A pressure boost valve and pressure boost module for a brake system

Abstract

The application relates to a pressure boosting valve and a pressure boosting module for a brake system, which comprises a valve body internally provided with a first oil channel, a first oil cavity and a second oil channel connected in sequence, the first oil channel and the second oil channel are external oil ports of the valve body, the first oil channel serves as an oil outlet, the second oil channel serves as an oil inlet, the second oil channel is internally provided with a throttle hole, and the throttle hole is a dumbbell-shaped through hole with large ends and a small middle part. By adopting the scheme, the second oil channel is provided with the oil inlet, the first oil channel is provided with the oil outlet, and the throttle hole is arranged in the second oil channel, the dumbbell-shaped throttle hole has a structure that the two ends are large, the middle part is suddenly changed and reduced in section, the throttle hole has a good throttling effect on the hydraulic oil flowing through the second oil channel, that is, the throttle hole has a throttling effect on the hydraulic oil at the oil inlet of the pressure boosting valve, and the pressure boosting valve is convenient for accurate control of pressure and flow.

Description

Technical Field

[0001] This invention relates to the field of booster valves, and in particular to a booster valve and booster module for a braking system. Background Technology

[0002] Depending on the intended use, a booster valve is required in the braking system. However, existing booster valves have poor throttling effect when no power is applied, making it difficult to meet the usage requirements of the braking system. Structures that can meet the requirements of the braking system often have problems such as high complexity of the valve's internal structure. Summary of the Invention

[0003] This invention addresses the problem of poor throttling effect of existing booster valves when no power is applied, and provides a booster valve and booster module with good throttling effect for use in braking systems.

[0004] The technical solution of the present invention to solve the above-mentioned technical problems is as follows: A booster valve for a braking system includes a valve body having a first oil passage, a first oil chamber and a second oil passage connected in sequence inside. The first oil passage and the second oil passage are external oil ports of the valve body. The first oil passage serves as an oil outlet and the second oil passage serves as an oil inlet. A throttling orifice is provided in the second oil passage. The throttling orifice is a dumbbell-shaped through hole that is large at both ends and small in the middle.

[0005] The beneficial effects of this invention are as follows: This application sets up a second oil passage for oil inlet and a first oil passage for oil outlet, and sets a throttling orifice in the second oil passage. The dumbbell-shaped throttling orifice has a structure with large ends and a sudden change in cross-section in the middle, so that the throttling orifice can play a better throttling effect on the hydraulic oil flowing through the second oil passage; that is, the throttling orifice can play a throttling effect on the hydraulic oil at the oil inlet of the booster valve, which facilitates the booster valve to accurately control the pressure and flow.

[0006] Based on the above technical solution, the present invention can be further improved as follows.

[0007] Furthermore, the valve body is provided with a movable valve stem, and an oil guide hole is provided between the first oil chamber and the second oil passage. One end of the valve stem extends into the first oil chamber and can block or open the oil guide hole, while the other end of the valve stem abuts against a movable clamping member.

[0008] The beneficial effect of adopting the above-mentioned further solution is that the oil guide hole is blocked by the valve stem to separate the cavities on both sides of the oil guide hole, and the opening of the oil guide hole can also be controlled to control the flow rate of hydraulic oil at the oil guide hole.

[0009] Furthermore, the valve body is provided with a stepped hole for placing the valve stem. One end of an elastic element in a compressed state is abutted on the end face of the stepped hole, and the other end of the elastic element presses the valve stem against the clamping element.

[0010] The beneficial effect of adopting the above-mentioned further solution is that the valve stem and valve body are respectively abutted at both ends of the elastic element, which is used to press the valve stem and the clamping element together, so that the self-test valve is kept in the normally open state, that is, the corresponding oil guide hole is in the open state.

[0011] Furthermore, the valve stem is elongated and has multiple first flow stabilizing grooves at one end near the clamping member, and the first flow stabilizing grooves are arranged axially; at least one pair of second flow stabilizing grooves are symmetrically formed on the outer wall of the clamping member.

[0012] The beneficial effect of adopting the above-mentioned further solution is that it stabilizes the flow of the incoming hydraulic oil.

[0013] Furthermore, both the clamping element and the valve body are magnetically conductive, and the outer periphery of the clamping element and the valve body is surrounded by energized coil windings.

[0014] The beneficial effect of adopting the above-mentioned further solution is that both the clamping element and the valve body are magnetic. When the coil winding is energized, a magnetic force will be generated to attract each other, thereby causing the clamping element to move toward the valve body and press down the valve stem. The magnitude of the magnetic field can be controlled by controlling the magnitude of the current, thereby controlling the downward pressing distance of the valve stem, that is, controlling the opening size of the oil guide hole; the clamping element can be an armature.

[0015] Furthermore, a magnetic shielding sleeve is provided inside the coil winding. The magnetic shielding sleeve is fixed to the side wall of the valve body and forms a receiving cavity at the end of the valve body. The clamping member is movably disposed in the receiving cavity.

[0016] The beneficial effect of adopting the above-mentioned further solution is that the clamping component is located inside the magnetic shielding sleeve, which serves to isolate the magnetic field. At the same time, the receiving cavity formed by the magnetic shielding sleeve serves as a limiting cavity for the movement of the clamping component.

[0017] Furthermore, the coil winding is wound around a ring-shaped and perforated coil frame, which is an insulating plastic component.

[0018] The beneficial effect of adopting the above-mentioned further solution is that the coil frame serves as the carrier of the coil winding, allowing the coil winding to be wound on the coil frame, which facilitates the winding of the coil and the adjustment of the density.

[0019] Furthermore, the oil guide hole is divided into a circular hole, a first conical hole, and a second conical hole with progressively increasing diameters along the axial direction; the circular hole is connected to the second oil passage, and the second conical hole is connected to the first oil cavity; the oil guide hole is located on the first valve seat, and the throttling hole is located on the second valve seat. The first valve seat has a thin-walled structure, and the second valve seat abuts against the first valve seat and presses it through the second oil passage.

[0020] The beneficial effects of adopting the above-mentioned further scheme are that two conical holes are set. The first conical hole with a small angle to the axial direction is used for linear pressure and flow control, and the second conical hole with a large angle to the axial direction is used for large opening and large flow control. The circular hole is used for throttling, and the size and length of the circular hole determine the throttling parameters. The oil guide hole and the throttling hole are both set in the second oil passage of the booster valve, which has a strong throttling effect on the hydraulic oil at the oil inlet of the booster valve and facilitates the booster valve to accurately control the pressure and flow.

[0021] Furthermore, an annular filter screen is fixed outside the valve body, and the annular filter screen covers the port of the first oil passage.

[0022] The beneficial effect of adopting the above-mentioned further solution is that an annular filter screen is installed at the location of the first oil passage. The annular filter screen surrounds the valve body, which can isolate large pieces of contaminants in the lateral flow channel and prevent large pieces of contaminants in the lateral flow channel from entering the internal working chamber of the solenoid valve.

[0023] Another technical solution of the present invention to solve the above-mentioned technical problems is as follows: a booster module, including the booster valve for the braking system, a first oil passage connected to a pressure reducing valve, and a second oil passage connected to an oil reservoir; the booster valve is a normally open valve, and the pressure reducing valve is a normally closed valve. Attached Figure Description

[0024] Figure 1 This is a cross-sectional view of an embodiment of the booster valve for a braking system according to the present invention;

[0025] Figure 2 This is a partial cross-sectional view in the second direction of an embodiment of the present invention;

[0026] Figure 3 This is a structural diagram of the valve stem of the present invention;

[0027] Figure 4 This is a structural diagram of the first valve seat of the present invention;

[0028] Figure 5 This is a structural diagram of the clamping component of the present invention.

[0029] The attached diagram lists the components represented by each number as follows:

[0030] 1 Valve body; 1-1 First oil passage; 1-2 Second oil passage; 1-3 First oil chamber; 1-4 Stepped orifice;

[0031] 2. Valve stem; 2-1 First flow stabilizer groove; 2-2 Exhaust port;

[0032] 3. Clamping component; 3-1. Second flow stabilizer;

[0033] 4. First valve seat; 4-1 Oil guide hole; 4-2 Round hole; 4-3 First conical hole; 4-4 Second conical hole;

[0034] 5. Second valve seat; 5-1 Throttling orifice; 5-2 Third conical orifice;

[0035] 6. Elastic element; 7. Coil winding; 8. Magnetic shielding sleeve; 9. Coil frame; 10. Annular filter screen;

[0036] 11 Shock-absorbing pad; 12 Valve ball; 13 Valve cover; 14 Coil housing; 15 Coil lower yoke; 16 Coil body; 17 Weld. Detailed Implementation

[0037] The principles and features of the present invention are described below. The examples given are only for explaining the present invention and are not intended to limit the scope of the present invention.

[0038] Example 1

[0039] like Figures 1 to 2 A booster valve for a braking system includes a valve body 1 having a first oil passage 1-1, a first oil chamber 1-3, and a second oil passage 1-2 connected in sequence inside. The first oil passage 1-1 and the second oil passage 1-2 are external oil ports of the valve body 1. The first oil passage 1-1 serves as an oil outlet, and the second oil passage 1-2 serves as an oil inlet. The second oil passage 1-2 has a throttling orifice 5-1, which is a dumbbell-shaped through hole that is large at both ends and small in the middle.

[0040] The beneficial effects of this embodiment are as follows: This application sets up a second oil passage 1-2 for oil inlet and a first oil passage 1-1 for oil outlet, and sets a throttling orifice 5-1 in the second oil passage 1-2. The dumbbell-shaped throttling orifice 5-1 has a structure that is large at both ends and abruptly decreases in cross-section in the middle, so that the throttling orifice 5-1 has a better throttling effect on the hydraulic oil flowing through the second oil passage 1-2; that is, the throttling orifice 5-1 has a throttling effect on the hydraulic oil at the oil inlet of the booster valve, which facilitates the booster valve to accurately control the pressure and flow.

[0041] Example 2

[0042] Preferably, based on embodiment 1, the valve body 1 is provided with a movable valve stem 2, and an oil guide hole 4-1 is provided between the first oil chamber 1-3 and the second oil passage 1-2. One end of the valve stem 2 extends into the first oil chamber 1-3 and can block or open the oil guide hole 4-1, and the other end of the valve stem 2 abuts against the movable clamping member 3.

[0043] The beneficial effect of adopting the preferred solution in the above embodiments is that the oil guide hole 4-1 is blocked by the valve stem 2 to separate the cavities on both sides of the oil guide hole 4-1, and the opening of the oil guide hole 4-1 can also be controlled to control the flow rate of hydraulic oil at the oil guide hole 4-1.

[0044] Based on the above embodiment, one end of the valve stem 2 is a ball head that can be moved to completely or partially block the oil guide hole 4-1. The end of the ball head of the valve stem 2 is provided with an exhaust hole 2-2, which has a diameter of 0.4 mm and a depth of 0.03 mm. A mold exhaust hole 2-2 is provided at the valve port to ensure the roundness of the high-precision spherical surface.

[0045] like Figure 3 In some embodiments, the valve stem 2 has a tapered structure. The end of the valve stem 2 closest to the clamping member 3 is the large end, and the end of the valve stem 2 with a ball head is the small end. The middle part of the valve stem 2 has a shoulder for abutting against the elastic member 6. The large end of the valve stem 2 always keeps in contact with the clamping member 3 under the action of the elastic member 6. The valve stem 2 can be a high-precision injection molded part made of PEEK material. The large end of the valve stem 2 has a first flow stabilizing groove 2-1 along the axial direction. The ball head of the small end of the valve stem 2 is a high-precision valve port sealing surface. The valve stem 2 made of PEEK material has a small mass and a small moment of inertia, which is beneficial for linear "hovering" stability control and noise control.

[0046] Example 3

[0047] Preferably, based on embodiments 1-2, the valve body 1 is provided with stepped holes 1-4 for placing the valve stem 2. One end of an elastic member 6 in a compressed state is abutted on the end face of the stepped holes 1-4, and the other end of the elastic member 6 presses the valve stem 2 against the clamping member 3.

[0048] The beneficial effect of adopting the preferred solution in the above embodiments is that the two ends of the elastic member 6 are respectively abutted against the valve stem 2 and the valve body 1, which is used to press the valve stem 2 and the clamping member 3 together, so that the self-test valve is kept in the normally open state, that is, the corresponding oil guide hole 4-1 is in the open state.

[0049] Based on the above embodiments, the valve stem 2 has a tapered structure. The end of the valve stem 2 closest to the clamping member 3 is the large end, and the end of the valve stem 2 with a ball head is the small end. The middle part of the valve stem 2 is provided with a shoulder for abutting against the elastic member 6. Under the action of the elastic member 6, the large end of the valve stem 2 always keeps in contact with the clamping member 3. The valve stem 2 can be a high-precision injection molded part made of PEEK material. The large end of the valve stem 2 has a first flow stabilizing groove 2-1- along the axial direction. The ball head of the small end of the valve stem 2 is a high-precision valve port sealing surface. The valve stem 2 made of PEEK material has a small mass and a small moment of inertia, which is beneficial for linear "hovering" stability control and noise control.

[0050] The elastic element 6 can be a structure that is elastic and has a rebound force after compression. A spring is preferred. The spring can be a small-diameter cylindrical compression spring to provide a restoring force when the solenoid valve is opened and closed. In the non-energized state, the pre-pressure of the spring keeps the exhaust port 2-2- of the self-test valve normally open.

[0051] Example 4

[0052] like Figure 5 Preferably, based on embodiments 1-3, the valve stem 2 is elongated and has a plurality of first flow stabilizing grooves 2-1 at one end near the clamping member 3, and the first flow stabilizing grooves 2-1 are arranged along the axial direction; at least one pair of second flow stabilizing grooves 3-1 are symmetrically provided on the outer wall of the clamping member 3.

[0053] The beneficial effect of adopting the preferred solution in the above embodiments is that it stabilizes the flow of the incoming hydraulic oil.

[0054] Based on the above embodiments, the clamping member 3 is a cold-forged part with two second flow-stabilizing grooves 3-1- along the axial direction, which has good magnetic permeability; after the electromagnetic coil is energized, it provides thrust for the valve stem 2 to close, pushing the valve stem 2 to seal with the valve seat or to keep it in a certain position, corresponding to the oil guide hole 4-1- partially opening, so as to output a specific pressure or flow rate.

[0055] Example 5

[0056] Preferably, based on embodiments 1-4, both the clamping member 3 and the valve body 1 are magnetically conductive, and the outer periphery of the clamping member 3 and the valve body 1 is surrounded by an energized coil winding 7.

[0057] The beneficial effect of adopting the preferred solution in the above embodiments is that both the clamping member 3 and the valve body 1 are magnetic. When the coil winding 7 is energized, a magnetic force will be generated to attract each other, thereby causing the clamping member 3 to move toward the valve body 1 and press down the valve stem 2. The magnitude of the magnetic field can be controlled by controlling the magnitude of the current, thereby controlling the downward pressing distance of the valve stem 2, that is, controlling the opening size of the oil guide hole 4-1; the clamping member 3 can be an armature.

[0058] In this embodiment, a coil frame 9 can be provided as a carrier for the coil winding 7, allowing the coil winding 7 to be wound on the coil frame 9, facilitating coil winding and density adjustment. The coil frame 9 can be an insulating plastic part injection molded from PA66+30GF or PBT material. The coil winding 7 can be a helical coil wound on the coil frame 9 with enameled wire at 220°C, with a wire diameter of 0.25mm, 552 turns, 12 layers, and a resistance value of 7.3±0.2Ω.

[0059] Example 6

[0060] Preferably, based on embodiments 1-5, a magnetic shielding sleeve 8 is provided inside the coil winding 7. The magnetic shielding sleeve 8 is fixed to the side wall of the valve body 1 and forms a receiving cavity at the end of the valve body 1. The clamping member 3 is movably disposed in the receiving cavity.

[0061] The beneficial effect of adopting the preferred solution in the above embodiments is that the clamping member 3 is provided inside the magnetic shielding sleeve 8, the magnetic shielding sleeve 8 plays the role of isolating the magnetic field, and at the same time, the receiving cavity formed by the magnetic shielding sleeve 8 serves as a limiting cavity for the movement of the clamping member 3.

[0062] Based on this embodiment, the magnetic shielding sleeve 8 is a precision stamped part made of stainless and non-magnetic material. After being connected to the valve body 1 by laser welding seam 1717, it forms a receiving cavity, which serves as the upper cavity of the hydraulic working chamber of the self-test valve. The coil winding 7 is surrounded by a coil housing 14 and a lower coil yoke 15, which are connected. The coil housing 14 extends to the magnetic shielding sleeve 8. The yoke of the coil housing 14 is a high-permeability part made of soft magnetic material through stretching and stamping, serving as the main path for the closed loop of external magnetic lines of force generated by the coil winding 7. The upper plane and inner flange of the coil housing 14 constitute the upper coil yoke. The coil housing 14 and the magnetic shielding sleeve 8 are fitted with a small clearance. The lower part of the coil housing 14 is press-fitted with the lower coil yoke 15 to minimize magnetic leakage. The lower coil yoke 15 is made of a soft magnetic material with high permeability, enabling the coil winding 7 to generate a closed loop of magnetic lines of force at the bottom of the coil. The upper end face of the lower coil yoke 15 is flush with the lower end face of the coil frame 9, and the outer circular surface of the lower coil yoke 15 is press-fitted with the inner circular surface of the coil housing 14. The magnetic shielding sleeve 8 is connected to the valve body 1 via laser welding weld 17 to form the upper chamber of the hydraulic working chamber of the self-test valve.

[0063] Example 7

[0064] Preferably, based on embodiments 1-6, the coil winding 7 is wound on a ring-shaped and perforated coil frame 9, and the coil frame 9 is an insulating plastic part.

[0065] The beneficial effect of adopting the preferred solution in the above embodiments is that the coil frame 9 serves as the carrier of the coil winding 7, so that the coil winding 7 is wound on the coil frame 9, which facilitates the winding of the coil and the adjustment of the density.

[0066] In this embodiment, a rubber damping pad 11 is fixed to the outside of the coil winding 7 and the magnetic shielding sleeve 8. The coil winding 7 is connected to the coil body 16, and the coil body 16 passes through the damping pad 11. The damping pad 11 provides vibration damping and protects the coil body 16. The damping pad 11 is made of EPDM material vulcanized into vibration-damping rubber. The damping pad 11 provides preload for the coil when mounted on the solenoid valve and attenuates vibrations during coil and solenoid valve engagement and disengagement, thereby protecting the coil body 16, the PI N, and the crimped conductive structure of the ECU PCB board, and improving durability.

[0067] The coil body 16 can be a solid press-fit structure, which is the lead connecting the coil winding 7 and the ECU PCB board. It is connected to the ECU PCB board through a press-fit structure. The ECU PCB board provides voltage or current control signals to the coil winding 7 through the coil body 16.

[0068] Example 8

[0069] like Figure 4Preferably, based on embodiments 1-7, the oil guide hole 4-1 is divided along the axial direction into a circular hole 4-2, a first conical hole 4-3, and a second conical hole 4-4, which are connected in sequence with increasing diameters; the circular hole 4-2 is connected to the second oil passage 1-2, and the second conical hole 4-4 is connected to the first oil cavity 1-3; the oil guide hole 4-1 is provided on the first valve seat 4, and the throttling hole 5-1 is provided on the second valve seat 5. The first valve seat 4 has a thin-walled structure, and the second valve seat 5 abuts against the first valve seat 4 and presses it tightly in the second oil passage 1-2.

[0070] The beneficial effects of the preferred scheme in the above embodiments are that two conical holes are provided. The first conical hole 4-3 with a small angle to the axial direction is used for linear pressure and flow control, and the second conical hole 4-4 with a large angle to the axial direction is used for large opening and large flow control. The circular hole 4-2 is used for throttling, and the size and length of the circular hole 4-2 determine the throttling parameters. The oil guide hole 4-1 and the throttling hole 5-1 are both located in the second oil passage 1-2 of the booster valve, which has a strong throttling effect on the hydraulic oil at the oil inlet of the booster valve, and facilitates the precise control of pressure and flow by the booster valve.

[0071] Based on this embodiment, the first valve seat 4 can be a high-precision thin-walled precision stretching part, and the two conical surfaces of the valve port are two inner conical surfaces that are connected to each other, and the inner conical surfaces are ground.

[0072] In some embodiments, the second valve seat 5 is located at the end of the first valve seat 4 facing away from the valve stem 2. The second valve seat 5 has a third conical hole 5-2, the two ends of which are connected to the first oil chamber 1-3 and the second oil passage 1-2, respectively. The smaller end of the third conical hole 5-2 is connected to the first oil chamber 1-3, and the larger end of the third conical hole 5-2 is connected to the second oil passage 1-2 and is equipped with a valve ball 12 to form a unidirectional conduction structure. The third conical hole 5-2 and the valve ball 12 form a structure that conducts in the forward direction and blocks in the reverse direction.

[0073] The second valve seat 5 can be a one-piece plastic part formed by bonding an annular filter screen 10 to a one-way valve plastic seat body. The upper positioning surface of the second valve seat 5 is fitted with the lower end of the valve body 1; the upper sealing post of the second valve seat 5 is interference-fitted with the inner circular surface of the first valve seat 4. The diameter of the valve ball 12 can be 1.5mm. The valve ball 12 is made of PEEK material. The PEEK valve ball 12 has small mass and small moment of inertia, and has the advantages of good sealing performance and fast opening and closing response speed. When there is a pressure difference between the two ends of the valve ball 12, it will push the valve ball 12 to move, so that the valve ball 12 is fitted or separated from the third conical hole 5-2, thereby corresponding to the open and closed states of the valve ball 12 and the third conical hole 5-2. In addition, the diameter of the valve ball 12 can be 1.5mm, and the through diameter of the third conical hole 5-2 can be 0.81mm.

[0074] Example 9

[0075] Preferably, based on embodiments 1-8, an annular filter 10 is fixed to the outside of the valve body 1, and the annular filter 10 covers the port of the first oil passage 1-1.

[0076] The beneficial effect of adopting the preferred solution in the above embodiments is that an annular filter 10 is set at the location of the first oil passage 1-1. The annular filter 10 surrounds the valve body 1, which can isolate large lateral flow channel contaminants and prevent large lateral flow channel contaminants from entering the internal working chamber of the solenoid valve.

[0077] Example 10

[0078] Based on embodiments 1-9, another technical solution of the present invention to solve the above-mentioned technical problems is as follows: a booster module, including the booster valve for the braking system, a first oil passage 1-1 connected to a pressure reducing valve, and a second oil passage 1-2 connected to an oil reservoir; the booster valve is a normally open valve, and the pressure reducing valve is a normally closed valve.

[0079] In some embodiments, the booster valve in the booster module can be connected to a servo pressure-building unit. A detachable valve cover 13 is connected to the end of the second valve seat 5 facing away from the valve body 1, and a filter screen is fixed on the valve cover 13. The filter screen isolates contaminants, preventing them from entering the internal working chamber of the solenoid valve, thus providing protection. The valve cover 13 can also serve as the lower limit of the one-way valve ball 12. The valve cover 13 can also be an integrated plastic part combined with the lower filter screen, with the inner circumferential surface of the valve cover 13 and the outer circumferential surface of the lower end of the valve seat connected by an interference fit. The booster module ensures the booster valve is open when no power is applied, while a normally closed valve refers to a pressure-reducing valve that is closed when no power is applied.

[0080] When the booster valve of this application is used in conjunction with the OV valve and the pressure reducing valve, the upper chamber of the OV valve can be connected to the first oil passage 1-1, and the lower chamber of the OV valve can be connected to the oil reservoir. The booster valve of this application, as a normally open linear control solenoid valve, has the following three connection methods:

[0081] (1) Neither the booster valve nor the OV valve is energized. The booster valve is normally open, and the OV valve is normally closed, working together to achieve the wheel cylinder boosting function: the pressure from the servo pressure building unit PSU flows into the wheel cylinder through the PSV valve, from the bottom port of the booster valve to the side port. Brake fluid flows from the bottom to the side of the booster valve. When the IV is energized using continuous variable duty cycle control, linear boosting control can be achieved in the "hover" state.

[0082] (2) The pressure-maintaining function is achieved by the pressure-boosting valve closing when energized and the OV valve remaining normally closed when de-energized: After the pressure-boosting valve closes when energized, the pressure of the servo pressure-building unit PSU is cut off by the pressure-boosting valve, and the pressure in the wheel cylinder remains unchanged. The brake fluid is not connected and does not flow at both ends of the pressure-boosting valve.

[0083] (3) The pressure reduction function is achieved by the energization and closure of the booster valve and the energization and opening of the OV valve: After the booster valve is energized and closed, the pressure of the servo pressure building unit PSU is isolated by the booster valve. At the same time, the OV valve opens, the brake fluid in the wheel cylinder flows back to the reservoir, and the pressure in the wheel cylinder decreases.

[0084] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0085] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0086] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0087] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0088] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0089] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A pressure boosting valve for a braking system, characterized in that, The valve body (1) includes a first oil passage (1-1), a first oil chamber (1-3), and a second oil passage (1-2) connected in sequence inside. The first oil passage (1-1) and the second oil passage (1-2) are the external oil ports of the valve body (1). The first oil passage (1-1) serves as the oil outlet, and the second oil passage (1-2) serves as the oil inlet. A throttling orifice (5-1) is provided in the second oil passage (1-2), which is a dumbbell-shaped through hole that is large at both ends and small in the middle. A movable valve stem (2) is provided inside the valve body (1). An oil guide hole (4-1) is provided between the first oil chamber (1-3) and the second oil passage (1-2). One end of the valve stem (2) extends into the first oil chamber (1-3) and can... The oil guide hole (4-1) is blocked or opened, and the other end of the valve stem (2) abuts against the movable clamping member (3); the oil guide hole (4-1) is divided into a circular hole (4-2), a first conical hole (4-3), and a second conical hole (4-4) with increasing diameters along the axial direction; the circular hole (4-2) is connected to the second oil passage (1-2), and the second conical hole (4-4) is connected to the first oil chamber (1-3); the oil guide hole (4-1) is provided on the first valve seat (4), and the throttling hole (5-1) is provided on the second valve seat (5). The first valve seat (4) has a thin-walled structure, and the second valve seat (5) abuts against the first valve seat (4) and presses it into the second oil passage (1-2).

2. A pressure boosting valve for a braking system according to claim 1, characterized in that, The valve body (1) is provided with a stepped hole (1-4) for placing the valve stem (2). One end of an elastic element (6) in a compressed state is abutted on the end face of the stepped hole (1-4). The other end of the elastic element (6) presses the valve stem (2) against the clamping element (3).

3. A pressure boosting valve for a braking system according to claim 2, characterized in that, The valve stem (2) is long and has a plurality of first flow stabilizing grooves (2-1) at one end near the clamping member (3), and the first flow stabilizing grooves (2-1) are arranged along the axial direction; at least one pair of second flow stabilizing grooves (3-1) are symmetrically provided on the outer wall of the clamping member (3).

4. A pressure boosting valve for a braking system according to claim 1, characterized in that, Both the clamping member (3) and the valve body (1) are magnetically conductive, and the outer periphery of the clamping member (3) and the valve body (1) is surrounded by an energized coil winding (7).

5. A pressure boosting valve for a braking system according to claim 4, characterized in that, The inner side of the coil winding (7) is provided with a magnetic shielding sleeve (8), which is fixed to the side wall of the valve body (1) and forms a receiving cavity at the end of the valve body (1). The clamping member (3) is movably disposed in the receiving cavity.

6. A pressure boosting valve for a braking system according to claim 4, characterized in that, The coil winding (7) is wound around a ring-shaped and perforated coil frame (9), which is an insulating plastic part.

7. A pressure boosting valve for a braking system according to any one of claims 1-6, characterized in that, An annular filter screen (10) is fixed to the outside of the valve body (1), and the annular filter screen (10) covers the port of the first oil passage (1-1).

8. A booster module, characterized in that, The pressure boosting valve for a braking system as described in any one of claims 1-7 is provided, wherein the first oil passage (1-1) is connected to a pressure reducing valve, and the second oil passage (1-2) is connected to an oil reservoir; the pressure boosting valve is a normally open valve, and the pressure reducing valve is a normally closed valve.

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