Large flow switching solenoid valve and hydraulic control unit for automotive brake system

Abstract

The application provides a large-flow switching electromagnetic valve and a hydraulic control unit of an automobile brake system. The large-flow switching electromagnetic valve comprises a valve shell, one end of which is fixed with a fixed iron, and the other end of which is formed with a valve outlet; an electromagnetic coil is arranged on the outside; a moving iron, a small-flow valve seat and a large-flow valve seat are sequentially arranged along the direction of the fixed iron towards the valve outlet, the moving iron is connected with the fixed iron through a first elastic element, the small-flow valve seat is connected with the large-flow valve seat through a second elastic element, and the small-flow valve seat and the moving iron are slidably arranged along the length direction of the valve shell; wherein the moving iron is provided with a first sealing part, the small-flow valve seat is provided with a second sealing part, a small-flow port, a large-flow port and the valve outlet are sequentially communicated; when the electromagnetic coil is powered off, the moving iron seals the small-flow port, and the small-flow valve seat seals the large-flow port; when the electromagnetic coil is powered on, the moving iron opens the small-flow port, and the small-flow valve seat opens the large-flow port. The large-flow opening of the electromagnetic valve is realized while the sealing performance of the electromagnetic valve is ensured.

Description

TECHNICAL FIELD

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

[0002] In the related art, the valve port of the large-flow switching electromagnetic valve for regulating the braking pressure of a vehicle is small (<1mm), and the oil passing capacity is limited, which is not suitable for large light commercial vehicles or off-road passenger vehicles. Simply increasing the valve port diameter further reduces the reverse sealing capacity of the large-flow switching electromagnetic valve under the existing structure. SUMMARY

[0003] The present application provides a large-flow switching electromagnetic valve and a hydraulic control unit of an automotive braking system to solve the defects in the prior art and achieve the following technical effects: the small-flow port of the small-flow valve seat and the large-flow port of the large-flow valve seat are automatically closed in the case of power-off of the electromagnetic coil, and are automatically opened in the case of power-on of the electromagnetic coil, thereby ensuring the sealing performance of the large-flow switching electromagnetic valve while realizing the large-flow opening of the large-flow switching electromagnetic valve.

[0004] According to the large-flow switching electromagnetic valve of the first aspect of the present application, comprising:

[0005] a valve shell having a fixed iron at one end and an open end forming a valve outlet; a containing space is formed in the valve shell and communicates with the valve outlet, and an electromagnetic coil is arranged on the outside of the valve shell, and the electromagnetic coil surrounds the fixed iron and the moving iron at the same time, so that the gap between the fixed iron and the moving iron is located in the middle position of the electromagnetic coil;

[0006] a moving iron, a small-flow valve seat and a large-flow valve seat are all installed in the containing space and arranged in sequence along the direction of the fixed iron towards the valve outlet, the moving iron is connected with the fixed iron through a first elastic member, the small-flow valve seat is connected with the large-flow valve seat through a second elastic member, and the small-flow valve seat and the moving iron are slidably arranged along the length direction of the valve shell;

[0007] wherein the end of the moving iron is provided with a first closing part for closing or opening the small-flow port of the small-flow valve seat, the end of the small-flow valve seat is provided with a second closing part for closing or opening the large-flow port of the large-flow valve seat, and the small-flow port, the large-flow port and the valve outlet are sequentially communicated;

[0008] In the case that the electromagnetic coil is powered off, the moving iron 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; in the case that the electromagnetic coil is powered on, the moving iron 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 in large flow.

[0009] According to an embodiment of the present application, the large flow switching electromagnetic valve further comprises:

[0010] A valve seat limiting ring is fixed in the accommodating space and located between the moving iron and the small flow valve seat, and a through hole is formed in the center of the valve seat limiting ring for the first closing part to pass through;

[0011] The valve seat limiting ring is used to limit the position of the small flow valve seat from exceeding the lower surface of the valve seat limiting ring.

[0012] According to an embodiment of the present application, the outer periphery of the valve seat limiting ring is fixed on the inner wall of the accommodating space, and a plurality of first oil passing grooves are further arranged between the outer periphery of the valve seat limiting ring and the inner wall of the accommodating space.

[0013] According to an embodiment of the present application, a valve inlet is arranged on the side wall of the valve shell, the valve inlet is communicated to the accommodating space, and in the case that the electromagnetic coil is powered on, the valve inlet is communicated to the valve outlet through the small flow port and the large flow port in sequence;

[0014] A sealing ring is fixedly sleeved on the outer periphery of the large flow valve seat and abuts against the inner wall of the accommodating space.

[0015] According to an 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 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 communicated to the valve outlet;

[0016] In the case that the electromagnetic coil is powered off and high pressure oil is input to the valve outlet and low pressure oil is input to the valve inlet, the high pressure oil enters the oil pressure space to push the large flow valve seat to slide towards the direction close to the small flow valve seat, at this time, the moving iron closes the small flow port, the small flow valve seat closes the large flow port, and one end of the small flow valve seat abuts against the valve seat limiting ring.

[0017] According to an embodiment of the present application, 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 shell and are communicated to the valve outlet;

[0018] The second oil passage, the sealing ring and the inner wall of the containing space define the oil pressure space.

[0019] 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.

[0020] In the case that the electromagnetic coil is powered off, the first spring presses the first closing part on the small flow valve seat by elastic force, and at this time the second spring is in a compressed state; in the case that the electromagnetic coil is powered on, the second spring pushes the small flow valve seat away from the large flow valve seat by elastic force, and at this time the first spring is in a compressed state.

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

[0022] According to one embodiment of the present application, the second closing part is a sealing 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 and cooperates 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 large flow switching electromagnetic valve according to the first aspect of the present application, and further comprises a pressure control module, wherein the large flow switching electromagnetic valve is installed in the pressure control module.

[0024] The present application provides a large flow switching electromagnetic valve with large flow, which automatically closes the small flow port of the small flow valve seat and the large flow port of the large flow valve seat in the case that the electromagnetic coil is powered off, and automatically opens the small flow port of the small flow valve seat and the large flow port of the large flow valve seat in the case that the electromagnetic coil is powered on, based on the mechanical action of the first elastic member, the second elastic member and the fixed iron, so as to ensure the sealing performance of the large flow switching electromagnetic valve and realize the large flow opening of the large flow switching electromagnetic valve.

[0025] Further, the large flow switching electromagnetic valve according to the present application can be used in the brake pressure control module of the automobile brake system, and can meet the valve port sealing of the oil inlet and outlet of the large flow switching electromagnetic valve under different working conditions with positive pressure difference or negative pressure difference, and realize the bidirectional sealing of pressure control. Meanwhile, when the valve is opened under the electromagnetic force, the valve also has a large flow capacity, can pass a large amount of brake fluid in a short time, and shorten the time for the wheel cylinder of the vehicle to reach the required pressure, so as to realize the rapid regulation and control of pressure. BRIEF DESCRIPTION OF DRAWINGS

[0026] 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.

[0027] Figure 1 is a structural schematic view of a large-flow switching electromagnetic valve provided by the present application.

[0028] Figure 2 is a structural schematic view of a large-flow switching electromagnetic valve provided by the present application.

[0029] Figure 3 is a structural schematic view of a small-flow valve seat provided by the present application.

[0030] Figure 4 is a structural schematic view of a large-flow valve seat provided by the present application.

[0031] Figure 5 is a structural schematic view of a valve seat limiting ring provided by the present application.

[0032] Figure 6 is a schematic view of a large-flow switching electromagnetic valve in a powered condition provided by the present application.

[0033] Figure 7 is a schematic view of a large-flow switching electromagnetic valve in a powered condition provided by the present application.

[0034] Figure 8 is a schematic view of a large-flow switching electromagnetic valve in a powered condition provided by the present application.

[0035] Figure 9 is a structural schematic view of a hydraulic control unit of an automobile braking system provided by the present application.

[0036] Reference signs:

[0037] 1, large-flow switching electromagnetic valve; 2, electromagnetic coil; 2.1, powered pin; 3, fixed iron; 4, first spring; 5, magnetic isolation tube; 6, moving iron; 6.1, first closed part; 7, valve base; 8, valve seat limiting ring; 8.1, first oil passing groove; 9, small-flow valve seat; 9.1, small valve port sealing cone surface; 9.2, second closed part; 10, second spring; 11, sealing ring; 12, large-flow valve seat; 12.1, large valve port sealing cone surface; 12.2, second oil passing groove; 12.3, limiting seat; 13, valve outlet; 14, small-flow port; 15, large-flow port; 16, hydraulic control unit; 17, pressure control module. DETAILED DESCRIPTION

[0038] 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 with reference to the drawings in the present application. Obviously, the described embodiments are only part of, rather than all of, the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative effort belong to the protection scope of the present application.

[0039] A large-flow switching electromagnetic valve and a hydraulic control unit of an automobile braking system are provided according to the present application.

[0040] As shown in the drawings, the large-flow switching electromagnetic valve 1 according to the first embodiment of the present application comprises a valve shell, a fixed iron 3, a moving iron 6, an electromagnetic coil 2, a small-flow valve seat 9 and a large-flow valve seat 12. Figures 1 to 9

[0041] One end of the valve shell is fixed with the fixed iron 3, and the other end of the valve shell is open to form a valve outlet 13. An accommodating space is formed in the valve shell and communicates with the valve outlet 13. The electromagnetic coil 2 is arranged on the outer side of the valve shell and surrounds the fixed iron 3 and the moving iron 6 at the same time, so that the gap between the fixed iron 3 and the moving iron 6 is located in the middle position of the electromagnetic coil 2.

[0042] The moving iron 6, the small-flow valve seat 9 and the large-flow valve seat 12 are all arranged in the accommodating space, and are arranged in sequence in the direction along the fixed iron 3 towards the valve outlet 13. The moving iron 6 is connected with the fixed iron 3 through the first elastic member 4. The small-flow valve seat 9 is connected with the large-flow valve seat 12 through the second elastic member 10. The small-flow valve seat 9 and the moving iron 6 are both arranged slidably along the length direction of the valve shell.

[0043] The end of the moving iron 6 is provided with a first closing part 6.1 for closing or opening a small-flow port 14 of the small-flow valve seat 9. The 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. The small-flow port 14, the large-flow port 15 and the valve outlet 13 are communicated in sequence.

[0044] As shown in the drawings, in the case that the electromagnetic coil 2 is powered off, the moving iron 6 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. Figure 7 8 As shown in the drawings, in the case that the electromagnetic coil 2 is powered on, the moving iron 6 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. Figure 6

[0045] ​​​According to the embodiment of the present invention, the large flow switching solenoid valve 1 can ensure the sealing ability of the large flow switching solenoid valve 1 while realizing the large flow switching solenoid valve 1 to be opened at a large flow rate, thereby having a larger flow capacity, and being able to pass more brake fluid in a short time, shortening the time for the vehicle wheel cylinder to reach the required pressure, thereby realizing rapid pressure regulation.

[0046] Specifically, the working principle and working process of the large flow switching solenoid valve 1 to achieve large flow opening while ensuring sealing are as follows:

[0047] like Figure 7 and 8 As shown, when the electromagnetic coil 2 is powered off, the fixed iron 3 has no magnetic force. Under the push of the first elastic member 4, the first closing portion 6.1 located at the lower end of the moving iron 6 abuts against the small flow port 14 of the small flow valve seat 9, thereby closing the small flow port 14; at the same time, the first elastic member 4 overcomes the elastic force of the second elastic member 10, so that the second closing portion 9.2 located at the lower end of the small flow valve seat 9 abuts against the large flow port 15 of the large flow valve seat 12, thereby closing the large flow port 15. At this time, the large flow switching solenoid valve 1 is in a closed state.

[0048] like Figure 6 As shown, when the electromagnetic coil 2 is energized instead of de-energized, the fixed iron 3 generates magnetic force, and the moving iron 6 is acted upon by the magnetic force of the fixed iron 3, overcomes the elastic force of the first elastic member 4 and moves upward. At this time, the first closing portion 6.1 located at the lower end of the moving iron 6 gradually moves away from the small flow port 14 of the small flow valve seat 9, thereby opening the small flow port 14; at the same time, under the elastic force of the second elastic member 10, the second closing portion 9.2 located at the lower end of the small flow valve seat 9 also gradually moves away from the large flow port 15, thereby opening the large flow port 15. At this time, the large flow switching solenoid valve 1 is opened to the outside of the valve outlet 13 through the large flow port 15, that is, the large flow switching solenoid valve 1 is opened with a large flow.

[0049] Existing high-flow switching solenoid valves used for vehicle brake pressure control have small orifices (less than 1mm) and limited oil flow capacity, making them unsuitable for light commercial vehicles or off-road passenger vehicles with larger wheel cylinders. Simply increasing the orifice diameter further reduces the reverse sealing capability of existing high-flow switching solenoid valves.

[0050] Therefore, in order to solve the technical defects existing in the above-mentioned related art, the present application provides a large-flow switching electromagnetic valve, by controlling whether the electromagnetic coil 2 is energized or not, and based on the mechanical action generated by the first elastic member 4, the second elastic member 10 and the fixed iron 3, the small-flow port 14 of the small-flow valve seat 9 and the large-flow port 15 of the large-flow valve seat 12 are automatically closed in the case of de-energization of the electromagnetic coil 2, and are automatically opened in the case of energization of the electromagnetic coil 2, so as to ensure the sealing performance of the large-flow switching electromagnetic valve 1 while realizing the large-flow opening of the large-flow switching electromagnetic valve 1.

[0051] As shown in Figure 2 According to some embodiments of the present application, the large-flow switching electromagnetic valve 1 further comprises a valve seat limiting ring 8, which is fixed in the accommodation space and located between the moving iron 6 and the small-flow valve seat 9, and a through hole is formed at the center of the valve seat limiting ring 8 for the first closed part 6.1 to pass through. The valve seat limiting ring 8 is used to limit the position of the small-flow valve seat 9 not to exceed the lower surface of the valve seat limiting ring 8.

[0052] It can be understood that the purpose of the valve seat limiting ring 8 is to limit the position of the small-flow valve seat 9, so as to avoid the small-flow valve seat 9 from exceeding the lower surface of the valve seat limiting ring 8 during movement.

[0053] Specifically, in the case of the electromagnetic coil 2 changing from de-energization to energization, 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 ring 8, at this time, the valve seat limiting ring 8 can avoid the small-flow valve seat 9 from being closed again due to excessive movement, that is, avoid the small-flow valve seat 9 from cooperating with the first closed part 6.1 under the pushing force to mistakenly close the small-flow port 14.

[0054] As shown in Figure 2 and Figure 5 In one specific embodiment of the present application, the outer periphery of the valve seat limiting ring 8 is fixed on the inner wall of the accommodation space, and a plurality of first oil passing grooves 8.1 are further arranged between the outer periphery of the valve seat limiting ring 8 and the inner wall of the accommodation space. For example, the outer periphery of the valve seat limiting ring 8 forms a plurality of first oil passing grooves 8.1 which are spaced and uniformly arranged.

[0055] 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. However, the existing large flow switching electromagnetic valves cannot form a seal under different working conditions with a bidirectional pressure difference, that is, the existing large flow switching electromagnetic valves for vehicle brake pressure regulation only have a one-way sealing function. 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, and has no sealing function. Based on the above-mentioned 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 the pipeline structure and control logic, and increasing the material cost and control cost.

[0056] Therefore, in order to solve the technical defects existing in the above-mentioned related art, as shown in Figure 2 According to some embodiments of the present application, a sealing ring 11 is fixedly sleeved on the outer periphery of the large flow valve seat 12 and abuts against the inner wall of the accommodating space. 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.

[0057] Further, the large flow valve seat 12 and the sealing ring 11 are slidably arranged along the length direction of the valve shell; and the outer peripheral surface of the large flow valve seat 12, the sealing ring 11 and the inner wall of the accommodating space define an oil pressure space, which is only communicated with the valve outlet 13.

[0058] In the case that the electromagnetic coil 2 is de-energized and high-pressure oil is delivered to the valve outlet 13, 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 until the one end surface of the small flow valve seat 9 abuts against the valve seat limiting ring 8. At this time, the moving iron 6 closes the small flow port 14, and the small flow valve seat 9 closes the large flow port 15.

[0059] In this way, based on the above-mentioned 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 a positive pressure difference or a negative pressure difference, and realize bidirectional sealing of pressure control.

[0060] For example Figure 4 As shown in the figure, 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 shell 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 accommodating space define an oil pressure space.

[0061] Furthermore, a limit seat 12.3 is formed on the outer circumference of the large flow valve seat 12. An annular sealing installation groove is formed on the outer circumference of the limit seat 12.3. A sealing ring 11 is fixed in the sealing installation groove.

[0062] It can be understood that when high-pressure oil is delivered to the valve outlet 13, most of the high-pressure oil will enter the large-flow port 15, and another 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 groove 12.2. At this time, the high-pressure oil will exert a pressure differential force on the sealing ring 11, thereby pushing the large-flow valve seat 12 to move upward, that is, toward the small-flow valve seat 9.

[0063] The specific working principle and working process of the high-flow switching solenoid valve of the present invention with a bidirectional sealing function are detailed below. The concept of the bidirectional sealing function of the high-flow switching solenoid valve of the present invention is explained as follows: the high-flow switching solenoid valve 1 can achieve sealing when high-pressure oil is introduced into the valve inlet and low-pressure oil is introduced into the valve outlet 13. The high-flow switching solenoid valve 1 can also achieve sealing when low-pressure oil is introduced into the valve inlet and high-pressure oil is introduced into the valve outlet 13. The working principle and working process of the high-flow switching solenoid valve 1 under different operating conditions are described below.

[0064] (i) High-pressure oil is supplied to the valve inlet and low-pressure oil is supplied to the valve outlet 13.

[0065] like Figure 7 As shown, under this working condition, if the electromagnetic coil 2 is de-energized and the fixed iron 3 has no magnetic force, a force analysis of the small flow valve seat 9 at this time shows that the small flow valve seat 9 is subjected to a first downward elastic force transmitted by the first elastic member 4 through the moving iron 6, 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) 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 will also be subjected to a downward pressure differential force brought about by the pressure differential. Furthermore, the small flow valve seat 9 will also be subjected to an upward second elastic force transmitted by the second elastic member 10. At this time, the sum of the first elastic force and the pressure differential force is greater than the second elastic force, so the small flow valve seat 9 moves downward.

[0066] At this point, force analysis of the high-flow valve seat 12 reveals that the high-flow valve seat 12 is subject to the downward force transmitted by the low-flow valve seat 9 and the downward force transmitted by the second elastic member 10. Under the action of these two forces, the high-flow valve seat 12 moves downward until the stop seat 12.3 on the outer periphery of the high-flow valve seat 12 abuts against the inner wall of the valve outlet 13. At this point, the high-flow switching solenoid valve 1 is in the closed state.

[0067] (ii) Low-pressure oil is introduced into the valve inlet and high-pressure oil is introduced into the valve outlet 13 .

[0068] As shown in Figure 8 the case, if the electromagnetic coil 2 is powered off, the fixed iron 3 has no magnetic force, at the same time of delivering high-pressure oil 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 groove 12.2, at this time, since the low-pressure oil from the valve inlet is located above the sealing ring 11, and the high-pressure oil from the second oil passing groove 12.2 is located below the sealing ring 11, under the pressure difference between the high-pressure oil and the low-pressure oil, the high-pressure oil will exert 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, and is also subjected to a downward second elastic force exerted by the second elastic member 10 and a downward first elastic force exerted by the first elastic member 4 (for example, a second spring), since the pressure difference force is greater than the first elastic force and the second elastic force, the large flow valve seat 12 is pushed to move upward, that is, in the direction of the small flow valve seat 9, thereby making the second closed part 9.2 located at the lower end of the small flow valve seat 9 close the large flow port 15.

[0069] At this time, the force analysis of the small flow valve seat 9 shows that the small flow valve seat 9 is subjected to a downward first elastic force transmitted by the moving iron 6 through the first elastic member 4, and is also subjected to an upward pressure difference force caused by the pressure difference between the low-pressure oil in the containing space above the small flow valve seat 9 (the low-pressure oil introduced into the valve inlet) and the high-pressure oil in the large flow port 15 below the small flow valve seat 9 (the high-pressure oil introduced into the valve outlet 13), further, the small flow valve seat 9 is also subjected to an upward second elastic force transmitted by the second elastic member 10, at this time, the sum of the second elastic force and the pressure difference force is greater than the first elastic force, so the small flow valve seat 9 moves upward, thereby making the first closed part 6.1 located at the lower end of the moving iron 6 close the small flow port 14.

[0070] In summary, based on the above structure, the large flow switching electromagnetic valve 1 of the present application can realize the bidirectional sealing function.

[0071] As shown in Figure 2 According to some embodiments of the present application, the first elastic member 4 is a first spring, and the second elastic member 10 is a second spring.

[0072] As shown in Figure 7 and 8 In the case that the electromagnetic coil 2 is powered off, the first spring presses the first closed part 6.1 tightly on the small flow valve seat 9 through the elastic force, and at this time, the second spring is in a compressed state. In this way, the sealing of the first closed part 6.1 to the small flow port 14 and the sealing of the second closed part 9.2 to the large flow port 15 can be ensured.

[0073] AsFigure 6 As shown, in the case of energizing the electromagnetic coil 2, the second spring pushes the small flow valve seat 9 away from the large flow valve seat 12 by elastic force, at this time the first spring is in compression. In this way, it can be guaranteed that the first closure 6.1 is away from the small flow port 14 to open the small flow port 14, and the second closure 9.2 is away from the large flow valve seat 12 to open the large flow port 15.

[0074] As shown in FIG. 1, the first closure 6.1 is a ball-shaped closure, and the small flow port 14 is formed with a small valve port sealing taper surface 9.1 matched with the ball-shaped closure. Figure 2 Figure 3 As shown in FIG. 1, the second closure 9.2 is a sealing arc surface formed at the bottom of the small flow valve seat 9, and the large flow port 15 is formed with a large valve port sealing taper surface 12.1 matched with the sealing arc surface.

[0075] As shown in FIG. 1, the first closure 6.1 is a ball-shaped closure, and the small flow port 14 is formed with a small valve port sealing taper surface 9.1 matched with the ball-shaped closure. Figure 3 Figure 4 As shown in FIG. 1, the second closure 9.2 is a sealing arc surface formed at the bottom of the small flow valve seat 9, and the large flow port 15 is formed with a large valve port sealing taper surface 12.1 matched with the sealing arc surface.

[0076] In this way, the above design enables the large flow switching electromagnetic valve 1 to maintain good sealing performance even under high flow demand. When the electromagnetic coil 2 is de-energized, the sealing arc surface of the second closure 9.2 will be pressed against the large valve port sealing taper surface 12.1, and the geometric cooperation 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.

[0077] When the electromagnetic coil is energized to open the large flow switching electromagnetic valve, the surface of the ball-shaped closure and the small valve port sealing taper surface 9.1 will separate, and the sealing arc surface and the large valve port sealing taper surface 12.1 will separate, 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.

[0078] It should be noted that the above embodiments of the first closure 6.1 and the second closure 9.2 are only exemplary and do not constitute a specific limitation on the structure of the first closure 6.1 and the second closure 9.2. The first closure 6.1 and the second closure 9.2 of the present application can also adopt other sealing structures, and the present application does not make special limitations here, as long as the first closure 6.1 and the second closure 9.2 can respectively realize the sealing of the small flow port 14 and the large flow port 15.

[0079] ​​A specific embodiment of the large flow switching solenoid valve 1 of the present invention is given below with reference to the accompanying drawings.

[0080] like Figures 1 to 8 As shown, the large flow switching solenoid valve 1 includes a valve housing, a fixed iron 3, a moving iron 6, an electromagnetic coil 2, a small flow valve seat 9, a large flow valve seat 12, a valve seat limiting ring 8, a sealing ring 11, a first spring and a second spring.

[0081] The valve housing comprises a magnetic isolation tube 5 and a valve seat 7. These two elements are fixed and interference-fitted. An electromagnetic coil 2 surrounds the outer surface of the magnetic isolation tube 5. A fixed iron 3 is fixed to the upper end of the tube 5. Inside the tube 5, a movable iron 6 is positioned, sliding along the length of the tube 5. The lower end of the fixed iron 3 is connected to the upper end of the movable iron 6 via a first spring. A valve inlet is defined on the sidewall of the valve seat 7, and its lower end is open to form a valve outlet 13. Inside the valve seat 7, from top to bottom, are a valve seat retaining ring 8, a low-flow valve seat 9, and a high-flow valve seat 12. The outer periphery of the valve seat retaining ring 8 is fixed to the inner wall of the valve seat 7, and several first oil-passing grooves 8.1 are defined between the outer periphery of the valve seat retaining ring 8 and the inner wall of the valve seat 7. The low-flow valve seat 9 and the high-flow valve seat 12 are connected via a second spring. Both the low-flow valve seat 9 and the high-flow valve seat 12 are slidable along the length of the valve seat 7.

[0082] A first sealing portion 6.1 is fixed to the lower end of the movable iron 6. This first sealing portion 6.1 is a spherical sealing member. A through hole for the entry and exit of the first sealing portion 6.1 is formed at the center of the valve seat retaining ring 8. A small flow port 14 is formed at the upper end of the small flow valve seat 9. This small flow port 14 has a small valve port sealing cone 9.1 that cooperates with the spherical sealing member. A second sealing portion 9.2 is formed at the lower end of the small flow valve seat 9. This second sealing portion 9.2 is a sealing arc surface. A large flow port 15 is formed at the upper end of the large flow valve seat 12. This large flow port 15 has a large valve port sealing cone 12.1 that cooperates with the sealing arc surface. The large flow port 15 is connected to the valve outlet 13.

[0083] A limit seat 12.3 is also formed on the outer circumference of the large-flow valve seat 12. From top to bottom, a sealing installation groove and a second oil-passing groove 12.2 are sequentially formed on the outer circumference of the limit seat 12.3. A sealing ring 11 is fixed in the sealing installation groove, and the sealing ring 11 is in close contact with the inner wall of the valve base 7. There are multiple second oil-passing grooves 12.2, and the multiple second oil-passing grooves 12.2 are spaced and evenly distributed along the outer circumference of the limit seat 12.3.

[0084] An oil pressure space is defined between the second oil flow groove 12.2, the sealing ring 11 and the inner wall of the valve base 7, and an oil flow gap communicating with the oil pressure space is left between the outer peripheral surface of the lower end of the large flow valve seat 12 and the valve outlet 13.

[0085] The specific working principle of the large flow switching solenoid valve 1 of the present invention is described below based on the above specific embodiments.

[0086] (1) When the electromagnetic coil 2 is powered off and no oil flows into the valve inlet and valve outlet 13: the fixed iron 3 has no magnetic force, and under the push of the first spring, the first closing portion 6.1 at the lower end of the moving iron 6 abuts against the small flow port 14 of the small flow valve seat 9, thereby closing the small flow port 14; at the same time, the first spring overcomes the elastic force of the second spring, so that the second closing portion 9.2 at the lower end of the small flow valve seat 9 abuts against the large flow port 15 of the large flow valve seat 12, thereby closing the large flow port 15. At this time, the large flow switching electromagnetic valve 1 is in a closed state.

[0087] (2) If Figure 7 As shown, when the electromagnetic coil 2 is de-energized and high-pressure oil is passed into the valve inlet and low-pressure oil is passed into the valve outlet 13: under this working condition, if the electromagnetic coil 2 is de-energized, the fixed iron 3 has no magnetic force. At this time, a force analysis of the small-flow valve seat 9 shows that the small-flow valve seat 9 is subjected to a first downward elastic force transmitted by the first spring through the moving iron 6, 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) 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 a downward pressure differential force brought about by the pressure differential. Furthermore, the small-flow valve seat 9 is also subjected to an upward second elastic force transmitted by the second spring. At this time, the sum of the first elastic force and the pressure differential force is greater than the second elastic force, so the small-flow valve seat 9 moves downward.

[0088] At this point, force analysis of the high-flow valve seat 12 reveals that the high-flow valve seat 12 is subject to both the downward push from the low-flow valve seat 9 and the downward elastic force from the second spring. Under the action of these two downward forces, the high-flow valve seat 12 moves downward until the stopper 12.3 on the outer periphery of the high-flow valve seat 12 abuts against the inner wall of the valve outlet 13. At this point, the high-flow switching solenoid valve 1 is in the closed state.

[0089] For example, when the electromagnetic coil 2 is powered off, the liquid pressure P1 at the valve inlet is greater than or equal to the liquid pressure P2 at the valve outlet 13, the large-flow switching electromagnetic valve 1 is closed, and the valve inlet and the valve outlet are blocked; at this time, the pressure of the return spring (that is, the first spring) of the moving iron 6 is greater than the pressure of the second spring.

[0090] The movable iron 6 is pressed down by the pressure of the first spring and the pressure differential force formed by the pressure difference between the two oil ports, forming a seal. Because the pressure of the first spring is greater than the pressure of the second spring, the small flow valve seat 9 moves downward under the downward pressure of the movable iron 6, compressing the second spring and closing the large flow port 15. Note: The pressure differential force on the movable iron 6 is ,in, Liquid pressure P1 at the valve inlet - liquid pressure P2 at the valve outlet 13; , where S1 is the sealing line area of ​​the small flow port 14.

[0091] When the electromagnetic coil 2 is energized, the moving iron 6 is subjected to an upward electromagnetic force. At this time, the electromagnetic force is greater than the first elastic force and the pressure difference force. The moving iron 6 moves upward, the small flow port 14 opens, △P becomes smaller and smaller, and the small flow valve seat 9 moves upward under the elastic force of the second spring, and the large flow port 15 opens, reaching the maximum flow of the large flow switching solenoid valve 1.

[0092] (3) If Figure 8 As shown, when the electromagnetic coil 2 is powered off and low-pressure oil is passed into the valve inlet and high-pressure oil is passed into the valve outlet 13: under this working condition, if the electromagnetic coil 2 is powered off and the fixed iron 3 has no magnetic force, then while delivering high-pressure oil to the valve outlet 13, most of the high-pressure oil will enter the large flow port 15, and another 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 groove 12.2. At this time, since the low-pressure oil passed from the valve inlet is located above the sealing ring 11, and the high-pressure oil passed from the second oil-passing groove 12.2 is located below the sealing ring 11, 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 difference force on the sealing ring 11. At this time, a force analysis of the large flow valve seat 12 shows that the large flow valve seat 12 is subjected to an upward pressure differential force and a second downward elastic force applied by the second spring. Since the pressure differential force is greater than the second elastic force, the large flow valve seat 12 is pushed upward, that is, toward the direction of the small flow valve seat 9, thereby causing the second closing portion 9.2 located at the lower end of the small flow valve seat 9 to close the large flow port 15.

[0093] At this time, a force analysis of the small flow valve seat 9 shows that the small flow valve seat 9 is subjected to a first downward elastic force transmitted by the first spring through the moving iron 6, and due to the pressure difference between the low-pressure oil in the accommodating space above the small flow valve seat 9 (the low-pressure oil passed into the valve inlet) and the high-pressure oil in the large flow port 15 below the small flow valve seat 9 (the high-pressure oil passed into the valve outlet 13), the small flow valve seat 9 is also subjected to an upward pressure differential force brought about by the pressure differential. Furthermore, the small flow valve seat 9 is also subjected to an upward second elastic force transmitted by the second spring. At this time, the sum of the second elastic force and the pressure differential force is greater than the first elastic force, so the small flow valve seat 9 moves upward, thereby causing the first closing portion 6.1 located at the lower end of the moving iron 6 to close the small flow port 14.

[0094] For example, when the electromagnetic coil 2 is powered off, the liquid pressure P1 at the valve inlet is less than the liquid pressure P2 at the valve outlet 13, the large flow switching electromagnetic valve 1 is closed, and the valve inlet and valve outlet 13 are blocked. At this time, the pressure differential force on the movable iron 6 is less than the first elastic force of the first spring, and the movable iron 6 moves downward to close the small flow port 14. ,in, Liquid pressure P1 at valve outlet 13 - liquid pressure P2 at valve inlet; , where S1 is the sealing line area of ​​the small flow port 14.

[0095] The pressure differential force on the large flow valve seat 12 is greater than the second elastic force of the second spring. The large valve seat moves upward and presses the upper surface of the small flow valve seat 9 against the lower surface of the valve seat limit ring 8. At this time, the large flow port 15 is closed. ,in, Liquid pressure P1 at valve outlet 13 - liquid pressure P2 at valve inlet; , where S2 is the sealing line area of ​​the sealing ring 11.

[0096] When electromagnetic coil 2 is energized, movable iron 6 is subjected to the upward electromagnetic force and the upward pressure differential force generated between the high-pressure oil below and the low-pressure oil above. The upward electromagnetic force plus the upward pressure differential force is greater than the downward first elastic force. At this time, movable iron 6 moves upward, small flow port 14 opens, and ΔP decreases. Under the second elastic force, large flow valve seat 12 moves downward, opening large flow port 15, achieving the maximum flow rate of large flow switching solenoid valve 1.

[0097] (4) If Figure 6 As shown, when the electromagnetic coil 2 is energized from being de-energized: the fixed iron 3 generates magnetic force, and the moving iron 6 is acted upon by the magnetic force of the fixed iron 3, overcomes the elastic force of the first spring and moves upward. At this time, the first closing portion 6.1 located at the lower end of the moving iron 6 gradually moves away from the small flow port 14 of the small flow valve seat 9, thereby opening the small flow port 14; at the same time, under the elastic force of the second spring, the second closing portion 9.2 located at the lower end of the small flow valve seat 9 also gradually moves away from the large flow port 15, thereby opening the large flow port 15. At this time, the large flow switching solenoid valve 1 is opened to the outside of the valve outlet 13 through the large flow port 15, that is, the large flow switching solenoid valve 1 is opened with a large flow.

[0098] For example, when electromagnetic coil 2 is energized, movable iron 6 is attracted to fixed iron 3 by electromagnetic force, small flow port 14 opens, the liquid pressure P1 at the valve inlet and the liquid pressure P2 at the valve outlet 13 become equal, and then large flow port 15 opens. The large flow switching solenoid valve 1 is in the fully open state, and the oil flow rate is maximum.

[0099] As Figures 1 to 9 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 as described in the first aspect of the present application, and further comprises a pressure control module 17, wherein the large-flow switching electromagnetic valve 1 is installed in the pressure control module 17.

[0100] According to some embodiments of the present application, in the automobile brake system, the large-flow switching electromagnetic valve 1 is used in cooperation with the electromagnetic coil 2, the energized pin 2.1 of the electromagnetic coil 2 is connected to the controller (ECU), and the ECU controls the pin to be energized or de-energized according to the vehicle state and the pre-burned control logic. After the pin is energized, the coil forms a magnetic field inside due to electromagnetic induction, the moving iron 6 inside the large-flow switching electromagnetic valve 1 is attracted to the fixed iron 3 under the action of the magnetic field, so as to make the valve outlet 13 and the valve inlet communicate to open the large-flow switching electromagnetic valve 1. After the electromagnetic coil 2 is de-energized, the magnetic field disappears, and the moving iron 6 inside the large-flow switching electromagnetic valve 1 is pressed and closed under the action of the moving iron 6 reset spring, so as to close the large-flow port 15 and the small-flow port 14 and form a seal, thereby closing the large-flow switching electromagnetic valve 1.

[0101] In summary, the present application provides a new large-flow switching electromagnetic valve 1 for the brake pressure control module of the automobile brake system, which can meet the sealing of the inlet and outlet ports 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. At the same time, when the valve is opened under the action of electromagnetic force, it also has a large flow capacity, can pass a large amount of brake fluid in a short time, and shorten the time for the vehicle wheel cylinder to reach the required pressure, thereby realizing rapid pressure regulation and control.

[0102] 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 for 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 large flow switching solenoid valve, characterized in that: include: A valve housing, one end of which is fixed with a fixed iron, and the other end is open to form a valve outlet; a receiving space connected to the valve outlet is formed in the valve housing, and an electromagnetic coil is also provided on the outside of the valve housing, and the electromagnetic coil surrounds the fixed iron and the movable iron at the same time, so that the gap between the fixed iron and the movable iron is located in the middle position of the electromagnetic coil; The movable iron, the small flow valve seat and the large flow valve seat are all installed in the accommodating space and are arranged in sequence along the direction of the fixed iron toward the valve outlet. The movable iron is connected to the fixed iron by a first elastic member, and the small flow valve seat is connected to the large flow valve seat by a second elastic member. The small flow valve seat and the movable iron are both slidably arranged along the length direction of the valve housing. The end of the moving iron is provided with a first closing portion for closing or opening the small flow port of the small flow valve seat, and the 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, and the small flow port, the large flow port and the valve outlet are connected in sequence; When the electromagnetic coil is powered off, the moving iron 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; when the electromagnetic coil is powered on, the moving iron 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 with a large flow rate; a valve seat limiting ring fixed in the accommodating space and located between the moving iron and the low-flow valve seat, with a through hole for the first closing portion to enter and exit formed at the center of the valve seat limiting ring; the valve seat limiting ring is used to limit the position of the low-flow valve seat to not exceed the lower surface of the valve seat limiting ring; The outer periphery of the valve seat limiting ring is fixed on the inner wall of the accommodating space, and a plurality of first oil-passing grooves are provided between the outer periphery of the valve seat limiting ring and the inner wall of the accommodating space; A valve inlet is provided on the side wall of the valve housing, the valve inlet is connected to the accommodating space, and when the electromagnetic coil is energized, the valve inlet is connected to the valve outlet via the small flow port 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 accommodating space; 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 communicated only with the valve outlet; When the electromagnetic coil is powered off 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 moving iron closes the small-flow port, the small-flow valve seat closes the large-flow port, and one end of the small-flow valve seat abuts against the valve seat limit ring.

2. The large flow switching solenoid valve according to claim 1, 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, and the second oil-passing grooves extend along the length direction of the valve housing and communicate with the valve outlet; The oil pressure space is defined between the second oil-passing groove, the sealing ring and the inner wall of the accommodating space.

3. The large flow switching solenoid valve according to claim 1 or 2, 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 powered off, the first spring presses the first closing portion against the small-flow valve seat through elastic force, and the second spring is in a compressed state at this time; when the electromagnetic coil is powered on, the second spring pushes the small-flow valve seat away from the large-flow valve seat through elastic force, and the first spring is in a compressed state at this time.

4. The large flow switching solenoid valve according to claim 1 or 2, characterized in that: The first closing portion is a spherical closing member, and a small valve port sealing cone surface that cooperates with the spherical closing member is formed at the small flow port.

5. The large flow switching solenoid valve according to claim 1 or 2, characterized in that: The second sealing portion is a sealing arc surface formed at the bottom of the small flow valve seat, and a large valve port sealing cone surface matching the sealing arc surface is formed at the large flow port.

6. A hydraulic control unit for an automobile braking system, characterized in that: It comprises the large flow switching solenoid valve according to any one of claims 1 to 5; 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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