Large-flow switching electromagnetic valve and hydraulic control unit of automobile braking system

Abstract

The invention provides a high-flow switching electromagnetic valve and a hydraulic control unit of an automobile braking system. The large-flow switching electromagnetic valve comprises a valve shell, a valve rod, a valve rod and a valve rod, an electromagnetic coil is arranged outside; the movable iron, the small-flow valve seat and the large-flow valve seat are sequentially arranged in the direction from the fixed iron to the valve outlet, the movable iron is connected with the fixed iron through a first elastic piece, the small-flow valve seat is connected with the large-flow valve seat through a second elastic piece, and the small-flow valve seat and the movable iron are arranged in a sliding mode in 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, and the small-flow port, the large-flow port and the valve outlet are communicated in sequence; 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 opening, and the small-flow valve seat opens the large-flow opening. While the sealing performance of the electromagnetic valve is guaranteed, large-flow opening of the electromagnetic valve is achieved.

Description

Technical Field

[0001] The invention relates to the technical field of automobiles, and in particular to a large-flow switching solenoid valve and a hydraulic control unit of an automobile braking system. Background Art

[0002] In the related art, the existing large flow switching solenoid valve for vehicle brake pressure control has a small valve port (<1mm) and limited oil flow capacity, which is not suitable for light commercial vehicles or off-road passenger vehicles with large wheel cylinders. Simply increasing the valve port diameter will further reduce the reverse sealing capacity of the large flow switching solenoid valve under the existing structure. Summary of the invention

[0003] The present invention provides a large flow switching solenoid valve and a hydraulic control unit of an automobile brake system, which are used to solve the defects in the prior art and achieve the following technical effects: the small flow port of a small flow valve seat and the large flow port of a large flow valve seat are automatically closed when the electromagnetic coil is powered off, and are automatically opened when the electromagnetic coil is powered on, thereby ensuring the sealing performance of the large flow switching solenoid valve and realizing the large flow opening of the large flow switching solenoid valve.

[0004] A large flow switching solenoid valve according to an embodiment of the first aspect of the present invention comprises: 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 arranged on the outside of the valve housing, 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 in the middle position of the electromagnetic coil; The moving 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 moving iron is connected to the fixed iron through a first elastic member, and the small flow valve seat is connected to the large flow valve seat through a second elastic member. The small flow valve seat and the moving 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 a small flow port of the small flow valve seat, the end of the small flow valve seat is provided with a second closing portion for closing or opening a 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 solenoid 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 solenoid valve is opened with a large flow.

[0005] According to one embodiment of the present invention, the large flow switching solenoid valve further includes: A valve seat limiting ring is fixed in the accommodating space and is located between the moving iron and the small flow valve seat, and a through hole for the first closing part to enter and exit is formed at the center of the valve seat limiting ring; The valve seat limiting ring is used to limit the position of the small flow valve seat so as not to exceed the lower surface of the valve seat limiting ring.

[0006] According to an embodiment of the present invention, 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 provided between the outer periphery of the valve seat limiting ring and the inner wall of the accommodating space.

[0007] According to one embodiment of the present invention, 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 through the small flow port and the large flow port in sequence; A sealing ring abutting against the inner wall of the accommodating space is fixedly sleeved on the outer periphery of the large flow valve seat.

[0008] According to an embodiment of the present invention, 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 communicated 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 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.

[0009] According to one embodiment of the present invention, 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 are connected to 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.

[0010] According to an embodiment of the present invention, 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; 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.

[0011] According to an embodiment of the present invention, the first sealing portion is a spherical sealing member, and a small valve port sealing cone surface cooperating with the spherical sealing member is formed at the small flow port.

[0012] According to one embodiment of the present invention, 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.

[0013] The hydraulic control unit of the automobile braking system according to the second embodiment of the present invention comprises the large flow switching solenoid valve as described in the first embodiment of the present invention; the hydraulic control unit also comprises a pressure control module, and the large flow switching solenoid valve is installed in the pressure control module.

[0014] The present invention provides a large-flow switching solenoid valve, which controls whether the electromagnetic coil is energized and based on the mechanical action produced by the first elastic member, the second elastic member and the fixed iron, the small-flow port of the small-flow valve seat and the large-flow port of the large-flow valve seat are automatically closed when the electromagnetic coil is powered off, and are automatically opened when the electromagnetic coil is powered on, thereby ensuring the sealing performance of the large-flow switching solenoid valve and realizing the large-flow opening of the large-flow switching solenoid valve.

[0015] Furthermore, the large flow switching solenoid valve of the present invention that can realize large flow switching 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 solenoid valve under different working conditions with positive pressure difference or negative pressure difference, and realize two-way 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 more brake fluid in a short time, shorten the time for the vehicle wheel cylinder to reach the required pressure, and thus realize rapid pressure regulation. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] In order to more clearly illustrate the technical solutions in the present invention or the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0017] Figure 1This is one of the structural schematic diagrams of the large flow switching solenoid valve provided by the present invention.

[0018] Figure 2 This is the second structural schematic diagram of the large flow switching solenoid valve provided by the present invention.

[0019] Figure 3 It is a structural schematic diagram of a small flow valve seat provided by the present invention.

[0020] Figure 4 It is a structural schematic diagram of a large flow valve seat provided by the present invention.

[0021] Figure 5 It is a structural schematic diagram of the valve seat limiting ring provided by the present invention.

[0022] Figure 6 It is a schematic diagram of the state of the large flow switching solenoid valve provided by the present invention when it is powered on.

[0023] Figure 7 It is a schematic diagram of the state of the large flow switching solenoid valve provided by the present invention when the power is off and high-pressure oil is input to the valve inlet.

[0024] Figure 8 It is a schematic diagram of the state of the large flow switching solenoid valve provided by the present invention when the power is off and high-pressure oil is input to the valve outlet.

[0025] Fig. 9 The present invention is a schematic structural diagram of a hydraulic control unit of an automobile braking system.

[0026] Reference numerals: 1. Large flow switching solenoid valve; 2. Electromagnetic coil; 2.1. Power-on pin; 3. Fixed iron; 4. First spring; 5. Magnetic isolation tube; 6. Moving iron; 6.1. First closing part; 7. Valve base; 8. Valve seat limit ring; 8.1. First oil-passing groove; 9. Small flow valve seat; 9.1. Small valve port sealing cone surface; 9.2. Second closing 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. Limit seat; 13. Valve outlet; 14. Small flow port; 15. Large flow port; 16. Hydraulic control unit; 17. Pressure control module. DETAILED DESCRIPTION

[0027] In order to make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the present invention will be clearly and completely described below in conjunction with the drawings of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0028] A large flow switching solenoid valve and a hydraulic control unit of an automobile braking system provided by the present invention will be described below with reference to the accompanying drawings.

[0029] like Figures 1 to 9 As shown, the large flow switching solenoid valve 1 according to the first embodiment of the present invention includes a valve housing, 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.

[0030] A fixed iron 3 is fixed at one end of the valve housing, and the other end of the valve housing is open to form a valve outlet 13; an accommodating space connected to the valve outlet 13 is formed inside the valve housing, and an electromagnetic coil 2 is also provided on the outside of the valve housing, and the electromagnetic coil 2 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 in the middle position of the electromagnetic coil 2.

[0031] The moving iron 6, the small flow valve seat 9 and the large flow valve seat 12 are all installed in the accommodating space, and in the direction along the fixed iron 3 toward the valve outlet 13, the moving iron 6, the small flow valve seat 9 and the large flow valve seat 12 are arranged in sequence, the moving iron 6 is connected to the fixed iron 3 through the first elastic member 4, the small flow valve seat 9 is connected to the large flow valve seat 12 through the second elastic member 10, and the small flow valve seat 9 and the moving iron 6 are both slidably arranged along the length direction of the valve housing.

[0032] Among them, the end of the moving iron 6 is provided with a first closing portion 6.1 for closing or opening the small flow port 14 of the small flow valve seat 9, and the end of the small flow valve seat 9 is provided with a second closing portion 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 are connected in sequence.

[0033] like Figure 7 and 8 As shown, when 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 6 As shown, when the electromagnetic coil 2 is energized, 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 with a large flow.

[0034] According to the large flow switching solenoid valve 1 of the embodiment of the present invention, the large flow switching solenoid valve 1 can be opened with a large flow rate while ensuring the sealing ability of the large flow switching solenoid valve 1, so that it has a larger flow capacity and can pass more brake fluid in a short time, thereby shortening the time for the vehicle wheel cylinder to reach the required pressure, thereby realizing rapid pressure regulation.

[0035] 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: like Figure 7 and 8 As shown, when the electromagnetic coil 2 is powered off, the fixed iron 3 has no magnetic force, and 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.

[0036] like Figure 6 As shown, when the electromagnetic coil 2 changes from being powered on to being powered on, 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 opens to the outside of the valve outlet 13 through the large flow port 15, that is, the large flow switching solenoid valve 1 opens with a large flow.

[0037] In the related art, the existing large flow switching solenoid valve for vehicle brake pressure control has a small valve port (<1mm) and limited oil flow capacity, which is not suitable for light commercial vehicles or off-road passenger vehicles with large wheel cylinders. Simply increasing the valve port diameter will further reduce the reverse sealing capacity of the large flow switching solenoid valve under the existing structure.

[0038] Therefore, in order to solve the technical defects existing in the above-mentioned related technologies, the present invention provides a large-flow switching solenoid valve with a large flow rate. 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 made by the large flow valve seat 12 are automatically closed when the electromagnetic coil 2 is powered off, and automatically opened when the electromagnetic coil 2 is powered on, thereby ensuring the sealing performance of the large-flow switching solenoid valve 1 while achieving the large-flow opening of the large-flow switching solenoid valve 1.

[0039] like Figure 2 As shown, according to some embodiments of the present invention, the large flow switching solenoid valve 1 further includes 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 for the first closing part 6.1 to enter and exit is formed at the center of the valve seat limiting ring 8. 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.

[0040] 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 to prevent the small flow valve seat 9 from exceeding the lower surface of the valve seat limiting ring 8 during the movement.

[0041] Specifically, when the electromagnetic coil 2 changes from being powered on to being powered on, the small flow valve seat 9 will move upward under the push of the second elastic member 10, that is, move toward the valve seat limit ring 8. At this time, the valve seat limit ring 8 can prevent the small flow valve seat 9 from moving excessively and causing the small flow port 14 to be closed again, that is, prevent the small flow valve seat 9 from cooperating with the first closing part 6.1 under the action of thrust, thereby accidentally closing the small flow port 14.

[0042] like Figure 2 and Figure 5 As shown, in a specific embodiment of the present invention, 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 provided 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 apart and evenly arranged.

[0043] In the related technology, the existing pressure-controlled large-flow switching solenoid valves are mainly divided into normally open, normally closed, and pilot-type large-flow switching solenoid valves. However, the above existing large-flow switching solenoid valves cannot form a seal under different working conditions with a two-way pressure difference, that is, they cannot form a two-way seal. That is, the existing large-flow switching solenoid valve used for vehicle brake pressure regulation only has a one-way sealing function. When the pressure of the brake line is reversed and reaches a certain pressure difference, the valve core of the large-flow switching solenoid valve opens naturally under the action of the liquid pressure, and has no sealing function. Based on the above-mentioned existing large-flow switching solenoid valve results, if it is necessary to achieve the purpose of two-way sealing in the automobile braking system, it is necessary to increase the number of large-flow switching solenoid valves in the pipeline, which causes the complication of the pipeline structure and the complication of the control logic, and increases the material cost and control cost.

[0044] Therefore, in order to solve the technical defects existing in the above-mentioned related technologies, Figure 2 As shown, according to some embodiments of the present invention, 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 solenoid valve 1.

[0045] Furthermore, the large flow valve seat 12 and the sealing ring 11 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 12, the sealing ring 11 and the inner wall of the accommodating space, and the oil pressure space is only connected to the valve outlet 13.

[0046] When the electromagnetic coil 2 is powered off 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 toward the small-flow valve seat 9 until one end surface of the small-flow valve seat 9 contacts the valve seat limit 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.

[0047] Thus, based on the above structure, the large flow switching solenoid valve 1 of the present invention can meet the valve port sealing requirements of the inlet and outlet oil ports of the large flow switching solenoid valve 1 under different working conditions with positive pressure difference or negative pressure difference, thereby realizing bidirectional sealing of pressure control.

[0048] For example Figure 4 As shown, a plurality of second oil-passing grooves 12.2 are 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 and are connected to the valve outlet 13. An 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.

[0049] 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.

[0050] It can be understood that 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, 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, that is, toward the direction of the small-flow valve seat 9.

[0051] The specific working principle and working process of the large flow switching solenoid valve with a bidirectional sealing function of the present invention are given in detail below. The concept of the bidirectional sealing function of the large flow switching solenoid valve of the present invention is explained as follows: the large flow switching solenoid valve 1 can achieve sealing when high-pressure oil is passed into the valve inlet and low-pressure oil is passed into the valve outlet 13, and the large flow switching solenoid valve 1 can also achieve sealing when low-pressure oil is passed into the valve inlet and high-pressure oil is passed into the valve outlet 13. The working principle and process of the large flow switching solenoid valve 1 under different working conditions are given below.

[0052] (i) High-pressure oil is passed to the valve inlet and low-pressure oil is passed to the valve outlet 13.

[0053] like Figure 7As shown, under this working condition, if the electromagnetic coil 2 is powered off 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 caused 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.

[0054] At this time, force analysis of the large flow valve seat 12 shows that the large 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 large flow valve seat 12 moves downward under the action of the two driving forces until the limit seat 12.3 on the outer periphery of the large flow valve seat 12 abuts against the inner wall of the valve outlet 13. At this time, the large flow switching solenoid valve 1 is in a closed state.

[0055] (ii) Low-pressure oil is introduced into the valve inlet and high-pressure oil is introduced into the valve outlet 13 .

[0056] like Figure 8 As shown, under this working condition, if the electromagnetic coil 2 is powered off and the fixed iron 3 has no magnetic force, 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 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 introduced from the valve inlet is located above the sealing ring 11, and the high-pressure oil introduced 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, a second downward elastic force applied to it by the second elastic member 10, and a first downward elastic force applied to it by the first elastic member 4 (for example, a second spring). Since the pressure differential 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, 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.

[0057] 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 elastic member 4 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 caused by the pressure difference. Furthermore, 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 differential force is greater than the first elastic force. Therefore, 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.

[0058] In summary, based on the above structure, the large flow switching solenoid valve 1 of the present invention can achieve a bidirectional sealing function.

[0059] like Figure 2 As shown, according to some embodiments of the present invention, the first elastic member 4 is a first spring, and the second elastic member 10 is a second spring.

[0060] like Figure 7 and 8 As shown, when the electromagnetic coil 2 is powered off, the first spring presses the first closing part 6.1 against the small flow valve seat 9 by elastic force, and the second spring is in a compressed state. In this way, the first closing part 6.1 can seal the small flow port 14, and the second closing part 9.2 can seal the large flow port 15.

[0061] like Figure 6 As shown, when the electromagnetic coil 2 is energized, the second spring pushes the small flow valve seat 9 away from the large flow valve seat 12 by elastic force, and the first spring is in a compressed state. In this way, it can be ensured that the first closing portion 6.1 is away from the small flow valve seat 9 to open the small flow port 14, and the second closing portion 9.2 is away from the large flow valve seat 12 to open the large flow port 15.

[0062] like Figure 2 and Figure 3 As shown, in some specific embodiments of the present invention, the first sealing portion 6.1 is a spherical sealing member, and a small valve port sealing cone surface 9.1 that cooperates with the spherical sealing member is formed at the small flow port 14. In this way, when the electromagnetic coil 2 is powered off, the surface of the spherical sealing member will be in close contact with the small valve port sealing cone surface 9.1, thereby forming a seal to prevent the fluid from passing through the small flow port 14.

[0063] like Figure 3 and Figure 4As shown, in some specific embodiments of the present invention, the second closing portion 9.2 is a sealing arc surface formed at the bottom of the small flow valve seat 9, and a large valve port sealing cone surface 12.1 matching the sealing arc surface is formed at the large flow port 15.

[0064] In this way, the above design enables the large flow switching solenoid valve 1 to maintain good sealing performance under high flow demand. When the electromagnetic coil 2 is powered off, the sealing arc surface of the second closing part 9.2 will be pressed against the large valve port sealing cone surface 12.1, and the geometric fit and material properties (such as elasticity or hardness) between them are used to ensure the sealing effect. The above design usually uses wear-resistant and corrosion-resistant materials to ensure that the sealing reliability can be maintained under long-term use and high-pressure environment.

[0065] When the electromagnetic coil is energized to open the large flow switching electromagnetic valve, the surface of the spherical closure and the small valve port sealing cone surface 9.1 will separate, and the sealing arc surface and the large valve port sealing cone surface 12.1 will separate, thereby allowing fluid to pass through the large flow port 15. For applications that need to handle large amounts of fluid or high-pressure fluid, this design can provide the necessary control and safety.

[0066] It should be pointed out that the above-mentioned embodiments of the first sealing portion 6.1 and the second sealing portion 9.2 are only for illustration and do not constitute any specific limitation on the structure of the first sealing portion 6.1 and the second sealing portion 9.2. The first sealing portion 6.1 and the second sealing portion 9.2 of the present invention may also adopt other sealing structures. The present invention does not impose any special limitation on this, as long as the first sealing portion 6.1 can seal the small flow port 14 and the second sealing portion 9.2 can seal the large flow port 15 respectively.

[0067] A specific embodiment of the large flow switching solenoid valve 1 of the present invention is given below with reference to the accompanying drawings.

[0068] 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.

[0069] The valve housing includes a magnetic isolation tube 5 and a valve seat 7. The magnetic isolation tube 5 and the valve seat 7 are fixed and interference fit. The outer side of the magnetic isolation tube 5 is surrounded by an electromagnetic coil 2. A fixed iron 3 is fixed to the upper end of the magnetic isolation tube 5. A movable iron 6 that can slide along the length direction of the magnetic isolation tube 5 is arranged inside the magnetic isolation tube 5. The lower end of the fixed iron 3 is connected to the upper end of the movable iron 6 through a first spring. A valve inlet is arranged on the side wall of the valve seat 7 and its lower end is open to form a valve outlet 13. A valve seat limiting ring 8, a small flow valve seat 9 and a large flow valve seat 12 are installed in the valve seat 7 from top to bottom, wherein the outer periphery of the valve seat limiting ring 8 is fixed on the inner wall of the valve seat 7, and a plurality of first oil passing grooves 8.1 are arranged between the outer periphery of the valve seat limiting ring 8 and the inner wall of the valve seat 7. The small flow valve seat 9 is connected to the large flow valve seat 12 through a second spring, and both the small flow valve seat 9 and the large flow valve seat 12 are slidably arranged along the length direction of the valve seat 7.

[0070] A first closing part 6.1 is fixed to the lower end of the moving iron 6, and the first closing part 6.1 is a spherical closing part. A through hole for the first closing part 6.1 to enter and exit is formed at the center of the valve seat limit ring 8. A small flow port 14 is formed at the upper end of the small flow valve seat 9, and a small valve port sealing cone 9.1 that cooperates with the spherical closing part is formed at the small flow port 14. A second closing part 9.2 is formed at the lower end of the small flow valve seat 9, and the second closing part 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, and a large valve port sealing cone 12.1 that cooperates with the sealing arc surface is formed at the large flow port 15. The large flow port 15 is connected to the valve outlet 13.

[0071] A limit seat 12.3 is also formed on the outer circumferential surface of the large-flow valve seat 12. In the direction from top to bottom, a sealing installation groove and a second oil-passing groove 12.2 are sequentially formed on the outer circumferential surface 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 circumferential surface of the limit seat 12.3.

[0072] An oil pressure space is defined between the second oil passing groove 12.2, the sealing ring 11 and the inner wall of the valve base 7, and an oil passing gap communicating with the oil pressure space is reserved between the outer peripheral surface of the lower end of the large flow valve seat 12 and the valve outlet 13.

[0073] 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.

[0074] (1) When the electromagnetic coil 2 is powered off and no oil is flowing 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 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 spring overcomes the elastic force of the second spring, 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 electromagnetic valve 1 is in a closed state.

[0075] (2) If Figure 7 As shown, when the electromagnetic coil 2 is powered off 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 powered off, 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 caused by the pressure difference. 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.

[0076] At this time, 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 elastic force transmitted by the second spring. At this time, the large flow valve seat 12 moves downward under the action of the two downward forces until the limit seat 12.3 on the outer periphery of the large flow valve seat 12 abuts against the inner wall of the valve outlet 13. At this time, the large flow switching solenoid valve 1 is in a closed state.

[0077] For example, the electromagnetic coil 2 is powered off, the liquid pressure P1 at the valve inlet ≥ 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.

[0078] The movable iron 6 presses the small flow port 14 downwards to form a seal under the pressure of the first spring and the pressure difference force formed by the pressure difference between the two oil ports. Since the pressure of the first spring is greater than the pressure of the second spring, the small flow valve seat 9 moves downwards under the downward pressure of the movable iron 6, compressing the second spring and closing the large flow port 15. Note: The pressure difference force on the movable iron 6 ,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.

[0079] 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.

[0080] (3) If Figure 8 As shown, when the electromagnetic coil 2 is powered off, 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, 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 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 to it 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.

[0081] 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 difference. 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. Therefore, 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.

[0082] 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 the valve outlet 13 are blocked. At this time, the pressure difference force on the moving iron 6 is less than the first elastic force of the first spring, and the moving iron 6 moves downward to close the small flow port 14. Note: The pressure difference force on the moving iron 6 ,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.

[0083] The pressure differential force on the large flow valve seat 12 is greater than the second elastic force of the second spring, and 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.

[0084] After the electromagnetic coil 2 is energized, the moving 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, the moving iron 6 moves upward, the small flow port 14 opens, and ΔP becomes smaller and smaller. Under the second elastic force, the large flow valve seat 12 moves downward, and the large flow port 15 opens, reaching the maximum flow of the large flow switching electromagnetic valve 1.

[0085] (4) If Figure 6 As shown, when the electromagnetic coil 2 changes from being powered on to being powered on, 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 opens to the outside of the valve outlet 13 through the large flow port 15, that is, the large flow switching solenoid valve 1 opens with a large flow.

[0086] For example, when the electromagnetic coil 2 is energized, the movable iron 6 is attracted to the fixed iron 3 under the action of the electromagnetic force, the small flow port 14 is opened, the liquid pressure P1 at the valve inlet and the liquid pressure P2 at the valve outlet 13 tend to be equal, and then the large flow port 15 is opened. The large flow switching electromagnetic valve 1 is in a fully open state, and the oil flow rate is the largest.

[0087] like Figures 1 to 9 As shown, the hydraulic control unit 16 of the automobile braking system according to the second embodiment of the present invention includes the large flow switching solenoid valve 1 as described in the first embodiment of the present invention, and also includes a pressure control module 17, and the large flow switching solenoid valve 1 is installed in the pressure control module 17.

[0088] According to some embodiments of the present invention, in the automobile braking system, the large flow switching solenoid valve 1 is used together with the electromagnetic coil 2, and the power-on pin 2.1 of the electromagnetic coil 2 is connected to the controller (ECU). The ECU controls the pin of the electromagnetic coil 2 to be powered on or off according to the vehicle state and the control logic pre-burned. After the pin is powered on, the coil forms a magnetic field inside due to electromagnetic induction. Under the action of the magnetic field, the moving iron 6 inside the large flow switching solenoid valve 1 compresses the return spring of the moving iron 6 and attracts the fixed iron 3, thereby causing the valve outlet 13 and the valve inlet to be connected to open the large flow switching solenoid valve 1. After the electromagnetic coil 2 is powered off, the magnetic field disappears, and the moving iron 6 inside the large flow switching solenoid valve 1 moves down, presses and closes the large flow port 15 and the small flow port 14 under the action of the return spring of the moving iron 6, forming a seal, thereby closing the large flow switching solenoid valve 1.

[0089] In summary, the present invention uses a new type of large flow switching large flow switching solenoid valve 1 for the brake pressure control module of the automobile brake system, which can meet the valve port sealing of the inlet and outlet of the large flow switching solenoid valve 1 under different working conditions with positive pressure difference or negative pressure difference, and realizes two-way 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 more brake fluid in a short time, shorten the time for the vehicle wheel cylinder to reach the required pressure, thereby realizing rapid pressure regulation.

[0090] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present invention.

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 arranged on the outside of the valve housing, 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 in the middle position of the electromagnetic coil; The moving 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 moving iron is connected to the fixed iron through a first elastic member, and the small flow valve seat is connected to the large flow valve seat through a second elastic member. The small flow valve seat and the moving 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 a small flow port of the small flow valve seat, the end of the small flow valve seat is provided with a second closing portion for closing or opening a 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 solenoid 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 solenoid valve is opened with a large flow.

2. The large flow switching solenoid valve according to claim 1, characterized in that: Also includes: A valve seat limiting ring is fixed in the accommodating space and is located between the moving iron and the small flow valve seat, and a through hole for the first closing part to enter and exit is formed at the center of the valve seat limiting ring; the valve seat limiting ring is used to limit the position of the small flow valve seat not to exceed the lower surface of the valve seat limiting ring.

3. The large flow switching solenoid valve according to claim 2, characterized in that: 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 arranged between the outer periphery of the valve seat limiting ring and the inner wall of the accommodating space.

4. The large flow switching solenoid valve according to claim 2, characterized in that: A valve inlet is provided on the side wall of the valve housing, and the valve inlet is connected to the accommodating space. 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.

5. The large flow switching solenoid valve according to claim 4, 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 communicated 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 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.

6. The large flow switching solenoid valve according to claim 5, characterized in that: A plurality of second oil-passing grooves are also 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 are connected to 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.

7. The large flow switching solenoid valve according to any one of claims 1 to 6, 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; 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.

8. The large flow switching solenoid valve according to any one of claims 1 to 6, characterized in that: The first sealing part is a spherical sealing member, and a small valve port sealing cone surface cooperating with the spherical sealing member is formed at the small flow port.

9. The large flow switching solenoid valve according to any one of claims 1 to 6, 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.

10. A hydraulic control unit for an automobile braking system, characterized in that: It comprises a large flow switching solenoid valve as described in any one of claims 1 to 9; the hydraulic control unit also comprises a pressure control module, and the large flow switching solenoid valve is installed in the pressure control module.

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