Normally-open high-flow switching electromagnetic valve and hydraulic control unit of automobile brake system

Abstract

The invention provides a normally-open large-flow switching electromagnetic valve and a hydraulic control unit of an automobile braking system. The electromagnetic valve comprises an electromagnetic coil, a valve shell, moving iron, a valve element, a small-flow valve seat and a large-flow valve seat. A containing space is formed in the valve shell, a valve element, a small-flow valve seat and a large-flow valve seat are sequentially arranged in the containing space from top to bottom, the valve element is connected with the moving iron, the electromagnetic coil is arranged around the moving iron and the valve shell, a first elastic piece is arranged between the valve element and the small-flow valve seat, and the small-flow valve seat is connected with the large-flow valve seat through a second elastic piece. When the electromagnetic coil is powered off, the valve element opens the small-flow opening, and the small-flow valve seat opens the large-flow opening, so that the electromagnetic valve is opened with large flow. When the electromagnetic coil is powered on, the valve element seals the small-flow opening, and the small-flow valve seat seals the large-flow opening, so that the electromagnetic valve is closed. The electromagnetic valve can meet the requirement that an oil inlet and an oil outlet of the electromagnetic valve are normally opened and keep high overflowing capacity, and therefore pressure can be rapidly regulated and controlled.

Description

Technical Field

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

[0002] In the related art, the existing normally open solenoid valves used for vehicle brake pressure regulation usually have a small valve port size and weak flow capacity, which will increase the braking time of commercial vehicles with large wheel cylinders and a large amount of fluid required for braking. If this problem needs to be solved, the existing normally open solenoid valve can only compensate by increasing the valve port diameter. However, after the valve port diameter increases, the solenoid valve flow rate increases, and it is necessary to increase the solenoid valve spring force, otherwise the solenoid valve will close automatically under the action of the Bernoulli principle. The increase in the solenoid valve spring force will increase the demand for electromagnetic force and electromagnetic coil current, which will worsen the power consumption and heat generation of the electromagnetic coil. At the same time, after the normally open valve with an increased valve port diameter is closed under the action of the electromagnetic coil, when a certain pressure appears at the oil outlet of the solenoid valve, the solenoid valve core naturally opens against the electromagnetic force under the action of the liquid pressure, causing the solenoid valve seal to fail. Summary of the invention

[0003] The present invention provides a normally open large flow switching solenoid valve and a hydraulic control unit of an automobile brake system, which are used to solve the defects existing in the prior art and achieve the following technical effects: the oil inlet and outlet of the solenoid valve can be normally open and maintain a large flow capacity, more brake fluid can pass through in a short time, and the time for the vehicle wheel cylinder and other brake control modules to reach the required pressure can be shortened, thereby realizing rapid pressure regulation. At the same time, when the solenoid valve is closed under the action of electromagnetic force, the solenoid valve can maintain good sealing performance, making the applicable working conditions of the solenoid valve more extensive.

[0004] A normally open large flow switching solenoid valve according to an embodiment of the first aspect of the present invention comprises a solenoid coil, a valve housing, a moving iron, a valve core, a small flow valve seat and a large flow valve seat; The valve housing is internally formed with a receiving space penetrating the upper and lower ends thereof, the valve core, the small flow valve seat and the large flow valve seat are sequentially arranged in the receiving space from top to bottom, the upper end of the valve core is connected to the moving iron and the electromagnetic coil is arranged around the moving iron and the valve housing, a first elastic member is arranged between the valve core and the small flow valve seat, the small flow valve seat is connected to the large flow valve seat via a second elastic member, and the small flow valve seat and the valve core are both slidably arranged along the central axis direction of the receiving space; The lower end of the valve core is provided with a first closing portion for closing or opening the small flow port of the small flow valve seat, and the lower end of the small flow valve seat is provided with a second closing portion for closing or opening the large flow port of the large flow valve seat, and the small flow port, the large flow port and the valve outlet formed at the lower end of the accommodating space are connected in sequence; When the electromagnetic coil is powered off, the valve core opens the small flow port, and the small flow valve seat opens the large flow port, so that the large flow switching electromagnetic valve is opened with a large flow; when the electromagnetic coil is powered on, the valve core closes the small flow port, and the small flow valve seat closes the large flow port, so that the large flow switching electromagnetic valve is closed.

[0005] According to one embodiment of the present invention, a valve seat limiting portion is further provided in the accommodating space, the valve seat limiting portion is located between the valve core and the small flow valve seat, and the valve seat limiting portion divides the accommodating space into a first space located on its upper side and a second space located on its lower side, and the first space and the second space are connected through a through hole located at the center of the valve seat limiting portion; The small flow valve seat passes through the through hole and enters the second space, and the upper surface of the valve seat limiting portion abuts against the lower end of the first elastic member, and the lower surface of the valve seat limiting portion abuts against the limiting boss of the small flow valve seat.

[0006] According to one embodiment of the present invention, the valve seat limiting portion is integrally formed with the valve housing, and the interior of the valve housing extends inwardly to form the annular valve seat limiting portion; Alternatively, the valve seat limiting portion and the valve housing are manufactured separately, wherein the valve seat limiting portion is pressed into the valve housing by interference fit.

[0007] According to one embodiment of the present invention, a valve inlet and a valve port are provided on the valve housing, the valve port is connected to the first space, and the valve inlet is connected to the second space; when the large flow switching solenoid valve is used in a hydraulic control unit, the first space and the second space are connected through the valve inlet and the valve port to achieve pressure balance; And when the electromagnetic coil is powered off, the valve port is connected to the valve outlet through the first space, the small flow port and the large flow port in sequence, and the valve inlet is connected to the valve outlet through the second space and the large flow port in sequence; a sealing ring is fixedly sleeved on the outer periphery of the large flow valve seat and abuts against the inner wall of the second space.

[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 energized and high-pressure oil is passed to the valve outlet and low-pressure oil is passed to the valve inlet, the high-pressure oil enters the oil pressure space to push the large-flow valve seat to slide toward the small-flow valve seat. At this time, the valve core closes the small-flow port, the small-flow valve seat closes the large-flow port, and the limiting boss of the small-flow valve seat abuts against the valve seat limiting portion.

[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 energized, the downward electromagnetic force is greater than the sum of the upward first spring force and the second spring force, the movable iron presses the first closing portion of the valve core onto the small flow valve seat, and the second closing portion of the small flow valve seat onto the large flow valve seat, at which time the first spring and the second spring are both in a compressed state; When the electromagnetic coil is powered off, the first spring pushes the valve core away from the small flow valve seat by elastic force, and the second spring pushes the small flow valve seat away from the large flow valve seat by elastic force.

[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 spherical arc surface formed at the bottom of the small flow valve seat, and a large valve port sealing conical surface matching the sealing arc surface is formed at the large flow port.

[0013] The hydraulic control unit of the automobile braking system according to the second aspect of the present invention comprises a normally open large flow switching solenoid valve as described in the first aspect 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 normally open large flow switching solenoid valve, which is used in a brake pressure control module of an automobile brake system. The solenoid valve oil inlet and outlet ports are normally open and maintain a large flow capacity, and a large amount of brake fluid can pass through in a short time, shortening the time for the vehicle wheel cylinder and other brake control modules to reach the required pressure, thereby realizing rapid pressure regulation. At the same time, when the solenoid valve is closed under the action of electromagnetic force, the solenoid valve can maintain good sealing performance, making the solenoid valve more widely applicable.

[0015] In addition, compared with the related art, the present invention has at least the following advantages.

[0016] (1) High flow opening capability in normally open state: When the electromagnetic coil is de-energized, the solenoid valve automatically remains in the open state, i.e. the normally open state. In this state, the solenoid valve is able to achieve high flow opening, which means that a large amount of brake fluid can pass through in a short period of time. This helps to shorten the time it takes for the vehicle wheel cylinder to reach the required pressure, thereby achieving faster pressure regulation.

[0017] (2) Fast response and pressure regulation: The solenoid valve can allow a large amount of brake fluid to pass through in a short period of time, which helps to improve the response speed of the braking system. Fast pressure regulation is particularly important in emergency braking situations and can significantly improve driving safety.

[0018] (3) Good sealing performance: When the electromagnetic coil is energized, the solenoid valve can be reliably closed to ensure good sealing performance. This efficient sealing ability helps prevent brake fluid leakage and ensure the stability and reliability of the brake system.

[0019] (4) Good bidirectional pressure resistance performance: When the electromagnetic coil is energized, when there is a large positive pressure difference or negative pressure difference between the valve inlet and the valve outlet, the closing sealing of the electromagnetic valve can be guaranteed.

[0020] In summary, the present invention, through its unique structural design and working principle, not only improves the large flow opening capability of the solenoid valve in the normally open state, but also ensures good sealing performance in the closed state, thereby improving the performance and safety of the entire braking system. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] 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.

[0022] Figure 1 This is one of the structural schematic diagrams of the large flow switching solenoid valve provided by the present invention.

[0023] Figure 2 This is the second structural schematic diagram of the large flow switching solenoid valve provided by the present invention.

[0024] Figure 3 It is a structural schematic diagram of the valve housing provided by the present invention.

[0025] Figure 4 It is a structural schematic diagram of a small flow valve seat provided by the present invention.

[0026] Figure 5 It is a structural schematic diagram of a large flow valve seat provided by the present invention.

[0027] Figure 6 It is a structural schematic diagram of the large flow switching solenoid valve provided by the present invention when the solenoid coil is powered off.

[0028] Figure 7 It is a structural schematic diagram of the large flow switching solenoid valve provided by the present invention when the solenoid coil is energized and high-pressure oil is introduced into the valve inlet.

[0029] Figure 8 It is a structural schematic diagram of the large flow switching solenoid valve provided by the present invention when the solenoid coil is energized and high-pressure oil is introduced into the valve outlet.

[0030] Fig. 9 This is one of the partial structural schematic diagrams of the large flow switching solenoid valve provided by the present invention.

[0031] Fig.10 This is the second partial structural schematic diagram of the large flow switching solenoid valve provided by the present invention.

[0032] Fig.11 This is the third partial structural schematic diagram of the large flow switching solenoid valve provided by the present invention.

[0033] Fig.12 This is the fourth partial structural schematic diagram of the large flow switching solenoid valve provided by the present invention.

[0034] Fig.13 The present invention is a schematic structural diagram of a hydraulic control unit of an automobile braking system.

[0035] Reference numerals: 1. Large flow switching solenoid valve; 2. Solenoid coil; 2.1. Power-on pin; 3. Magnetic isolation tube; 4. Moving iron; 5. Valve core; 6. First elastic part; 7. Valve housing; 7.1. Valve inlet; 7.2. Valve port; 7.3. Valve seat limiter; 8. Limit baffle; 9. Small flow valve seat; 9.1. Small valve port sealing cone; 9.2. Second closing part; 10. Second elastic part; 11. Sealing ring; 12. Large flow valve seat; 12.1. Large valve port sealing cone; 12.2. Second oil groove; 13. Valve outlet; 14. Small flow port; 15. Large flow port; 16. Hydraulic control unit; 17. Pressure control module. DETAILED DESCRIPTION

[0036] 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.

[0037] In the description of the embodiments of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the embodiments of the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as limitations on the embodiments of the present invention. In addition, the terms "first", "second", and "third" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance.

[0038] In the description of the embodiments of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "connected" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms in the embodiments of the present invention can be understood according to specific circumstances.

[0039] In the embodiments of the present invention, unless otherwise clearly specified and limited, the first feature being "above" or "below" the second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, the first feature being "above", "above" and "above" the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. The first feature being "below", "below" and "below" the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0040] A normally open large flow switching solenoid valve 1 and a hydraulic control unit 16 of a vehicle braking system having the large flow switching solenoid valve 1 provided by the present invention will be described below with reference to the accompanying drawings.

[0041] like Figures 1 to 13 As shown, the normally open large flow switching solenoid valve 1 according to the first embodiment of the present invention includes a solenoid coil 2, a valve housing 7, a moving iron 4, a valve core 5, a small flow valve seat 9 and a large flow valve seat 12.

[0042] The interior of the valve housing 7 is formed with a receiving space that runs through the upper and lower ends thereof, and the receiving space is provided with a valve core 5, a small flow valve seat 9 and a large flow valve seat 12 in sequence from top to bottom. The upper end of the valve core 5 is connected to the moving iron 4 (for example, the upper end of the valve core 5 is in contact with the moving iron 4, etc., and the present invention does not impose any special restrictions here), and the electromagnetic coil 2 is arranged around the moving iron 4 and the valve housing 7. A first elastic member 6 is provided between the valve core 5 and the small flow valve seat 9, and the small flow valve seat 9 is connected to the large flow valve seat 12 via a second elastic member 10, and the small flow valve seat 9 and the valve core 5 are both slidably arranged along the central axis direction of the receiving space. A limit baffle 8 is also provided in the valve housing 7, and the limit baffle 8 is located in the valve outlet 13 and is interference fit with the valve housing 7, and its upper surface is in contact with the valve housing 7.

[0043] Among them, the lower end of the valve core 5 is provided with a first closing portion for closing or opening a small flow port 14 of a small flow valve seat 9, and the lower end of the small flow valve seat 9 is provided with a second closing portion 9.2 for closing or opening a large flow port 15 of a large flow valve seat 12, and the small flow port 14, the large flow port 15 and the valve outlet 13 formed at the lower end of the accommodating space are connected in sequence.

[0044] When the electromagnetic coil 2 is powered off, the valve core 5 opens the small flow port 14, and the small flow valve seat 9 opens the large flow port 15, so that the large flow switching electromagnetic valve 1 is opened with a large flow; when the electromagnetic coil 2 is powered on, the valve core 5 closes the small flow port 14, and the small flow valve seat 9 closes the large flow port 15, so that the large flow switching electromagnetic valve 1 is closed.

[0045] The large flow switching solenoid valve 1 according to the embodiment of the present invention can maintain a normally open state when the electromagnetic coil 2 is powered off, and can achieve a large flow opening in the normally open state, thereby having a larger flow capacity, 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 achieving rapid pressure regulation.

[0046] Specifically, the working principle and working process of the large flow switching solenoid valve 1 to achieve large flow while ensuring normal opening are as follows: like Figure 1 As shown, when the electromagnetic coil 2 is powered off, the valve housing 7 has no magnetic force (it can be understood that in the structure of the present invention, the valve housing 7 is equivalent to the fixed iron). At this time, under the action of the first upward elastic force applied by the first elastic member 6 to the valve core 5, the valve core 5 moves upward and takes the movable iron 4 away from the valve housing 7. At this time, the first closing portion located at the lower end of the valve core 5 is away from the small flow valve seat 9, so that the small flow port 14 of the small flow valve seat 9 is opened; and under the action of the second upward elastic force applied by the second elastic member 10 to the small flow valve seat 9, the small flow valve seat 9 moves upward. At this time, the second closing portion 9.2 located at the lower end of the small flow valve seat 9 is away from the large flow valve seat 12, so that the large flow port 15 of the large flow valve seat 12 is also opened. Therefore, the liquid entering the accommodating space can flow out to the outside of the valve housing 7 through the small flow port 14 and the large flow port 15, so that the large flow switching electromagnetic valve 1 can achieve large flow operation in the normally open state.

[0047] like Figure 7 and 8 As shown, when the electromagnetic coil 2 changes from being powered on to being powered on, the valve housing 7 generates a magnetic force, and the moving iron 4 is acted upon by the downward magnetic force exerted on it by the valve housing 7. At this time, the valve core 5 is simultaneously acted upon by the downward first electromagnetic force exerted on it by the moving iron 4 and the upward first elastic force exerted on it by the first elastic member 6. Since the first electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and causes the first closing portion to close the small flow port 14 of the small flow valve seat 9; further, the small flow valve seat 9 is acted upon by the downward pressure force exerted on it by the valve core 5, and the small flow valve seat 9 is also acted upon by the upward second elastic force exerted on it by the second elastic member 10. Since the pressure force is greater than the second elastic force, the small flow valve seat 9 and the large flow valve seat 12 are brought close to each other, so that the second closing portion 9.2 of the small flow valve seat 9 closes the large flow port 15 of the large flow valve seat 12, thereby realizing the closing of the large flow switching electromagnetic valve 1, and its sealing performance is good in the closed state.

[0048] In the related art, the existing normally open solenoid valves used for vehicle brake pressure regulation usually have a small valve port size and weak flow capacity, which will increase the braking time of commercial vehicles with large wheel cylinders and a large amount of fluid required for braking. If this problem needs to be solved, the existing normally open solenoid valve can only compensate by increasing the valve port diameter. However, after the valve port diameter increases, the solenoid valve flow rate increases, and it is necessary to increase the solenoid valve spring force, otherwise the solenoid valve will close automatically under the action of the Bernoulli principle. The increase in the solenoid valve spring force will increase the demand for electromagnetic force and electromagnetic coil current, which will worsen the power consumption and heat generation of the electromagnetic coil. At the same time, after the normally open valve with an increased valve port diameter is closed under the action of the electromagnetic coil, when a certain pressure appears at the oil outlet of the solenoid valve, the solenoid valve core naturally opens against the electromagnetic force under the action of the liquid pressure, causing the solenoid valve seal to fail.

[0049] Therefore, in order to solve the technical defects existing in the above-mentioned related technologies, the present invention provides a normally open large flow switching solenoid valve 1, which is used in the brake pressure control module 17 of the automobile brake system, and can meet the requirements of the normally open inlet and outlet of the solenoid valve and maintain a large flow capacity, and can pass more brake fluid in a short time, shortening the time for the vehicle wheel cylinder and other brake control modules to reach the required pressure, thereby realizing rapid pressure regulation. At the same time, when the solenoid valve is closed under the action of electromagnetic force, the solenoid valve can maintain good sealing performance, making the solenoid valve more widely applicable.

[0050] In addition, compared with the related art, the present invention has at least the following advantages.

[0051] (1) High flow opening capability in the normally open state: When the electromagnetic coil 2 is de-energized, the solenoid valve automatically remains in the open state, i.e. the normally open state. In this state, the solenoid valve is able to achieve high flow opening, which means that a large amount of brake fluid can pass through in a short period of time. This helps to shorten the time it takes for the vehicle wheel cylinder to reach the required pressure, thereby achieving faster pressure regulation.

[0052] (2) Fast response and pressure regulation: The solenoid valve can allow a large amount of brake fluid to pass through in a short period of time, which helps to improve the response speed of the braking system. Fast pressure regulation is particularly important in emergency braking situations and can significantly improve driving safety.

[0053] (3) Good sealing performance: When the electromagnetic coil 2 is energized, the electromagnetic valve can be reliably closed to ensure good sealing performance. This efficient sealing ability helps prevent brake fluid leakage and ensure the stability and reliability of the brake system.

[0054] (4) Good bidirectional pressure resistance performance: When the electromagnetic coil 2 is energized, when a large positive pressure difference or negative pressure difference appears between the valve inlet 7.1 and the valve outlet 13, the closing sealing of the electromagnetic valve can be guaranteed.

[0055] In summary, the present invention, through its unique structural design and working principle, not only improves the large flow opening capability of the solenoid valve in the normally open state, but also ensures good sealing performance in the closed state, thereby improving the performance and safety of the entire braking system.

[0056] like Figure 3 As shown, according to some embodiments of the present invention, a valve seat limiter 7.3 is further provided in the accommodating space, the valve seat limiter 7.3 is located between the valve core 5 and the small flow valve seat 9, and the valve seat limiter 7.3 divides the accommodating space into a first space located on its upper side and a second space located on its lower side, and the first space and the second space are connected via a through hole located at the center of the valve seat limiter 7.3.

[0057] The small flow valve seat 9 passes through the through hole and enters the second space, and the upper surface of the valve seat limiting portion 7.3 abuts against the lower end of the first elastic member 6, and the lower surface of the valve seat limiting portion 7.3 abuts against the limiting boss of the small flow valve seat 9.

[0058] It can be understood that the upper surface of the valve seat limiter 7.3 contacts the lower end of the first elastic member 6, playing the role of supporting the first elastic member 6; while the lower surface of the valve seat limiter 7.3 contacts the limiter boss of the small flow valve seat 9, limiting the movement range of the small flow valve seat 9. That is, the main purpose of the valve seat limiter 7.3 is to limit the position of the small flow valve seat 9, so as to prevent the small flow valve seat 9 from exceeding the lower surface of the valve seat limiter ring during movement.

[0059] Specifically, when the electromagnetic coil 2 is powered off, since the valve core 5 and the small flow valve seat 9 are not affected by the electromagnetic force, 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 portion 7.3. At this time, the valve seat limit portion 7.3 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 portion under the action of thrust, thereby accidentally closing the small flow port 14.

[0060] like Figure 3 As shown, further, the valve seat limiting portion 7.3 is integrally formed with the valve housing 7, and the interior of the valve housing 7 extends inwardly to form an annular valve seat limiting portion 7.3.

[0061] It is understood that the valve seat limiter 7.3 and the valve housing 7 are manufactured in the same manufacturing process, rather than being manufactured separately and then assembled together. The valve seat limiter 7.3 divides the accommodation space into two parts through its annular structure, which can better control the position and movement of different components.

[0062] In this way, the one-piece design increases the strength of the overall structure and reduces the risk of leakage caused by the connection parts. At the same time, one-piece molding reduces the assembly steps, simplifies the manufacturing process, and helps to reduce production costs.

[0063] Alternatively, the valve seat limiting portion 7.3 and the valve housing 7 are manufactured separately, wherein the valve seat limiting portion 7.3 is pressed into the valve housing 7 by interference fit.

[0064] like Figure 3 As shown, according to some embodiments of the present invention, a valve inlet 7.1 and a valve port 7.2 are provided on the valve housing 7, the valve port 7.2 is connected to the first space, the valve inlet 7.1 is connected to the second space, and when the electromagnetic coil 2 is powered off, the valve port 7.2 is connected to the valve outlet 13 via the first space, the small flow port 14 and the large flow port 15 in sequence, and the valve inlet 7.1 is connected to the valve outlet 13 via the second space and the large flow port 15 in sequence.

[0065] Furthermore, when a large flow rate switching solenoid valve is used in the hydraulic control unit 16, the first space and the second space are connected through the valve inlet 7.1 and the valve port 7.2 to achieve pressure balance.

[0066] It should be pointed out that when a large flow switching solenoid valve is applied to the hydraulic control unit 16, a closed space is formed outside the valve inlet 7.1 and the valve port 7.2, and the first space and the second space can be connected by the valve inlet 7.1 and the valve port 7.2 in the closed space to achieve pressure balance.

[0067] Specifically, when the electromagnetic coil 2 is powered off, the first space and the second space can achieve pressure balance through the connection between the valve inlet 7.1 and the valve port 7.2 in the closed space, which can ensure the smooth flow of the medium between the valve inlet 7.1 and the valve outlet 13, avoid the existence of pressure difference affecting the smooth flow of the electromagnetic valve, and ensure the flow effect of the electromagnetic valve. In addition, when the electromagnetic coil 2 changes from power on to power off, the first space and the second space can achieve pressure balance through the connection between the valve inlet 7.1 and the valve port 7.2 in the closed space, thereby gradually reducing the pressure difference between the valve inlet 7.1 and the valve outlet 13, and helping the electromagnetic valve to open smoothly.

[0068] 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.

[0069] Therefore, in order to solve the technical defects existing in the above-mentioned related technologies, Figure 1 and 5 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.

[0070] like Figure 1 and 5 As shown, further, the large flow valve seat 12 and the sealing ring 11 are both slidably arranged along the length direction of the valve housing 7; and an oil pressure space is defined between the outer peripheral surface of the large flow valve seat 12, the sealing ring 11 and the inner wall of the accommodating space, and the oil pressure space is only connected to the valve outlet 13.

[0071] For example, when the electromagnetic coil 2 is energized and high-pressure oil is passed to the valve outlet 13 and low-pressure oil is passed to the valve inlet 7.1, the high-pressure oil enters the oil pressure space to push the large-flow valve seat 12 to slide toward the direction close to the small-flow valve seat 9. At this time, the valve core 5 closes the small-flow port 14, the small-flow valve seat 9 closes the large-flow port 15, and the limiting boss of the small-flow valve seat 9 abuts against the valve seat limiting portion 7.3.

[0072] For another example, when the electromagnetic coil 2 is energized and high-pressure oil is passed to the valve inlet 7.1 and low-pressure oil is passed to the valve outlet 13, this situation is a normal situation during use and will not be specifically introduced here. In the above situation, the large-flow switching solenoid valve 1 of the present invention can also achieve closed sealing.

[0073] 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.

[0074] like Figure 1 and5 As shown, in some specific embodiments of the present invention, a plurality of second oil-passing grooves 12.2 are further formed on the outer peripheral surface of the large-flow valve seat 12 between the sealing ring 11 and the valve outlet 13. The second oil-passing grooves 12.2 extend along the length direction of the valve housing 7 and are 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.

[0075] like Figure 1 and 5 As shown, further, a limit seat is formed on the outer circumference of the large flow valve seat 12, and an annular sealing installation groove is formed on the outer circumference of the limit seat, and a sealing ring 11 is fixed in the sealing installation groove.

[0076] 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.

[0077] The specific working principle and working process of the large flow switching solenoid valve 1 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 1 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 7.1 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 7.1 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.

[0078] (i) High-pressure oil is passed to the valve inlet 7.1 and low-pressure oil is passed to the valve outlet 13.

[0079] like Figure 7 As shown, under this working condition, if the electromagnetic coil 2 is energized, the valve housing 7 generates magnetic force, the moving iron 4 is subjected to the downward electromagnetic force exerted on it by the valve housing 7, and the moving iron 4 transmits the downward electromagnetic force to the valve core 5 connected thereto. At this time, a force analysis of the valve core 5 shows that the valve core 5 is subjected to the downward electromagnetic force transmitted by the valve housing 7 through the moving iron 4, and the valve core 5 is also subjected to the upward first elastic force exerted on it by the first elastic member 6. It can be understood that since the electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and approaches the small flow valve seat 9, thereby causing the first closing portion to close the small flow port 14 of the small flow valve seat 9.

[0080] Furthermore, from the force analysis of the small flow valve seat 9 at this time, it can be known that the small flow valve seat 9 is subjected to the downward pressure force exerted on it by the valve core 5, and due to the pressure difference between the high-pressure oil above the small flow valve seat 9 (the high-pressure oil passed into the valve inlet 7.1) and the low-pressure oil below the small flow valve seat 9 (the low-pressure oil passed into the valve outlet 13), the small flow valve seat 9 is also subjected to the downward pressure difference force brought about by the pressure difference. Furthermore, the small flow valve is also subjected to the upward second elastic force transmitted by the second elastic member 10. At this time, the sum of the pressure force and the pressure difference force is greater than the second elastic force. Therefore, the small flow valve seat 9 moves downward, thereby causing the second closing portion 9.2 to close the large flow port 15 of the large flow valve seat 12.

[0081] Further, at this time, the force analysis of the large flow valve seat 12 shows that the large flow valve seat 12 is subjected to the downward 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 on the periphery of the large flow valve seat 12 abuts against the limit baffle 8, the limit baffle 8 and the valve housing 7 have an interference fit, and the upper surface of the limit baffle 8 contacts the sink surface of the valve housing 7. At this time, the large flow switching solenoid valve 1 is in a closed state.

[0082] (ii) Low-pressure oil is passed into the valve inlet 7.1 and high-pressure oil is passed into the valve outlet 13.

[0083] like Figure 8 As shown, under this working condition, if the electromagnetic coil 2 is energized, the valve housing 7 generates magnetic force, the moving iron 4 is subjected to the downward electromagnetic force exerted on it by the valve housing 7, and the moving iron 4 transmits the downward electromagnetic force to the valve core 5 connected thereto. At this time, a force analysis of the valve core 5 shows that the valve core 5 is subjected to the downward electromagnetic force transmitted by the valve housing 7 through the moving iron 4, and the valve core 5 is also subjected to the upward first elastic force exerted on it by the first elastic member 6. It can be understood that since the electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and approaches the small flow valve seat 9, thereby causing the first closing portion to close the small flow port 14 of the small flow valve seat 9.

[0084] While delivering high-pressure oil to the valve outlet 13, the high-pressure oil will enter the oil pressure space and flow to the sealing ring 11 through the second oil-passing groove 12.2. At this time, since the low-pressure oil above the sealing ring 11 is introduced from the valve inlet 7.1, and the high-pressure oil below the sealing ring 11 is introduced from the second oil-passing groove 12.2, the high-pressure oil will exert an upward pressure differential force on the sealing ring 11 under the pressure difference between the high-pressure oil and the low-pressure oil. At this time, 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 downward second elastic force applied to it by the second elastic member 10, and a downward pressure force applied to it by the small flow valve seat 9. Since the pressure differential force is greater than the downward pressure force and the second elastic force applied to it by the small flow valve seat 9, the large flow valve seat 12 is pushed to move upward, that is, to move in the direction of the small flow valve seat 9, pushing the small flow valve seat 9 to move upward until the small flow valve seat 9 abuts against the valve seat limiter 7.3, the large flow valve seat 12 and the small flow valve seat 9 no longer move, and the large flow port 15 is still closed. However, due to the electromagnetic force, the valve core 5 is still in contact with the small flow valve seat 9 at this time, and the small flow port 14 is still closed.

[0085] In summary, based on the above structure, the large flow switching solenoid valve 1 of the present invention can achieve a bidirectional sealing function.

[0086] like Figure 1 As shown, according to some embodiments of the present invention, the first elastic member 6 is a first spring, and the second elastic member 10 is a second spring.

[0087] When the electromagnetic coil 2 is energized, the downward electromagnetic force is greater than the sum of the upward first spring force and the second spring force, and the moving iron 4 presses the first closing part of the valve core 5 onto the small flow valve seat 9, and the second closing part 9.2 of the small flow valve seat 9 is pressed onto the large flow valve seat 12. At this time, the first spring and the second spring are both in a compressed state.

[0088] When the electromagnetic coil 2 is de-energized, the first spring pushes the valve core 5 away from the small flow valve seat 9 by elastic force, and the second spring pushes the small flow valve seat 9 away from the large flow valve seat 12 by elastic force.

[0089] like Figure 1 and 4 As shown, in some specific embodiments of the present invention, the first sealing part 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 energized, 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.

[0090] like Figure 1 , 4As shown in FIG. 5 , in some specific embodiments of the present invention, the second closing portion 9.2 is a sealing spherical arc surface formed at the bottom of the small flow valve seat 9, and a large valve port sealing conical surface 12.1 matching the sealing arc surface is formed at the large flow port 15.

[0091] 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 energized, the sealing spherical arc surface of the second closing part 9.2 will be pressed against the large valve port sealing conical surface 12.1, and the geometric 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.

[0092] When the electromagnetic coil 2 is de-energized to open the large flow switching electromagnetic valve 1, the surface of the spherical closure and the small valve port sealing cone surface 9.1 will separate, and the sealing ball arc surface and the large valve port sealing cone surface 12.1 will separate, thereby allowing the 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.

[0093] It should be pointed out that the above-mentioned embodiments of the first sealing portion 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 and the second sealing portion 9.2. The first sealing portion 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 here, as long as the first sealing portion can seal the small flow port 14 and the second sealing portion 9.2 can seal the large flow port 15 respectively.

[0094] A specific embodiment of the large flow switching solenoid valve 11 of the present invention is given below with reference to the accompanying drawings.

[0095] like Figures 1 to 12 As shown, the large flow switching solenoid valve 1 includes a solenoid coil 2, a valve housing 7, a moving iron 4, a valve core 5, a small flow valve seat 9, a large flow valve seat 12, a sealing ring 11, a first spring and a second spring.

[0096] A accommodating space is formed inside the valve housing 7 and runs through its upper and lower ends. A valve core 5, a small flow valve seat 9 and a large flow valve seat 12 are arranged in sequence from top to bottom in the accommodating space. The upper end of the valve core 5 is connected to the moving iron 4 and the electromagnetic coil 2 is arranged around the moving iron 4 and the valve housing 7. A first spring is provided between the valve core 5 and the small flow valve seat 9. The small flow valve seat 9 is connected to the large flow valve seat 12 by a second spring, and the small flow valve seat 9 and the valve core 5 are both slidably arranged along the central axis direction of the accommodating space.

[0097] Among them, the lower end of the valve core 5 is provided with a first closing portion for closing or opening a small flow port 14 of a small flow valve seat 9, and the lower end of the small flow valve seat 9 is provided with a second closing portion 9.2 for closing or opening a large flow port 15 of a large flow valve seat 12, and the small flow port 14, the large flow port 15 and the valve outlet 13 formed at the lower end of the accommodating space are connected in sequence.

[0098] A valve seat limiter 7.3 is also provided in the accommodating space. The valve seat limiter 7.3 is located between the valve core 5 and the small flow valve seat 9, and the valve seat limiter 7.3 divides the accommodating space into a first space located on its upper side and a second space located on its lower side. The first space and the second space are connected through a through hole located at the center of the valve seat limiter 7.3.

[0099] The small flow valve seat 9 passes through the through hole and enters the second space, and the upper surface of the valve seat limiting portion 7.3 abuts against the lower end of the first elastic member 6, and the lower surface of the valve seat limiting portion 7.3 abuts against the limiting boss of the small flow valve seat 9.

[0100] The valve housing 7 is provided with a valve inlet 7.1 and a valve port 7.2. The valve port 7.2 is connected to the first space, and the valve inlet 7.1 is connected to the second space.

[0101] The large flow valve seat 12 and the sealing ring 11 are both slidably arranged along the length direction of the valve housing 7; and an oil pressure space is defined between the outer peripheral surface of the large flow valve seat 12, the sealing ring 11 and the inner wall of the accommodation space, and the oil pressure space is only connected to the valve outlet 13. A plurality of second oil passing grooves 12.2 are also formed on the outer peripheral surface of the large flow valve seat 12 located between the sealing ring 11 and the valve outlet 13, and the second oil passing grooves 12.2 extend along the length direction of the valve housing 7 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 accommodation space.

[0102] A limit seat is also formed on the outer circumference of the large flow valve seat 12, and an annular sealing installation groove is formed on the outer circumference of the limit seat, and a sealing ring 11 is fixed in the sealing installation groove. A limit baffle 8 is also provided below the limit seat, and the limit baffle 8 is located at the valve outlet 13 and is used to limit the large flow valve seat 12 to prevent the large flow valve seat 12 from exceeding the position of the valve outlet 13.

[0103] The specific working principle of the large flow switching solenoid valve 11 of the present invention is described below based on the above specific embodiments.

[0104] (1) If Figure 6As shown, when the electromagnetic coil 2 is powered off: the valve housing 7 has no magnetic force. At this time, under the action of the first upward elastic force applied by the first spring to the valve core 5, the valve core 5 moves upward and takes the moving iron 4 away from the valve housing 7. At this time, the first closing portion at the lower end of the valve core 5 is away from the small flow valve seat 9, so that the small flow port 14 of the small flow valve seat 9 is opened; and under the action of the second upward elastic force applied by the second spring to the small flow valve seat 9, the small flow valve seat 9 moves upward. At this time, the second closing portion 9.2 at the lower end of the small flow valve seat 9 is away from the large flow valve seat 12, so that the large flow port 15 of the large flow valve seat 12 is also opened. Therefore, the liquid entering the accommodating space can flow out to the outside of the valve housing 7 through the small flow port 14 and the large flow port 15, so that the large flow switching electromagnetic valve 1 can achieve large flow operation in the normally open state.

[0105] like Fig. 9 As shown, at this time, the axial clearance L1 between the moving iron 4 and the valve housing 7 is larger than the sum of the axial clearance L2 between the valve core 5 and the small flow valve seat 9 and the axial clearance L3 between the small flow valve seat 9 and the large flow valve seat 12, that is, .

[0106] (2) If Figure 7 As shown, when the electromagnetic coil 2 is energized, high-pressure oil is passed into the valve inlet 7.1, and low-pressure oil is passed into the valve outlet 13: under this working condition, if the electromagnetic coil 2 is energized, the valve housing 7 generates magnetic force, the moving iron 4 is subjected to the downward electromagnetic force exerted on it by the valve housing 7, and the moving iron 4 transmits the downward electromagnetic force to the valve core 5 connected thereto. At this time, a force analysis of the valve core 5 shows that the valve core 5 is subjected to the downward electromagnetic force transmitted by the valve housing 7 through the moving iron 4, and the valve core 5 is also subjected to the upward first elastic force exerted on it by the first elastic member 6. It can be understood that since the electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and approaches the small flow valve seat 9, thereby causing the first closing portion to close the small flow port 14 of the small flow valve seat 9.

[0107] Furthermore, from the force analysis of the small flow valve seat 9 at this time, it can be known that the small flow valve seat 9 is subjected to the downward pressure force exerted on it by the valve core 5, and due to the pressure difference between the high-pressure oil above the small flow valve seat 9 (the high-pressure oil passed into the valve inlet 7.1) and the low-pressure oil below the small flow valve seat 9 (the low-pressure oil passed into the valve outlet 13), the small flow valve seat 9 is also subjected to the downward pressure difference force brought about by the pressure difference. Furthermore, the small flow valve is also subjected to the upward second elastic force transmitted by the second elastic member 10. At this time, the sum of the pressure force and the pressure difference force is greater than the second elastic force. Therefore, the small flow valve seat 9 moves downward, thereby causing the second closing portion 9.2 to close the large flow port 15 of the large flow valve seat 12.

[0108] Further, at this time, the force analysis of the large flow valve seat 12 shows that the large flow valve seat 12 is subjected to the downward 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 on the periphery of the large flow valve seat 12 abuts against the limit baffle 8, the limit baffle 8 and the valve housing 7 have an interference fit, and the upper surface of the limit baffle 8 contacts the sink surface of the valve housing 7. At this time, the large flow switching solenoid valve 1 is in a closed state.

[0109] In the above case, the electromagnetic force F1 generated by the magnetic field is greater than the sum of the first elastic force F2 and the second elastic force F3, that is, .

[0110] At this time, the liquid pressure P1 at the valve inlet 7.1 is ≥ the liquid pressure P2 at the valve outlet 13, and F4 is the pressure difference force on the lower end of the small flow valve seat 9. At this time, the force on the small flow valve seat 9 is , vertically downward. Since F1, F2, and F3 are all fixed values, and due to the existence of the valve port 7.2, the force on the small flow valve seat 9 is only related to the sealing circle area of ​​its large flow port 15, so when F4 is larger, the force on the small flow valve seat 9 is greater, the contact with the large flow valve seat 12 is tighter, and the sealing effect is better.

[0111] like Fig.10 As shown, the pressure difference force on the small flow valve seat 9 is ,in, Liquid pressure P1 at valve inlet 7.1 - liquid pressure P2 at valve outlet 13; , where S1 is the sealing circle area of ​​the large flow port 15.

[0112] (3) If Figure 8 As shown, when the electromagnetic coil 2 is energized, low-pressure oil is passed into the valve inlet 7.1, and high-pressure oil is passed into the valve outlet 13: under this working condition, if the electromagnetic coil 2 is energized, the valve housing 7 generates magnetic force, the moving iron 4 is subjected to the downward electromagnetic force exerted on it by the valve housing 7, and the moving iron 4 transmits the downward electromagnetic force to the valve core 5 connected thereto. At this time, a force analysis of the valve core 5 shows that the valve core 5 is subjected to the downward electromagnetic force transmitted by the valve housing 7 through the moving iron 4, and the valve core 5 is also subjected to the upward first elastic force exerted on it by the first elastic member 6. It can be understood that since the electromagnetic force is greater than the first elastic force, the valve core 5 moves downward and approaches the small flow valve seat 9, thereby causing the first closing portion to close the small flow port 14 of the small flow valve seat 9.

[0113] While delivering high-pressure oil to the valve outlet 13, the high-pressure oil will enter the oil pressure space and flow to the sealing ring 11 through the second oil-passing groove 12.2. At this time, since the low-pressure oil above the sealing ring 11 is introduced from the valve inlet 7.1, and the high-pressure oil below the sealing ring 11 is introduced from the second oil-passing groove 12.2, the high-pressure oil will exert an upward pressure differential force on the sealing ring 11 under the pressure difference between the high-pressure oil and the low-pressure oil. At this time, 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 downward second elastic force applied to it by the second elastic member 10, and a downward pressure force applied to it by the small flow valve seat 9. Since the pressure differential force is greater than the downward pressure force and the second elastic force applied to it by the small flow valve seat 9, the large flow valve seat 12 is pushed to move upward, that is, to move in the direction of the small flow valve seat 9, pushing the small flow valve seat 9 to move upward until the small flow valve seat 9 abuts against the valve seat limiter 7.3, the large flow valve seat 12 and the small flow valve seat 9 no longer move, and the large flow port 15 is still closed. However, due to the electromagnetic force, the valve core 5 is still in contact with the small flow valve seat 9 at this time, and the small flow port 14 is still closed.

[0114] It can be understood that, in the above situation, the electromagnetic coil 2 is energized to generate a magnetic field, the small flow valve port and the large flow valve port are both closed, and the electromagnetic valve is in a completely closed and sealed state. When the pressure at the valve outlet 13 gradually rises, the force of the liquid pressure P2 at the valve outlet 13 acting on the large flow valve seat 12 (that is, the pressure difference force F5 on the large flow valve seat 12) is greater than the electromagnetic force and the friction force of the sealing ring 11 at the large flow valve seat 12, the large flow valve seat 12 is lifted up and pushes the small flow valve seat 9 upward. When the small flow valve seat 9 stops at the valve seat limit portion 7.3, the small flow valve seat 9 and the large flow valve seat 12 both stop moving.

[0115] like Fig.11 As shown, the pressure difference force on the entire large flow valve seat 12 is ,in, Liquid pressure P1 at valve outlet 13 - liquid pressure P2 at valve inlet 7.1; , where S2 is the sealing line area of ​​the sealing ring 11.

[0116] When the liquid pressure at the valve outlet 13 continues to rise, the small flow valve seat 9 and the large flow valve seat 12 are limited. The key point of the liquid pressure at this time is that the valve core 5 is still subjected to force. At this time, the valve core 5 is subjected to the electromagnetic force F1, the first elastic force F2 and the pressure difference force F6. The force formula is: At this time, F6 is related to the sealing circle area of ​​the first closing part of the valve core 5.

[0117] like Fig.12 As shown, ,in, Liquid pressure P1 at valve outlet 13 - liquid pressure P2 at valve inlet 7.1; , where S3 is the sealing circle area of ​​the first closing part of the valve core 5.

[0118] Since the valve port sealing line of the first closing portion is small enough (usually between 0.4-0.5 mm, or even smaller), the F6 value is small, so that the valve core 5 does not move upward, the small flow port 14 is still closed, and then the solenoid valve is still in a closed and sealed state.

[0119] (4) If Figure 6 and 8 As shown, when the electromagnetic coil 2 changes from being energized to being de-energized in case (3): the electromagnetic valve coil is controlled to be de-energized, and the valve core 5 pushes the moving iron 4 upward under the upward elastic force of the first elastic member 6, and the small flow port 14 of the small flow valve seat 9 is opened. If there is liquid pressure at the valve outlet 13 at this time, the liquid flows through the large flow port 15 and the small flow port 14 in sequence and enters the first space, and finally flows out to the outside of the valve housing 7 through the valve port 7.2 on the first space. It can be understood that in this process, the high pressure at the valve outlet 13 will gradually decrease. When the pressure at the valve outlet 13 and the pressure at the valve inlet 7.1 tend to a certain difference, that is, when the pressure difference is less than the elastic force applied by the second elastic member 10, the large flow valve seat 12 moves downward under the elastic force of the second elastic member 10 until it is limited by the limit baffle 8, and the large flow port 15 is opened.

[0120] Furthermore, when a large flow rate switching solenoid valve is used in the hydraulic control unit 16, the first space and the second space are connected through the valve inlet 7.1 and the valve port 7.2 to achieve pressure balance.

[0121] It should be pointed out that when a large flow switching solenoid valve is applied to the hydraulic control unit 16, a closed space is formed outside the valve inlet 7.1 and the valve port 7.2, and the first space and the second space can be connected by the valve inlet 7.1 and the valve port 7.2 in the closed space to achieve pressure balance.

[0122] It can be understood that when the electromagnetic coil 2 changes from being energized to being de-energized in situation (2), that is, if there is no liquid pressure at the valve outlet 13, the large flow valve seat 12 moves directly downward under the elastic force of the second elastic member 10 until it is limited by the limit baffle 8, and the large flow port 15 is opened.

[0123] like Fig.13As shown, the hydraulic control unit 16 of the automobile brake system according to the second embodiment of the present invention includes the large flow switching solenoid valve 1 according to the first embodiment of the present invention. The hydraulic control unit 16 also includes a pressure control module 17, and the large flow switching solenoid valve 1 is installed in the pressure control module 17.

[0124] Furthermore, the large flow switching solenoid valve 1 of the present invention is used together with the electromagnetic coil 2, and the power 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 status and the control logic burned in advance. After the pin is powered on, the coil forms a magnetic field inside due to electromagnetic induction. The moving iron 4 inside the solenoid valve approaches the valve housing 7 under the action of the magnetic field, pushes the valve core 5, compresses the first elastic member 6, and makes the valve core 5 fit with the small flow valve seat 9 to close the small flow port 14. The valve core 5 is continuously pushed, compressing the second elastic member 10, so that the small flow valve seat 9 fits with the large flow valve seat 12 and closes the large flow port 15, so that the solenoid valve is completely closed and sealed.

[0125] After the electromagnetic coil 2 is powered off, the magnetic field disappears, and the valve core 5 inside the electromagnetic valve moves upward under the action of the first elastic member 6 and pushes the movable iron 4 to reset, opening the small flow port 14. The internal small flow valve seat 9 moves upward to the valve seat limit portion 7.3 under the action of the second elastic member 10, opening the large flow port 15.

[0126] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the embodiment of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of the different embodiments or examples, without contradiction.

[0127] 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 normally open large flow switching solenoid valve, characterized in that: It includes electromagnetic coil, valve housing, moving iron, valve core, small flow valve seat and large flow valve seat; The valve housing is internally formed with a receiving space penetrating the upper and lower ends thereof, the valve core, the small flow valve seat and the large flow valve seat are sequentially arranged in the receiving space from top to bottom, the upper end of the valve core is connected to the moving iron and the electromagnetic coil is arranged around the moving iron and the valve housing, a first elastic member is arranged between the valve core and the small flow valve seat, the small flow valve seat is connected to the large flow valve seat via a second elastic member, and the small flow valve seat and the valve core are both slidably arranged along the central axis direction of the receiving space; The lower end of the valve core is provided with a first closing portion for closing or opening the small flow port of the small flow valve seat, and the lower end of the small flow valve seat is provided with a second closing portion for closing or opening the large flow port of the large flow valve seat, and the small flow port, the large flow port and the valve outlet formed at the lower end of the accommodating space are connected in sequence; When the electromagnetic coil is powered off, the valve core opens the small flow port, and the small flow valve seat opens the large flow port, so that the large flow switching electromagnetic valve is opened with a large flow; when the electromagnetic coil is powered on, the valve core closes the small flow port, and the small flow valve seat closes the large flow port, so that the large flow switching electromagnetic valve is closed.

2. The normally open large flow switching solenoid valve according to claim 1 is characterized in that: A valve seat limiting portion is also provided in the accommodating space, the valve seat limiting portion is located between the valve core and the small flow valve seat, and the valve seat limiting portion divides the accommodating space into a first space located on the upper side thereof and a second space located on the lower side thereof, and the first space and the second space are connected through a through hole located at the center of the valve seat limiting portion; The small flow valve seat passes through the through hole and enters the second space, and the upper surface of the valve seat limiting portion abuts against the lower end of the first elastic member, and the lower surface of the valve seat limiting portion abuts against the limiting boss of the small flow valve seat.

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

4. The normally open large flow switching solenoid valve according to claim 2 is characterized in that: The valve housing is provided with a valve inlet and a valve port, the valve port is connected to the first space, and the valve inlet is connected to the second space; when the large flow switching solenoid valve is used in a hydraulic control unit, the first space and the second space are connected through the valve inlet and the valve port to achieve pressure balance; And when the electromagnetic coil is powered off, the valve port is connected to the valve outlet through the first space, the small flow port and the large flow port in sequence, and the valve inlet is connected to the valve outlet through the second space and the large flow port in sequence; a sealing ring is fixedly sleeved on the outer periphery of the large flow valve seat and abuts against the inner wall of the second space.

5. The normally open large flow switching solenoid valve according to claim 4 is 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 energized and high-pressure oil is passed to the valve outlet and low-pressure oil is passed to the valve inlet, the high-pressure oil enters the oil pressure space to push the large-flow valve seat to slide toward the small-flow valve seat. At this time, the valve core closes the small-flow port, the small-flow valve seat closes the large-flow port, and the limiting boss of the small-flow valve seat abuts against the valve seat limiting portion.

6. The normally open 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 normally open 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 energized, the downward electromagnetic force is greater than the sum of the upward first spring force and the second spring force, the movable iron presses the first closing portion of the valve core onto the small flow valve seat, and the second closing portion of the small flow valve seat onto the large flow valve seat, at which time the first spring and the second spring are both in a compressed state; When the electromagnetic coil is powered off, the first spring pushes the valve core away from the small flow valve seat by elastic force, and the second spring pushes the small flow valve seat away from the large flow valve seat by elastic force.

8. The normally open 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 normally open large flow switching solenoid valve according to any one of claims 1 to 6, characterized in that: The second sealing portion is a sealing spherical arc surface formed at the bottom of the small flow valve seat, and a large valve port sealing conical surface matching the sealing arc surface is formed at the large flow port.

10. A hydraulic control unit for an automobile braking system, characterized in that: It comprises a normally open 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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