Normally open large flow switching solenoid valve and hydraulic control unit for automobile brake system

Abstract

The application provides a normally open large-flow switching electromagnetic valve and a hydraulic control unit of an automobile brake system. The electromagnetic valve comprises an electromagnetic coil, a valve shell, a moving iron, a valve core, a small-flow valve seat and a large-flow valve seat. An accommodating space is formed in the valve shell. The valve core, the small-flow valve seat and the large-flow valve seat are sequentially arranged in the accommodating space from top to bottom. The valve core is connected with the moving iron, and the electromagnetic coil is arranged around the moving iron and the valve shell. A first elastic member is arranged between the valve core and the small-flow valve seat. The small-flow valve seat and the large-flow valve seat are connected through a second elastic member. When the electromagnetic coil is powered off, the valve core opens a small-flow port, and the small-flow valve seat opens a large-flow port, so that the electromagnetic valve is opened with large flow. When the electromagnetic coil is powered on, the valve core closes the small-flow port, and the small-flow valve seat closes the large-flow port, so that the electromagnetic valve is closed. The application can satisfy the normally open and large-flow capacity of the electromagnetic valve, so as to realize rapid pressure regulation.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of automobiles, in particular to a normally open large-flow switching electromagnetic valve and a hydraulic control unit of an automobile braking system. BACKGROUND

[0002] In the related art, the existing normally open electromagnetic valve for regulating vehicle braking pressure usually has a small valve port size and weak flow capacity, which increases the braking time of commercial vehicles with large wheel cylinders and large amounts of required brake fluid. To solve this problem, the existing normally open electromagnetic valve can only compensate by increasing the valve port diameter. However, after increasing the valve port diameter, the flow rate of the electromagnetic valve increases, and the spring force of the electromagnetic valve needs to be increased, otherwise the electromagnetic valve will be closed under the action of Bernoulli's principle. Increasing the spring force of the electromagnetic valve will increase the demand for electromagnetic force and electromagnetic coil current, which will worsen the power consumption and heat generation of the electromagnetic coil. Meanwhile, after the normally open valve with an increased valve port diameter is closed under the action of the electromagnetic coil, when a certain pressure appears at the oil outlet of the electromagnetic valve, the electromagnetic valve core will naturally open under the action of hydraulic pressure against the electromagnetic force, causing the electromagnetic valve to fail to seal. SUMMARY

[0003] The present application provides a normally open large-flow switching electromagnetic valve and a hydraulic control unit of an automobile braking system to solve the defects in the prior art and achieve the following technical effects: the electromagnetic valve inlet and outlet can be normally open and maintain a large flow capacity, a large amount of brake fluid can be passed in a short time, the time required for the vehicle wheel cylinder and other brake control modules to reach the required pressure can be shortened, and rapid pressure regulation can be achieved. Meanwhile, when the electromagnetic valve is closed under the action of the electromagnetic force, the electromagnetic valve can maintain good sealing performance, and the applicable working conditions of the electromagnetic valve are more extensive.

[0004] According to the normally open large-flow switching electromagnetic valve of the first aspect of the present application, the electromagnetic valve comprises an electromagnetic coil, a valve housing, a moving iron, a valve core, a small-flow valve seat and a large-flow valve seat.

[0005] The inside of the valve housing forms an accommodation space penetrating through the upper and lower ends thereof, the valve core, the small-flow valve seat and the large-flow valve seat are sequentially arranged in the accommodation space from top to bottom, the upper end of the valve core is connected with the moving iron, and the electromagnetic coil is arranged around the moving iron and the valve housing, a first elastic member is arranged between the valve core and the small-flow valve seat, the small-flow valve seat and the large-flow valve seat are connected through a second elastic member, and the small-flow valve seat and the valve core are slidably arranged along the central axis direction of the accommodation space.

[0006] The lower end of the valve core is provided with a first closing part for closing or opening a small flow port of the small flow valve seat, the lower end of the small flow valve seat is provided with a second closing part for closing or opening a large flow port of the large flow valve seat, and the valve outlet formed by the small flow port, the large flow port and the containing space lower end communicates in sequence.

[0007] In the case that the electromagnetic coil is powered off, the valve core opens the small flow port, the small flow valve seat opens the large flow port, so that the large flow switching electromagnetic valve is opened in large flow; in the case that the electromagnetic coil is powered on, the valve core closes the small flow port, the small flow valve seat closes the large flow port, so that the large flow switching electromagnetic valve is closed.

[0008] According to an embodiment of the present application, the containing space is further provided with a valve seat limiting part between the valve core and the small flow valve seat, and the valve seat limiting part divides the containing space into a first space on the upper side and a second space on the lower side, and the first space and the second space communicate through a through hole at the center of the valve seat limiting part.

[0009] The small flow valve seat passes through the through hole and enters the second space, and the upper surface of the valve seat limiting part abuts against the lower end of the first elastic member, and the lower surface of the valve seat limiting part abuts against the limiting boss of the small flow valve seat.

[0010] According to an embodiment of the present application, the valve seat limiting part is integrally formed with the valve shell, and the inside of the valve shell extends inwardly to form the annular valve seat limiting part.

[0011] Alternatively, the valve seat limiting part is manufactured separately from the valve shell, and the valve seat limiting part is pressed into the valve shell through interference fit.

[0012] According to an embodiment of the present application, the valve shell is provided with a valve inlet and a valve through port, the valve through port communicates to the first space, and the valve inlet communicates to the second space; when the large flow switching electromagnetic valve is applied in a hydraulic control unit, the first space and the second space communicate through the valve inlet and the valve through port to realize pressure balance.

[0013] In the case that the electromagnetic coil is powered off, the valve through port communicates to the valve outlet through the first space, the small flow port and the large flow port in sequence, and the valve inlet communicates to the valve outlet through the second space and the large flow port in sequence; a sealing ring is fixedly sleeved on the outer periphery of the large flow valve seat and abuts against the inner wall of the second space.

[0014] According to one embodiment of the present application, the large flow valve seat and the sealing ring are slidably arranged along the length direction of the valve shell; and an oil pressure space is defined between the outer circumferential surface of the large flow valve seat, the sealing ring and the inner wall of the accommodating space, and the oil pressure space only communicates with the valve outlet;

[0015] When the electromagnetic coil is energized and high pressure oil is supplied to the valve outlet and low pressure oil is supplied to the valve inlet, the high pressure oil enters the oil pressure space to push the large flow valve seat to slide towards the small flow valve seat, at this time, the valve core closes the small flow port, the small flow valve seat closes the large flow port, and the limiting boss of the small flow valve seat abuts against the valve seat limiting portion.

[0016] According to one embodiment of the present application, a plurality of second oil passing grooves are further formed on the outer circumferential surface of the large flow valve seat between the sealing ring and the valve outlet, and the second oil passing grooves extend along the length direction of the valve shell and communicate with the valve outlet;

[0017] The second oil passing grooves, the sealing ring and the inner wall of the accommodating space define the oil pressure space.

[0018] According to one embodiment of the present application, the first elastic member is a first spring and the second elastic member is a second spring;

[0019] When the electromagnetic coil is energized, the downward electromagnetic force is greater than the sum of the upward first spring force and the second spring force, the moving iron presses the first closing portion of the valve core against the small flow valve seat, and the second closing portion of the small flow valve seat is pressed against the large flow valve seat, at this time, the first spring and the second spring are in compressed state;

[0020] When the electromagnetic coil is de-energized, the first spring pushes the valve core away from the small flow valve seat by elastic force, and the second spring pushes the small flow valve seat away from the large flow valve seat by elastic force.

[0021] According to one embodiment of the present application, the first closing portion is a spherical closing member, and a small valve port sealing conical surface is formed at the small flow port to cooperate with the spherical closing member.

[0022] According to one embodiment of the present application, the second closing portion is a sealing spherical arc surface formed at the bottom of the small flow valve seat, and a large valve port sealing conical surface is formed at the large flow port to cooperate with the sealing arc surface.

[0023] The hydraulic control unit of the automobile brake system according to the second aspect of the present application comprises the normally open large-flow switching electromagnetic valve according to the first aspect of the present application, and further comprises a pressure control module, wherein the normally open large-flow switching electromagnetic valve is installed in the pressure control module.

[0024] The present application provides a normally open large-flow switching electromagnetic valve for a brake pressure control module of an automobile brake system, which can satisfy the requirements of keeping the inlet and outlet of the electromagnetic valve open and maintaining a large flow capacity, pass a large amount of brake fluid in a short time, shorten the time for the wheel cylinder and other brake control modules to reach the required pressure, and thus realize rapid pressure regulation and control. When the electromagnetic valve is closed under the action of electromagnetic force, the electromagnetic valve can maintain good sealing performance, and the application conditions of the electromagnetic valve are more extensive.

[0025] In addition, the present application has at least the following advantages compared with the related art.

[0026] (1) Large-flow opening capacity in normally open state: In the case of power-off of the electromagnetic coil, the electromagnetic valve automatically maintains an open state, i.e., a normally open state. In this state, the electromagnetic valve can realize large-flow opening, which means that a large amount of brake fluid can pass in a short time. This helps to shorten the time for the wheel cylinder to reach the required pressure, thereby realizing faster pressure regulation.

[0027] (2) Rapid response and pressure regulation: The electromagnetic valve can pass a large amount of brake fluid in a short time, which helps to improve the response speed of the brake system. Rapid pressure regulation is particularly important in emergency braking situations, which can significantly improve driving safety.

[0028] (3) Good sealing performance: When the electromagnetic coil is powered on, the electromagnetic valve can be reliably closed to ensure good sealing performance. This efficient sealing capability helps to prevent brake fluid leakage and ensures the stability and reliability of the brake system.

[0029] (4) Good bidirectional pressure resistance: When the electromagnetic coil is powered on, the electromagnetic valve can ensure sealing in the closed state when there is a large positive pressure difference or a large negative pressure difference between the inlet and the outlet of the valve.

[0030] In summary, the present application, through its unique structural design and working principle, not only improves the large-flow opening capacity of the electromagnetic valve in the normally open state, but also ensures good sealing performance in the closed state, thereby improving the performance and safety of the entire brake system. BRIEF DESCRIPTION OF DRAWINGS

[0031] In order to make the technical solutions in the present application or prior art clearer, the accompanying drawings needed in the embodiments or prior art description will be briefly introduced. Obviously, the accompanying drawings in the following description are only some embodiments of the present application, and other drawings can be obtained by those skilled in the art without any creative effort based on these drawings.

[0032] Figure 1 is a structural schematic diagram of a large-flow switching electromagnetic valve provided by the present application.

[0033] Figure 2 is a structural schematic diagram of a large-flow switching electromagnetic valve provided by the present application.

[0034] Figure 3 is a structural schematic diagram of a valve shell provided by the present application.

[0035] Figure 4 is a structural schematic diagram of a small-flow valve seat provided by the present application.

[0036] Figure 5 is a structural schematic diagram of a large-flow valve seat provided by the present application.

[0037] Figure 6 is a structural schematic diagram of a large-flow switching electromagnetic valve when the electromagnetic coil is powered off.

[0038] Figure 7 is a structural schematic diagram of a large-flow switching electromagnetic valve when the electromagnetic coil is powered on and the valve inlet is connected to high-pressure oil.

[0039] Figure 8 is a structural schematic diagram of a large-flow switching electromagnetic valve when the electromagnetic coil is powered on and the valve outlet is connected to high-pressure oil.

[0040] Figure 9 is a partial structural schematic diagram of a large-flow switching electromagnetic valve provided by the present application.

[0041] Figure 10 is a partial structural schematic diagram of a large-flow switching electromagnetic valve provided by the present application.

[0042] Figure 11 is a partial structural schematic diagram of a large-flow switching electromagnetic valve provided by the present application.

[0043] Figure 12 is a partial structural schematic diagram of a large-flow switching electromagnetic valve provided by the present application.

[0044] Figure 13 is a structural schematic diagram of a hydraulic control unit of an automobile braking system provided by the present application.

[0045] Reference signs:

[0046] 1, large flow switching electromagnetic valve; 2, electromagnetic coil; 2.1, power supply pin; 3, magnetic isolation tube; 4, moving iron; 5, valve core; 6, first elastic member; 7, valve shell; 7.1, valve inlet; 7.2, valve opening; 7.3, valve seat limiting part; 8, limiting baffle; 9, small flow valve seat; 9.1, small valve opening sealing cone surface; 9.2, second closed part; 10, second elastic member; 11, sealing ring; 12, large flow valve seat; 12.1, large valve opening sealing conical surface; 12.2, second oil groove; 13, valve outlet; 14, small flow opening; 15, large flow opening; 16, hydraulic control unit; 17, pressure control module. DETAILED DESCRIPTION

[0047] In order to make the objects, technical solutions and advantages of the present application clearer, the technical solutions in the present application will be described clearly and completely below in combination with the drawings in the present application. Obviously, the described embodiments are part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0048] In the description of the embodiments of the present application, it should be noted that the orientations or positional relationships indicated by the terms "center", "longitudinal", "transverse", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the embodiments of the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the embodiments of the present application. In addition, the terms "first", "second", "third" are only for the purpose of description, and cannot be understood as indicating or implying relative importance.

[0049] In the description of the embodiments of the present application, it should be noted that unless otherwise explicitly specified and limited, the terms "connected", "connected" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or integrally connected; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium. For those skilled in the art, the specific meaning of the above terms in the embodiments of the present application can be understood according to the specific circumstances.

[0050] In the embodiments of the present application, unless otherwise explicitly specified and limited, the first feature is "on" or "under" the second feature, which can be that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, the first feature can be "above", "over" and "on" the second feature, which can be that the first feature is directly above or obliquely above the second feature, or only means that the first feature is higher in horizontal height than the second feature. The first feature can be "under", "below" and "under" the second feature, which can be that the first feature is directly below or obliquely below the second feature, or only means that the first feature is lower in horizontal height than the second feature.

[0051] A normally open large flow switching electromagnetic valve 1 and a hydraulic control unit 16 of an automobile brake system having the same are described below with reference to the accompanying drawings.

[0052] As shown in the drawings, the normally open large flow switching electromagnetic valve 1 according to the first aspect of the present application comprises an electromagnetic coil 2, a valve housing 7, a moving iron 4, a valve core 5, a small flow valve seat 9 and a large flow valve seat 12. Figures 1 to 13

[0053] The inside of the valve housing 7 is formed with an accommodation space penetrating through the upper and lower ends thereof, the valve core 5, the small flow valve seat 9 and the large flow valve seat 12 are sequentially arranged in the accommodation space from top to bottom, the upper end of the valve core 5 is connected with the moving iron 4 (for example, the upper end of the valve core 5 is in contact with the moving iron 4, etc., which is not particularly limited in the present application), and the electromagnetic coil 2 is arranged around the moving iron 4 and the valve housing 7, a first elastic member 6 is arranged between the valve core 5 and the small flow valve seat 9, the small flow valve seat 9 and the large flow valve seat 12 are connected through a second elastic member 10, and the small flow valve seat 9 and the valve core 5 are slidably arranged along the central axis direction of the accommodation space. A limiting baffle 8 is further arranged in the valve housing 7, the limiting baffle 8 is located in the valve outlet 13 and is in interference fit with the valve housing 7, and the upper surface of the limiting baffle 8 is in contact with the valve housing 7

[0054] The lower end of the valve core 5 is provided with a first closing part for closing or opening the small flow port 14 of the small flow valve seat 9, the lower end of the small flow valve seat 9 is provided with a second closing part 9.2 for closing or opening the large flow port 15 of the large flow valve seat 12, and the small flow port 14, the large flow port 15 and the valve outlet 13 formed at the lower end of the accommodation space are sequentially communicated.

[0055] In the case that the electromagnetic coil 2 is de-energized, the valve core 5 opens the small flow port 14, and the small flow valve seat 9 opens the large flow port 15, so that the large flow switching electromagnetic valve 1 is opened in large flow; in the case that the electromagnetic coil 2 is energized, the valve core 5 closes the small flow port 14, and the small flow valve seat 9 closes the large flow port 15, so that the large flow switching electromagnetic valve 1 is closed.

[0056] ​According to the embodiment of the present invention, the large-flow switching solenoid valve 1 can maintain a normally open state when the electromagnetic coil 2 is powered off, and can achieve high-flow opening in the normally open state, thereby having a large flow capacity, being able to pass more brake fluid in a short time, shortening the time it takes for the vehicle wheel cylinder to reach the required pressure, and thus achieving rapid pressure regulation.

[0057] Specifically, the working principle and working process of the large flow switching solenoid valve 1 to achieve large flow while ensuring normal opening are as follows:

[0058] like Figure 1 As shown, when the electromagnetic coil 2 is de-energized, the valve housing 7 has no magnetic force (it will be understood that, in the structure of the present invention, the valve housing 7 is equivalent to the fixed iron). At this time, under the action of the first upward elastic force exerted by the first elastic member 6 on the valve core 5, the valve core 5 moves upward and moves the movable iron 4 away from the valve housing 7. At this time, the first sealing portion at the lower end of the valve core 5 moves away from the small flow valve seat 9, thereby opening the small flow port 14 of the small flow valve seat 9. Under the action of the second upward elastic force exerted by the second elastic member 10 on the small flow valve seat 9, the small flow valve seat 9 moves upward. At this time, the second sealing portion 9.2 at the lower end of the small flow valve seat 9 moves away from the high flow valve seat 12, thereby also opening the high flow port 15 of the high flow valve seat 12. Therefore, the liquid entering the accommodation space can flow out of the valve housing 7 through the small flow port 14 and the high flow port 15, so that the high flow switching solenoid valve 1 can achieve high flow operation in the normally open state.

[0059] like Figure 7 and 8 As shown, when the electromagnetic coil 2 is energized instead of de-energized, the valve housing 7 generates a magnetic force, and the moving iron 4 is acted upon by the downward magnetic force exerted by the valve housing 7. At this time, the valve core 5 is simultaneously acted upon by the first downward electromagnetic force exerted by the moving iron 4 and the first upward elastic force exerted by the first elastic member 6. Since the first electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and causes the first closing portion to close the small flow port 14 of the small flow valve seat 9; further, the small flow valve seat 9 is acted upon by the downward pressure force exerted by the valve core 5, and the small flow valve seat 9 is also acted upon by the second upward elastic force exerted by the second elastic member 10. Since the pressure force is greater than the second elastic force, the small flow valve seat 9 and the large flow valve seat 12 approach each other, so that the second closing portion 9.2 of the small flow valve seat 9 closes the large flow port 15 of the large flow valve seat 12, thereby realizing the closure of the large flow switching solenoid valve 1, and its sealing performance is good in the closed state.

[0060] In the related art, the existing normally open electromagnetic valve for vehicle brake pressure regulation usually has a small valve port size and weak flow capacity, which can increase the brake time of commercial vehicles with larger wheel cylinders and larger brake fluid requirements. If this problem needs to be solved, the existing normally open electromagnetic valve can only increase the valve port diameter to compensate. However, after the valve port diameter is increased, the flow rate of the electromagnetic valve is increased, and the spring force of the electromagnetic valve needs to be increased, otherwise the electromagnetic valve will be closed under the action of Bernoulli's principle. The increase of the spring force of the electromagnetic valve will increase the demand for electromagnetic force and electromagnetic coil current, which will worsen the power consumption and heat of the electromagnetic coil. At the same time, after the normally open valve with increased valve diameter is closed under the action of the electromagnetic coil, when a certain pressure appears at the oil outlet of the electromagnetic valve, the electromagnetic valve core naturally opens under the action of hydraulic pressure against the electromagnetic force, which causes the sealing failure of the electromagnetic valve.

[0061] Therefore, in order to solve the technical defects existing in the above related art, the present application provides a normally open large flow switching electromagnetic valve 1 for a vehicle brake system brake pressure control module 17, which can meet the normally open and large flow capacity of the electromagnetic valve inlet and outlet, can pass more brake fluid in a short time, shorten the time for the vehicle wheel cylinder and other brake control modules to reach the required pressure, and thus realize rapid pressure regulation. At the same time, when the electromagnetic valve is closed under the action of the electromagnetic force, the electromagnetic valve can maintain good sealing performance, and the applicable working conditions of the electromagnetic valve are more extensive.

[0062] In addition, the present application has at least the following advantages compared with the related art.

[0063] (1) Large flow opening capacity in normally open state: In the case of de-energization of the electromagnetic coil 2, the electromagnetic valve automatically maintains an open state, i.e. a normally open state. In this state, the electromagnetic valve can realize large flow opening, which means that a large amount of brake fluid can pass in a short time. This helps to shorten the time for the vehicle wheel cylinder to reach the required pressure, thereby realizing faster pressure regulation.

[0064] (2) Fast response and pressure regulation: The electromagnetic valve can pass a large amount of brake fluid in a short time, which helps to improve the response speed of the brake system. Fast pressure regulation is particularly important in emergency braking situations, which can significantly improve driving safety.

[0065] (3) Good sealing performance: When the electromagnetic coil 2 is energized, the electromagnetic valve can be reliably closed to ensure good sealing performance. This efficient sealing capability helps to prevent brake fluid leakage and ensures the stability and reliability of the brake system.

[0066] (4) Good bidirectional pressure resistance: When the electromagnetic coil 2 is energized, the valve inlet 7.1 and the valve outlet 13 have a large positive pressure difference or a large negative pressure difference, which can ensure the closing and sealing performance of the electromagnetic valve.

[0067] In conclusion, the present application, by virtue of its unique structural design and working principle, not only improves the large-flow opening capability of the electromagnetic valve in the normally open state, but also ensures good sealing performance in the closed state, thereby improving the performance and safety of the entire brake system.

[0068] As shown in Figure 3 According to some embodiments of the present application, a valve seat limiting portion 7.3 is further arranged in the accommodation space, located between the valve core 5 and the small-flow valve seat 9, and dividing the accommodation space into a first space on the upper side and a second space on the lower side, which are communicated through a through hole at the center of the valve seat limiting portion 7.3.

[0069] The small-flow valve seat 9 passes through the through hole and enters the second space, and the upper surface of the valve seat limiting portion 7.3 abuts against the lower end of the first elastic member 6, and the lower surface of the valve seat limiting portion 7.3 abuts against the limiting boss of the small-flow valve seat 9.

[0070] It can be understood that the upper surface of the valve seat limiting portion 7.3 is in contact with the lower end of the first elastic member 6, which serves to support the first elastic member 6; and the lower surface of the valve seat limiting portion 7.3 is in contact with the limiting boss of the small-flow valve seat 9, which limits the movement range of the small-flow valve seat 9. That is, the main purpose of the valve seat limiting portion 7.3 is to limit the position of the small-flow valve seat 9, so as to avoid the small-flow valve seat 9 from moving beyond the lower surface of the valve seat limiting ring during movement.

[0071] Specifically, in the case that the electromagnetic coil 2 is de-energized, since neither the valve core 5 nor the small-flow valve seat 9 is subjected to electromagnetic force, the small-flow valve seat 9 will move upward under the pushing action of the second elastic member 10, that is, move toward the valve seat limiting portion 7.3, at which time the valve seat limiting portion 7.3 can avoid the small-flow valve seat 9 from causing the small-flow port 14 to be closed again due to excessive movement, that is, avoid the small-flow valve seat 9 from cooperating with the first closing portion under the pushing force to mistakenly close the small-flow port 14.

[0072] As shown in Figure 3 Further, the valve seat limiting portion 7.3 is integrally formed with the valve housing 7, and the inside of the valve housing 7 extends inwardly to form the annular valve seat limiting portion 7.3.

[0073] It can be understood that the valve seat limiting portion 7.3 and the valve housing 7 are made in the same manufacturing process, rather than being separately manufactured and then assembled together. The valve seat limiting portion 7.3 divides the accommodation space into two parts through its annular structure, which can better control the positions and movements of different components.

[0074] This one-piece design increases the strength of the overall structure and reduces the risk of leakage at the joints. It also reduces assembly steps, simplifies the manufacturing process, and helps reduce production costs.

[0075] Alternatively, the valve seat limiting portion 7.3 and the valve housing 7 are manufactured separately, wherein the valve seat limiting portion 7.3 is pressed into the valve housing 7 by interference fit.

[0076] like Figure 3 As shown, according to some embodiments of the present invention, a valve inlet 7.1 and a valve port 7.2 are provided on the valve housing 7, the valve port 7.2 is connected to the first space, and the valve inlet 7.1 is connected to the second space, and when the electromagnetic coil 2 is powered off, the valve port 7.2 is connected to the valve outlet 13 through the first space, the small flow port 14 and the large flow port 15 in sequence, and the valve inlet 7.1 is connected to the valve outlet 13 through the second space and the large flow port 15 in sequence.

[0077] Furthermore, when a large flow switching solenoid valve is used in the hydraulic control unit 16, the first space and the second space are connected through the valve inlet 7.1 and the valve port 7.2 to achieve pressure balance.

[0078] It should be pointed out that when a large-flow switching solenoid valve is applied to the hydraulic control unit 16, a closed space is formed outside the valve inlet 7.1 and the valve port 7.2, and the first space and the second space can be connected by the valve inlet 7.1 and the valve port 7.2 in the closed space to achieve pressure balance.

[0079] Specifically, when the electromagnetic coil 2 is de-energized, the first and second spaces can achieve pressure equilibrium within the enclosed space through the connection between the valve inlet 7.1 and the valve port 7.2. This ensures smooth flow of the medium between the valve inlet 7.1 and the valve outlet 13, preventing pressure differentials from affecting the smooth flow of the solenoid valve and ensuring the effective flow of the solenoid valve. Furthermore, when the electromagnetic coil 2 is de-energized, the first and second spaces can achieve pressure equilibrium within the enclosed space through the connection between the valve inlet 7.1 and the valve port 7.2. This gradually reduces the pressure differential between the valve inlet 7.1 and the valve outlet 13, facilitating smooth opening of the solenoid valve.

[0080] In the related art, the existing pressure control large flow switching electromagnetic valves are mainly divided into normally open type, normally closed type and pilot type large flow switching electromagnetic valves, but in the above existing large flow switching electromagnetic valves, a seal cannot be formed under different working conditions of bidirectional pressure difference, that is, the existing large flow switching electromagnetic valves for vehicle brake pressure regulation only have a one-way sealing function, and when the pressure of the brake pipeline reverses and reaches a certain pressure difference, the large flow switching electromagnetic valve core naturally opens under the action of hydraulic pressure, without sealing function. Based on the above existing large flow switching electromagnetic valve, if bidirectional sealing is required in the automobile brake system, the number of large flow switching electromagnetic valves in the pipeline needs to be increased, thereby causing the complication of pipeline structure and control logic, and increasing the material cost and control cost.

[0081] Therefore, in order to solve the technical defects existing in the above related art, as shown in Figure 1 and 5 According to some embodiments of the present application, a sealing ring 11 abutting with the inner wall of the accommodating space is fixedly sleeved on the outer periphery of the large flow valve seat 12. The sealing ring 11 can ensure the sealing effect between the oil outlet and the oil inlet of the large flow switching electromagnetic valve 1.

[0082] As shown in Figure 1 and 5 Further, the large flow valve seat 12 and the sealing ring 11 are slidably arranged along the length direction of the valve shell 7; and an oil pressure space is defined between the outer peripheral surface of the large flow valve seat 12, the sealing ring 11 and the inner wall of the accommodating space, and the oil pressure space only communicates with the valve outlet 13.

[0083] For example, in the case that the electromagnetic coil 2 is energized and high-pressure oil is input to the valve outlet 13 and low-pressure oil is input to the valve inlet 7.1, the high-pressure oil enters the oil pressure space to push the large flow valve seat 12 to slide towards the direction close to the small flow valve seat 9, at this time, the valve core 5 closes the small flow port 14, the small flow valve seat 9 closes the large flow port 15, and the limiting boss of the small flow valve seat 9 abuts against the valve seat limiting portion 7.3.

[0084] For another example, in the case that the electromagnetic coil 2 is energized and high-pressure oil is input to the valve inlet 7.1 and low-pressure oil is input to the valve outlet 13, which is a normal condition in use and will not be specially introduced here, under the above condition, the large flow switching electromagnetic valve 1 of the present application can also achieve closed sealing.

[0085] In this way, based on the above structure, the large flow switching electromagnetic valve 1 of the present application can satisfy the valve port sealing of the oil inlet and outlet of the large flow switching electromagnetic valve 1 under different working conditions with positive pressure difference or negative pressure difference, and realize bidirectional sealing of pressure control.

[0086] As shown in Figure 1 and5 As shown in the drawings, in some embodiments of the present application, a plurality of second oil passing grooves 12.2 are formed on the outer circumferential surface of the large flow valve seat 12 between the sealing ring 11 and the valve outlet 13, the second oil passing grooves 12.2 extend along the length direction of the valve shell 7 and are communicated to the valve outlet 13. The oil pressure space is defined between the second oil passing grooves 12.2, the sealing ring 11 and the inner wall of the accommodating space.

[0087] As shown in the drawings, Figure 1 and 5 Further, the outer circumferential surface of the large flow valve seat 12 is formed with a limiting seat, the outer circumferential surface of the limiting seat is formed with an annular sealing installation groove, and the sealing ring 11 is fixed in the sealing installation groove.

[0088] It can be understood that, while the high pressure oil is delivered to the valve outlet 13, most of the high pressure oil will enter the large flow port 15, and a small part of the high pressure oil will enter the oil pressure space and flow to the sealing ring 11 through the second oil passing grooves 12.2, at this time, the high pressure oil will exert a pressure difference force on the sealing ring 11, thereby pushing the large flow valve seat 12 to move upward, i.e. in the direction of the small flow valve seat 9.

[0089] The specific working principle and working process of the large flow switching electromagnetic valve 1 with bidirectional sealing function of the present application are given in detail below. The concept of the bidirectional sealing function of the large flow switching electromagnetic valve 1 of the present application is explained as follows: the large flow switching electromagnetic valve 1 can realize sealing when the valve inlet 7.1 is connected to high pressure oil and the valve outlet 13 is connected to low pressure oil, and the large flow switching electromagnetic valve 1 can also realize sealing when the valve inlet 7.1 is connected to low pressure oil and the valve outlet 13 is connected to high pressure oil. The working principle and process of the large flow switching electromagnetic valve 1 under different working conditions are given below.

[0090] (I) The valve inlet 7.1 is connected to high pressure oil and the valve outlet 13 is connected to low pressure oil.

[0091] As shown in the drawings, Figure 7 Under this working condition, if the electromagnetic coil 2 is energized, the valve shell 7 generates a magnetic force, the moving iron 4 receives the downward electromagnetic force exerted by the valve shell 7, and the moving iron 4 transmits the downward electromagnetic force to the valve core 5 connected thereto. At this time, the valve core 5 receives the downward electromagnetic force transmitted by the valve shell 7 through the moving iron 4, and the valve core 5 also receives the upward first elastic force exerted by the first elastic member 6. It can be understood that, since the electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and approaches the small flow valve seat 9, thereby causing the first closed part to close the small flow port 14 of the small flow valve seat 9.

[0092] Furthermore, from the force analysis of the small flow valve seat 9 at this time, it can be seen that the small flow valve seat 9 is subjected to the downward pressure force applied by the valve core 5, and due to the pressure difference between the high-pressure oil above the small flow valve seat 9 (the high-pressure oil passed into the valve inlet 7.1) and the low-pressure oil below the small flow valve seat 9 (the low-pressure oil passed into the valve outlet 13), the small flow valve seat 9 is also subjected to the downward pressure differential force brought about by the pressure differential. Furthermore, the small flow valve is also subjected to the upward second elastic force transmitted by the second elastic member 10. At this time, the sum of the pressure force and the pressure differential force is greater than the second elastic force. Therefore, the small flow valve seat 9 moves downward, thereby causing the second closing portion 9.2 to close the large flow port 15 of the large flow valve seat 12.

[0093] Furthermore, a force analysis of the high-flow valve seat 12 at this time shows that the high-flow valve seat 12 is subjected to the downward driving force transmitted by the small-flow valve seat 9 and the downward driving force transmitted by the second elastic member 10. At this time, the high-flow valve seat 12 moves downward under the action of these two driving forces until the limit seat on the outer periphery of the high-flow valve seat 12 abuts against the limit block 8. The limit block 8 and the valve housing 7 have an interference fit, and the upper surface of the limit block 8 contacts the sink surface of the valve housing 7. At this time, the high-flow switching solenoid valve 1 is in the closed state.

[0094] (ii) Low-pressure oil is passed to the valve inlet 7.1 and high-pressure oil is passed to the valve outlet 13.

[0095] like Figure 8 As shown, under this working condition, if the electromagnetic coil 2 is energized, the valve housing 7 generates magnetic force, the moving iron 4 is subjected to the downward electromagnetic force exerted on it by the valve housing 7, and the moving iron 4 transmits the downward electromagnetic force to the valve core 5 connected thereto. At this time, a force analysis of the valve core 5 shows that the valve core 5 is subjected to the downward electromagnetic force transmitted by the valve housing 7 through the moving iron 4, and the valve core 5 is also subjected to the upward first elastic force exerted on it by the first elastic member 6. It can be understood that since the electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and approaches the small flow valve seat 9, thereby causing the first closing portion to close the small flow port 14 of the small flow valve seat 9.

[0096] When the high pressure oil is delivered to the valve outlet 13, the high pressure oil enters the oil pressure space and flows to the sealing ring 11 through the second oil groove 12.2, at this time, the low pressure oil from the valve inlet 7.1 is above the sealing ring 11, and the high pressure oil from the second oil groove 12.2 is below the sealing ring 11, under the pressure difference between the high pressure oil and the low pressure oil, the high pressure oil exerts an upward pressure difference force on the sealing ring 11. At this time, the force analysis of the large flow valve seat 12 shows that the large flow valve seat 12 is subjected to an upward pressure difference force, a downward second elastic force exerted by the second elastic member 10, and a downward pressure force exerted by the small flow valve seat 9, since the pressure difference force is greater than the downward pressure force exerted by the small flow valve seat 9 and the second elastic force, the large flow valve seat 12 is pushed upward, i.e. moves towards the small flow valve seat 9, pushing the small flow valve seat 9 to move upward until the small flow valve seat 9 abuts against the valve seat limiting portion 7.3, the large flow valve seat 12 and the small flow valve seat 9 no longer move, and the large flow port 15 is still closed. However, under the action of the electromagnetic force, the valve core 5 still contacts the small flow valve seat 9, and the small flow port 14 is still closed.

[0097] In summary, based on the above structure, the large flow switching electromagnetic valve 1 of the present application can realize the bidirectional sealing function.

[0098] As shown in Figure 1 , according to some embodiments of the present application, the first elastic member 6 is a first spring, and the second elastic member 10 is a second spring.

[0099] When the electromagnetic coil 2 is energized, the downward electromagnetic force is greater than the sum of the upward first spring force and the second spring force, the moving iron 4 presses the first sealing portion of the valve core 5 against the small flow valve seat 9, and the second sealing portion 9.2 of the small flow valve seat 9 is pressed against the large flow valve seat 12, at this time, the first spring and the second spring are in a compressed state.

[0100] When the electromagnetic coil 2 is de-energized, the first spring pushes the valve core 5 away from the small flow valve seat 9 by the elastic force, and the second spring pushes the small flow valve seat 9 away from the large flow valve seat 12 by the elastic force.

[0101] As shown in Figure 1 and 4 , in some specific embodiments of the present application, the first sealing portion is a spherical sealing member, and the small flow port 14 is formed with a small valve port sealing cone surface 9.1 which cooperates with the spherical sealing member. In this way, when the electromagnetic coil 2 is energized, the surface of the spherical sealing member is in close contact with the small valve port sealing cone surface 9.1, thereby forming a seal to prevent fluid from passing through the small flow port 14.

[0102] As shown in Figure 1 , 4As shown in Figs. 1 and 5, in some embodiments of the present application, the second closing part 9.2 is a sealing spherical arc surface formed at the bottom of the small flow valve seat 9, and a large valve port sealing conical surface 12.1 is formed at the large flow port 15 to match the sealing arc surface.

[0103] In this way, the above design enables the large flow switching electromagnetic valve 1 to maintain good sealing performance under high flow demand. When the electromagnetic coil 2 is energized, the sealing spherical arc surface of the second closing part 9.2 will be pressed against the large valve port sealing conical surface 12.1, and the geometric matching and material properties (such as elasticity or hardness) between them will ensure the sealing effect. The above design usually uses wear-resistant and corrosion-resistant materials to ensure the reliability of the seal under long-term use and high-pressure environment.

[0104] When the electromagnetic coil 2 is de-energized to open the large flow switching electromagnetic valve 1, the surface of the spherical closing part will separate from the small valve port sealing conical surface 9.1, and the sealing spherical arc surface will separate from the large valve port sealing conical surface 12.1, thereby allowing fluid to pass through the large flow port 15. For applications that require handling large amounts of fluid or high-pressure fluid, this design can provide the necessary control and safety.

[0105] It should be noted that the above embodiments of the first closing part and the second closing part 9.2 are only exemplary and do not constitute a specific limitation on the structure of the first closing part and the second closing part 9.2. The first closing part and the second closing part 9.2 of the present application can also take other closing structures, and the present application does not make special limitations here, as long as the first closing part can seal the small flow port 14 and the second closing part 9.2 can seal the large flow port 15, respectively.

[0106] A specific embodiment of the large flow switching electromagnetic valve 11 of the present application is described below with reference to the accompanying drawings.

[0107] As shown in Figs. 1 and 5, in some embodiments of the present application, the second closing part 9.2 is a sealing spherical arc surface formed at the bottom of the small flow valve seat 9, and a large valve port sealing conical surface 12.1 is formed at the large flow port 15 to match the sealing arc surface. Figures 1 to 12 The large flow switching electromagnetic valve 1 includes an electromagnetic coil 2, a valve housing 7, a moving iron 4, a valve core 5, a small flow valve seat 9, a large flow valve seat 12, a sealing ring 11, a first spring, and a second spring.

[0108] The inside of the valve housing 7 forms a containing space that penetrates through the upper and lower ends thereof, and the valve core 5, the small flow valve seat 9, and the large flow valve seat 12 are sequentially arranged from top to bottom in the containing space. The upper end of the valve core 5 is connected with the moving iron 4, and the electromagnetic coil 2 is arranged around the moving iron 4 and the valve housing 7. The first spring is arranged between the valve core 5 and the small flow valve seat 9, and the small flow valve seat 9 and the large flow valve seat 12 are connected by the second spring. The small flow valve seat 9 and the valve core 5 are slidably arranged along the central axis direction of the containing space.

[0109] The lower end of the valve core 5 is provided with a first closing part for closing or opening a small flow port 14 of the small flow valve seat 9, the lower end of the small flow valve seat 9 is provided with a second closing part 9.2 for closing or opening a large flow port 15 of the large flow valve seat 12, and the valve outlet 13 formed by the small flow port 14, the large flow port 15 and the lower end of the containing space are sequentially communicated.

[0110] The containing space is further provided with a valve seat limiting part 7.3 between the valve core 5 and the small flow valve seat 9, and the valve seat limiting part 7.3 divides the containing space into a first space on the upper side and a second space on the lower side, and the first space and the second space are communicated through a through hole at the center of the valve seat limiting part 7.3.

[0111] The small flow valve seat 9 passes through the through hole and enters the second space, and the upper surface of the valve seat limiting part 7.3 abuts against the lower end of the first elastic member 6, and the lower surface of the valve seat limiting part 7.3 abuts against the limiting boss of the small flow valve seat 9.

[0112] The valve housing 7 is provided with a valve inlet 7.1 and a valve through port 7.2, the valve through port 7.2 is communicated to the first space, the valve inlet 7.1 is communicated to the second space,

[0113] The large flow valve seat 12 and the sealing ring 11 are slidably arranged along the length direction of the valve housing 7; and an oil pressure space is defined between the outer peripheral surface of the large flow valve seat 12, the sealing ring 11 and the inner wall of the containing space, and the oil pressure space is only communicated to the valve outlet 13. A plurality of second oil passing grooves 12.2 are further formed on the outer peripheral surface of the large flow valve seat 12 between the sealing ring 11 and the valve outlet 13, the second oil passing grooves 12.2 extend along the length direction of the valve housing 7 and are communicated to the valve outlet 13. The second oil passing grooves 12.2, the sealing ring 11 and the inner wall of the containing space define the oil pressure space.

[0114] The outer peripheral surface of the large flow valve seat 12 further forms a limiting seat, an annular sealing installation groove is formed on the outer peripheral surface of the limiting seat, and the sealing ring 11 is fixed in the sealing installation groove. A limiting baffle 8 is further arranged below the limiting seat, the limiting baffle 8 is located at the valve outlet 13 and is used for limiting the large flow valve seat 12, so as to avoid the large flow valve seat 12 from exceeding the position of the valve outlet 13.

[0115] The specific working principle of the large flow switching electromagnetic valve 11 of the present application will be described below based on the above specific embodiment.

[0116] (1) as Figure 6As shown, when the electromagnetic coil 2 is de-energized, the valve housing 7 has no magnetic force. At this point, under the action of the first upward elastic force exerted by the first spring on the valve core 5, the valve core 5 moves upward, carrying the movable iron 4 away from the valve housing 7. The first sealing portion at the lower end of the valve core 5 moves away from the low-flow valve seat 9, thereby opening the low-flow port 14 of the low-flow valve seat 9. Furthermore, under the action of the second upward elastic force exerted by the second spring on the low-flow valve seat 9, the low-flow valve seat 9 moves upward. The second sealing portion 9.2 at the lower end of the low-flow valve seat 9 moves away from the high-flow valve seat 12, thereby also opening the high-flow port 15 of the high-flow valve seat 12. Therefore, liquid entering the accommodation space can flow out of the valve housing 7 through the low-flow port 14 and the high-flow port 15, allowing the high-flow switching solenoid valve 1 to achieve high-flow operation in the normally open state.

[0117] like Figure 9 As shown, the axial clearance L1 between the moving iron 4 and the valve housing 7 is larger than the sum of the axial clearance L2 between the valve core 5 and the small flow valve seat 9 and the axial clearance L3 between the small flow valve seat 9 and the large flow valve seat 12, that is, .

[0118] (2) If Figure 7 As shown, when the electromagnetic coil 2 is energized and high-pressure oil is passed into the valve inlet 7.1 and low-pressure oil is passed into the valve outlet 13: under this working condition, if the electromagnetic coil 2 is energized, the valve housing 7 generates magnetic force, the moving iron 4 is subjected to the downward electromagnetic force applied by the valve housing 7, and the moving iron 4 transmits the downward electromagnetic force to the valve core 5 connected thereto. At this time, a force analysis of the valve core 5 shows that the valve core 5 is subjected to the downward electromagnetic force transmitted by the valve housing 7 through the moving iron 4, and the valve core 5 is also subjected to the upward first elastic force applied by the first elastic member 6. It can be understood that since the electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and approaches the small flow valve seat 9, thereby causing the first closing portion to close the small flow port 14 of the small flow valve seat 9.

[0119] Furthermore, from the force analysis of the small flow valve seat 9 at this time, it can be seen that the small flow valve seat 9 is subjected to the downward pressure force applied by the valve core 5, and due to the pressure difference between the high-pressure oil above the small flow valve seat 9 (the high-pressure oil passed into the valve inlet 7.1) and the low-pressure oil below the small flow valve seat 9 (the low-pressure oil passed into the valve outlet 13), the small flow valve seat 9 is also subjected to the downward pressure differential force brought about by the pressure differential. Furthermore, the small flow valve is also subjected to the upward second elastic force transmitted by the second elastic member 10. At this time, the sum of the pressure force and the pressure differential force is greater than the second elastic force. Therefore, the small flow valve seat 9 moves downward, thereby causing the second closing portion 9.2 to close the large flow port 15 of the large flow valve seat 12.

[0120] Further, at this time, the force analysis of the large flow valve seat 12 shows that the large flow valve seat 12 is subjected to the downward pushing force transmitted by the small flow valve seat 9 and the downward pushing force transmitted by the second elastic member 10, at this time, the large flow valve seat 12 moves downward under the action of the two pushing forces, until the limiting seat on the outer periphery of the large flow valve seat 12 abuts against the limiting baffle 8, the limiting baffle 8 is in interference fit with the valve housing 7, and the upper surface of the limiting baffle 8 is in contact with the sunken table surface of the valve housing 7. At this time, the large flow switching electromagnetic valve 1 is in a closed state.

[0121] In the above case, the electromagnetic force F1 generated by the magnetic field is greater than the sum of the first elastic force F2 and the second elastic force F3, that is, .

[0122] At this time, the liquid pressure P1 at the valve inlet 7.1 is greater than the liquid pressure P2 at the valve outlet 13, F4 is the differential pressure acting force on the lower end of the small flow valve seat 9, at this time, the force on the small flow valve seat 9 is , vertically downward. Since F1, F2 and F3 are fixed values, and since the small flow valve seat 9 is subjected to force only related to the sealing circle area of the large flow port 15 due to the existence of the valve through port 7.2, the greater F4 is, the greater the force on the small flow valve seat 9 is, the tighter the contact with the large flow valve seat 12 is, and the better the sealing effect is.

[0123] As shown in Figure 10 , wherein the differential pressure acting force on the small flow valve seat 9 is , wherein, the liquid pressure P1 at the valve inlet 7.1 minus the liquid pressure P2 at the valve outlet 13; , wherein S1 is the sealing circle area of the large flow port 15.

[0124] (3) As shown in Figure 8 , in the case that the electromagnetic coil 2 is energized and the valve inlet 7.1 is connected to low pressure oil and the valve outlet 13 is connected to high pressure oil: in this working condition, if the electromagnetic coil 2 is energized, the valve housing 7 generates a magnetic force, the moving iron 4 is subjected to the downward electromagnetic force exerted by the valve housing 7, and the moving iron 4 transmits the downward electromagnetic force to the valve core 5 connected thereto, at this time, the force analysis of the valve core 5 shows that the valve core 5 is subjected to the downward electromagnetic force transmitted by the valve housing 7 through the moving iron 4, and the valve core 5 is also subjected to the upward first elastic force exerted by the first elastic member 6. It can be understood that since the electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and approaches the small flow valve seat 9, thereby causing the first sealing portion to close the small flow port 14 of the small flow valve seat 9.

[0125] While delivering high-pressure oil to the valve outlet 13, the high-pressure oil will enter the oil pressure space and flow to the sealing ring 11 through the second oil-passing groove 12.2. At this time, since the low-pressure oil above the sealing ring 11 is introduced from the valve inlet 7.1, and the high-pressure oil below the sealing ring 11 is introduced from the second oil-passing groove 12.2, under the action of the pressure difference between the high-pressure oil and the low-pressure oil, the high-pressure oil will exert an upward pressure differential force on the sealing ring 11. At this time, a force analysis of the high-flow valve seat 12 shows that the high-flow valve seat 12 is subjected to an upward pressure differential force, a downward second elastic force exerted by the second elastic member 10, and a downward pressure force exerted by the small-flow valve seat 9. Since the pressure differential force is greater than the downward pressure force and the second elastic force exerted by the small-flow valve seat 9, the high-flow valve seat 12 is pushed upward, that is, toward the small-flow valve seat 9, pushing the small-flow valve seat 9 upward until the small-flow valve seat 9 abuts the valve seat limiter 7.3. At this time, the high-flow valve seat 12 and the small-flow valve seat 9 no longer move, and the high-flow port 15 remains closed. However, due to the electromagnetic force, the valve core 5 is still in contact with the small-flow valve seat 9, and the small-flow port 14 is still closed.

[0126] It can be understood that in the above situation, the electromagnetic coil 2 is energized to generate a magnetic field, and both the small-flow valve port and the large-flow valve port are closed. When the electromagnetic valve is in a completely closed and sealed state, when the pressure at the valve outlet 13 gradually rises, the force of the liquid pressure P2 at the valve outlet 13 acting on the large-flow valve seat 12 (that is, the pressure differential force F5 exerted on the large-flow valve seat 12) is greater than the friction force between the electromagnetic force and the sealing ring 11 at the large-flow valve seat 12, the large-flow valve seat 12 is lifted upward and pushes the small-flow valve seat 9 upward. When the small-flow valve seat 9 stops at the valve seat limit portion 7.3, both the small-flow valve seat 9 and the large-flow valve seat 12 stop moving.

[0127] like Figure 11 As shown, the pressure difference force on the entire large flow valve seat 12 is ,in, Liquid pressure P1 at valve outlet 13 - liquid pressure P2 at valve inlet 7.1; , where S2 is the sealing line area of ​​the sealing ring 11.

[0128] When the liquid pressure at the valve outlet 13 continues to rise, the small flow valve seat 9 and the large flow valve seat 12 are limited. The key point of the liquid pressure at this time is that the valve core 5 is still subjected to force. At this time, the valve core 5 is subjected to the electromagnetic force F1, the first elastic force F2 and the pressure difference force F6. The force formula is: At this time, F6 is related to the sealing circle area of ​​the first closing part of the valve core 5.

[0129] like Figure 12 As shown, ,in, liquid pressure P1 at the valve outlet 13 - liquid pressure P2 at the valve inlet 7.1; wherein S3 is the sealing circle area of the first closed part of the spool 5.

[0130] Since the valve port sealing line of the first closed part is small enough (usually between 0.4-0.5mm, or even smaller), the value of F6 is small, so that the spool 5 will not move upward, the small flow port 14 is still closed, and the electromagnetic valve is still in the closed sealing state.

[0131] (4) As shown in Figure 6 and 8 , when the electromagnetic coil 2 changes from being energized in case (3) to being de-energized: the electromagnetic valve coil is controlled to be de-energized, the spool 5 is lifted up by the upward elastic force of the first elastic member 6, at this time the small flow port 14 of the small flow valve seat 9 is opened. If there is liquid pressure at the valve outlet 13 at this time, the liquid flows through the large flow port 15 and the small flow port 14 in turn and enters the first space, and finally flows out to the outside of the valve shell 7 through the valve port 7.2 on the first space. It can be understood that in this process, the high pressure at the valve outlet 13 will gradually decrease, and when the pressure at the valve outlet 13 and the pressure at the valve inlet 7.1 tend to a certain difference, that is, the pressure difference is less than the elastic force exerted by the second elastic member 10, the large flow valve seat 12 moves downward under the elastic force of the second elastic member 10 until it is limited by the limiting baffle 8, at this time the large flow port 15 is opened.

[0132] Further, when the large flow switching electromagnetic valve is applied in the hydraulic control unit 16, the first space and the second space are communicated through the valve inlet 7.1 and the valve port 7.2 to achieve pressure balance.

[0133] It should be pointed out that when the large flow switching electromagnetic valve is applied in the hydraulic control unit 16, a closed space is formed outside the valve inlet 7.1 and the valve port 7.2, and the first space and the second space can be communicated through the valve inlet 7.1 and the valve port 7.2 in the closed space to achieve pressure balance.

[0134] It can be understood that when the electromagnetic coil 2 changes from being energized in case (2) to being de-energized, that is, if there is no liquid pressure at the valve outlet 13, the large flow valve seat 12 directly moves downward under the elastic force of the second elastic member 10 until it is limited by the limiting baffle 8, and the large flow port 15 is opened.

[0135] As shown in Figure 13As shown, the hydraulic control unit 16 of the automobile brake system according to the second aspect of the present application comprises the large-flow switching electromagnetic valve 1 according to the first aspect of the present application. The hydraulic control unit 16 further comprises a pressure control module 17, and the large-flow switching electromagnetic valve 1 is installed in the pressure control module 17.

[0136] Further, the large-flow switching electromagnetic valve 1 according to the present application is used together with an electromagnetic coil 2, and a power-on pin 2.1 of the electromagnetic coil 2 is connected to a controller (ECU). The ECU controls the power-on pin of the electromagnetic coil 2 to be powered on or powered off according to the state of the vehicle and the control logic burned in advance. After the pin is powered on, the coil forms a magnetic field inside due to electromagnetic induction. The moving iron 4 inside the electromagnetic valve is attracted to the valve shell 7 under the action of the magnetic field, pushes the valve core 5, compresses the first elastic member 6, and makes the valve core 5 adhere to the small-flow valve seat 9 to close the small-flow port 14. The valve core 5 is continuously pushed, the second elastic member 10 is compressed, the small-flow valve seat 9 adheres to the large-flow valve seat 12, and the large-flow port 15 is closed, so that the electromagnetic valve is completely closed and sealed.

[0137] After the electromagnetic coil 2 is powered off, the magnetic field disappears, the valve core 5 inside the electromagnetic valve moves up under the action of the first elastic member 6 and pushes the moving iron 4 to reset, and the small-flow port 14 is opened. The small-flow valve seat 9 inside is moved up to the valve seat limiting portion 7.3 under the action of the second elastic member 10, and the large-flow port 15 is opened.

[0138] In the description of the present specification, the description of the terms "one embodiment", "some embodiments", "an example", "a specific example", or "some examples" and the like means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the present specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any appropriate manner in any one or more embodiments or examples. In addition, different embodiments or examples described in the present specification and the features of different embodiments or examples can be combined and combined by those skilled in the art without contradiction.

[0139] Finally, it should be noted that: the above embodiments are only used to illustrate the technical solutions of the present application, and not to limit them; although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that: it can still modify the technical solutions recorded in the foregoing embodiments, or make equivalent replacement to part of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the embodiments of the present application.

Claims

1. A normally open large flow switching solenoid valve, characterized in that: Including electromagnetic coil, valve housing, moving iron, valve core, small flow valve seat and large flow valve seat; The interior of the valve housing is formed with an accommodating space running through its upper and lower ends. The accommodating space is sequentially provided with a valve core, a small flow valve seat, and a large flow valve seat from top to bottom. The upper end of the valve core is connected to the moving iron, and the electromagnetic coil is arranged around the moving iron and the valve housing. A first elastic member is provided between the valve core and the small flow valve seat. The small flow valve seat and the large flow valve seat are connected by a second elastic member. The small flow valve seat and the valve core are both slidably arranged along the central axis of the accommodating space. The lower end of the valve core is provided with a first closing portion for closing or opening the small flow port of the small flow valve seat, and the lower end of the small flow valve seat is provided with a second closing portion for closing or opening the large flow port of the large flow valve seat. The small flow port, the large flow port and the valve outlet formed at the lower end of the accommodating space are connected in sequence; When the electromagnetic coil is powered off, the valve core opens the small flow port, and the small flow valve seat opens the large flow port, so that the large flow switching electromagnetic valve is opened at a large flow rate; when the electromagnetic coil is powered on, the valve core closes the small flow port, and the small flow valve seat closes the large flow port, so that the large flow switching electromagnetic valve is closed; A valve seat limiting portion is further provided in the accommodating space. The valve seat limiting portion is located between the valve core and the small-flow valve seat, and the valve seat limiting portion divides the accommodating space into a first space located on its upper side and a second space located on its lower side. The first space and the second space are connected through a through hole located in the center of the valve seat limiting portion. The small flow valve seat passes through the through hole and enters the second space, and the upper surface of the valve seat limiting portion abuts against the lower end of the first elastic member, and the lower surface of the valve seat limiting portion abuts against the limiting boss of the small flow valve seat; The valve housing is provided with a valve inlet and a valve port, the valve port being connected to the first space, and the valve inlet being connected to the second space; when the high-flow switching solenoid valve is used in a hydraulic control unit, the first space and the second space are connected through the valve inlet and the valve port to achieve pressure balance; When the electromagnetic coil is powered off, the valve port is connected to the valve outlet through the first space, the small flow port and the large flow port in sequence, and the valve inlet is connected to the valve outlet through the second space and the large flow port in sequence; a sealing ring is fixedly sleeved on the outer periphery of the large flow valve seat and abuts against the inner wall of the second space.

2. The normally open large flow switching solenoid valve according to claim 1, characterized in that: The valve seat limiting portion is integrally formed with the valve housing, and the interior of the valve housing extends inwardly to form an annular valve seat limiting portion; Alternatively, the valve seat limiting portion and the valve housing are manufactured separately, wherein the valve seat limiting portion is pressed into the valve housing by interference fit.

3. The normally open large flow switching solenoid valve according to claim 2, characterized in that: The large flow valve seat and the sealing ring are both slidably arranged along the length direction of the valve housing; and an oil pressure space is defined between the outer peripheral surface of the large flow valve seat, the sealing ring and the inner wall of the accommodating space, and the oil pressure space is only connected to the valve outlet; When the electromagnetic coil is energized and high-pressure oil is passed to the valve outlet and low-pressure oil is passed to the valve inlet, the high-pressure oil enters the oil pressure space to push the large-flow valve seat to slide toward the direction close to the small-flow valve seat. At this time, the valve core closes the small-flow port, the small-flow valve seat closes the large-flow port, and the limiting boss of the small-flow valve seat contacts the valve seat limiting part.

4. The normally open large flow switching solenoid valve according to claim 3, characterized in that: A plurality of second oil-passing grooves are further formed on the outer peripheral surface of the large-flow valve seat between the sealing ring and the valve outlet. The second oil-passing grooves extend along the length direction of the valve housing and are connected to the valve outlet. An oil pressure space is defined between the second oil-passing groove, the sealing ring and the inner wall of the accommodating space.

5. The normally open large flow switching solenoid valve according to any one of claims 1 to 4, characterized in that: The first elastic member is a first spring, and the second elastic member is a second spring; When the electromagnetic coil is energized, the downward electromagnetic force is greater than the sum of the upward forces of the first and second springs. The movable iron presses the first closing portion of the valve core against the small flow valve seat, and the second closing portion of the small flow valve seat is pressed against the large flow valve seat. At this time, both the first and second springs are in a compressed state. When the electromagnetic coil is de-energized, the first spring pushes the valve core away from the small-flow valve seat by elastic force, and the second spring pushes the small-flow valve seat away from the large-flow valve seat by elastic force.

6. The normally open large flow switching solenoid valve according to any one of claims 1 to 4, characterized in that: The first closing portion is a spherical closing piece, and a small valve port sealing cone surface that cooperates with the spherical closing piece is formed at the small flow port.

7. The normally open large flow switching solenoid valve according to any one of claims 1 to 4, characterized in that: The second sealing portion is a sealing spherical arc surface formed at the bottom of the small flow valve seat, and a large valve port sealing conical surface matching the sealing arc surface is formed at the large flow port.

8. A hydraulic control unit for an automobile braking system, characterized in that: It comprises a normally open large flow switching solenoid valve according to any one of claims 1 to 7; the hydraulic control unit further comprises a pressure control module, and the large flow switching solenoid valve is installed in the pressure control module.

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