0088] The dual-pulse solenoid valve provided in the embodiment of the present application can realize the following functions: setting the output pressure value, switching the gas path, regulating the flow rate and overflow, etc. Specifically, the principle and process of its realization are analyzed as follows:

[0089] Adjust the output pressure value:

[0090] The input port 15 of the dual-pulse solenoid valve is always connected to the second chamber 19. In the initial state without wind pressure, the pressure-regulating spring is compressed by rotating the pressure-regulating screw, forming a spring preload. This pressure causes the piston seat 11 to move downward, ultimately pushing the valve stem 9 downward, and the lower valve port V3 opens.

[0091] When air pressure is input into the second chamber 19, which is connected to the input port 15, and the force acting on the piston seat 11 is less than the force exerted by the pressure-regulating spring on the piston seat 11, the air pressure in the third chamber 20 equals the air pressure in the second chamber 19. When the force exerted by the air pressure in the second chamber 19 on the piston seat 11 is greater than the force exerted by the pressure-regulating spring on the piston seat 11, the piston seat 11 moves upward, and the valve stem 9 moves upward under the force of the return spring, closing the lower valve port V3 and keeping the pressure in the third chamber 20 below the set pressure. The greater the compression of the pressure-regulating spring, the greater the maximum pressure in the third chamber 20.

[0092] Gas circuit switching:

[0093] When the right coil assembly 2 is energized or the right push rod 4 is pressed, the piston rod 6 will move to the left, and at this time it is connected with the output port 16 of the double-pulse solenoid valve through the third chamber 20, that is, the input port 15 and the output port 16 of the double-pulse solenoid valve are connected, and the exhaust port 17 is cut off; when the left coil assembly 2 is energized or the left push rod 4 is pressed, the piston rod 6 will move to the right, and at this time the third chamber 20 and the output port 16 are cut off, that is, the input port 15 and the output port 16 of the double-pulse solenoid valve are cut off, the output port 16 and the exhaust port 17 are connected through the guide sleeve 5, and the output port 16 is discharged by wind pressure.

[0094] Traffic changes:

[0095] The diameters of the input port 15 and the exhaust port 17 are relatively large, while the diameter of the air path 25 connecting the pressure regulating mechanism and the third chamber 20 is relatively small, forming a throttling effect, so that the valve has the characteristics of small air filling flow but large air exhaust flow.

[0096] Overflow function:

[0097] When the wind pressure downstream of the double-pulse solenoid valve increases abnormally (pressure at the output port 16 > pressure at the input port 15 > set pressure value), the lower valve port V3 is closed, and the piston seat 11 moves upward under the action of the wind pressure at the output port 16, causing the upper valve port V1 to open. The pressure at the output port 16 is discharged from the overflow port 23 through the upper valve port V1, until the pressure at the output port 16 is lower than the set pressure, at which point the upper valve port V1 is closed and the lower valve port V3 is opened.

[0098] On the whole, the dual-pulse solenoid valve provided in the embodiment of the present application is a dual-pulse solenoid valve with adjustable output pressure for rail vehicles. The output pressure is adjustable, the charging flow is small, and the exhaust flow is large, which can reduce the impact load on the parking cylinder spring; it has an overflow protection function, which can ensure that when the wind pressure downstream of the dual-pulse solenoid valve increases abnormally, the overflow port 23 of the solenoid valve pressure regulating mechanism will discharge excess wind pressure to protect the parking cylinder spring.

[0099] It should be noted that, in the description of this application, the terms "first," "second," etc., are used solely for descriptive purposes and to distinguish similar objects. There is no order of precedence between the two, nor should they be understood to indicate or imply relative importance. Furthermore, in the description of this application, unless otherwise specified, "plurality" means two or more.

[0100] The above-mentioned various embodiments in this specification are described in a progressive manner. The same or similar parts between the various embodiments can be referenced to each other. Each embodiment focuses on the differences from other embodiments.

[0101] The above are only a few embodiments of the present invention. Although the embodiments disclosed in the present invention are as above, the contents are only embodiments adopted to facilitate understanding of the present invention and are not intended to limit the present invention. Any person skilled in the art of the present invention may make any modifications and changes in the form and details of the embodiments without departing from the spirit and scope disclosed in the present invention. However, the scope of patent protection of the present invention shall still be based on the scope defined by the appended claims.

Claims

1. A double pulse solenoid valve, characterized in that: The double-pulse solenoid valve includes: a pressure regulating mechanism and a plunger mechanism, The pressure regulating mechanism includes: a valve body, a pressure regulating operating portion arranged along a first direction, a pressure regulating component, a piston seat, a valve stem, and a reset member; the valve body includes a detachably connected upper valve body and a lower valve body; a first cavity is formed in the upper valve body, an overflow port is provided on the upper valve body, a valve seat is provided in the lower valve body, an upper valve port is provided on the piston seat, and a lower valve port is provided on the valve seat; at least a second cavity, an input port, an output port, and an exhaust port are provided in the lower valve body; The plunger mechanism includes: a piston rod, a guide sleeve sleeved outside the piston rod, a third chamber provided between the guide sleeve and the piston rod; an air path connected to the third chamber provided in the pressure regulating mechanism; the diameter of the air path is smaller than the diameters of the input port and the exhaust port; the pressure in the third chamber is not higher than a set pressure value; when the pressure at the output port is greater than the pressure at the input port and greater than the set pressure value, the upper valve port opens, and the pressure at the output port can be discharged from the overflow port through the upper valve port; The upper valve body and the lower valve body are connected by threads, and a first accommodating portion for mounting the piston seat is formed at the position where the upper valve body and the lower valve body cooperate, and the piston seat can move along the first direction; the upper valve body is provided with an opening for passing the pressure regulating operating portion, and the pressure regulating operating portion passes through the opening and extends into the first cavity, and the pressure regulating component is a pressure regulating spring, one end of the pressure regulating spring is connected to the pressure regulating operating portion, and the other end is connected to the piston seat, and the pressure regulating spring is used to ensure that the output pressure of the double-pulse solenoid valve is not greater than the set value; The lower valve body is provided with a through hole extending along the second direction, the guide sleeve and the piston rod are installed in the through hole, and the plunger mechanism further includes side covers, which are sealingly sleeved on both ends of the guide sleeve.

2. The double pulse solenoid valve according to claim 1, characterized in that: An accommodating chamber for accommodating the valve stem and the valve seat is provided in the lower valve body. When the valve stem contacts the valve seat, the accommodating chamber in the lower valve body is divided into a fourth chamber located between the valve seat and the piston seat, and the second chamber. The fourth chamber is connected to the third chamber through the air path. The second chamber is used as an input pressure chamber for connecting to the input port. The input port can be connected to the brake air pressure to supply air to the double-pulse solenoid valve.

3. The double-pulse solenoid valve according to claim 2, characterized in that: A second accommodating portion for mounting the valve seat is provided in the lower valve body. When the valve stem moves along the first direction, the valve stem cooperates with the valve seat to realize the opening and closing of the lower valve port.

4. The double-pulse solenoid valve according to claim 3, characterized in that: The valve stem is an overall stepped shaft with a variable diameter, including a first shaft segment with a smaller diameter and a second shaft segment with a larger diameter. A stepped portion is formed at the transition between the first shaft segment and the second shaft segment. The first shaft segment passes through the lower valve port. The diameter of the first shaft segment is smaller than the aperture of the lower valve port, and the diameter of the second shaft segment is larger than the aperture of the lower valve port. When the input pressure is greater than the pressure set by the pressure regulating operating part, the stepped portion of the valve stem can contact the lower valve port and close the lower valve port; when the input pressure is less than the pressure set by the pressure regulating operating part, the stepped portion of the valve stem separates from the lower valve port and the lower valve port opens.

5. The double-pulse solenoid valve according to claim 1, characterized in that: The plunger mechanism further includes a push rod, which is installed in the side cover and can move along the second direction to drive the piston rod to move.

6. The double-pulse solenoid valve according to claim 5, characterized in that: The plunger mechanism also includes a coil assembly, a pilot chamber is provided in the side cover, a pilot valve port is provided in the pilot chamber, and a sealing member for closing the pilot valve port. When the coil assembly is energized, the sealing member is separated from the pilot valve port, driving air pressure to flow through the pilot chamber to the push rod, driving the push rod and the piston rod to move along the second direction.

7. The double-pulse solenoid valve according to claim 6, characterized in that: The coil assembly includes a left coil assembly and a right coil assembly, and the ejector rod includes a right ejector rod and a left ejector rod. When the right coil assembly is energized or pressed, the piston rod can move to the left and communicate with the output port through the third chamber, and the exhaust port is cut off. When the left coil assembly is energized or pressed, the piston rod can move to the right, the third chamber is cut off from the output port, and the output port is connected to the exhaust port through the guide sleeve.

Images