Balancing structure of a brake valve

Abstract

The application provides a balance structure of a brake valve and belongs to the technical field of brake valves. The balance structure of the brake valve solves the technical problem of short service life of the existing brake valve. In the balance structure of the brake valve, the balance structure comprises a pressure relief flow channel and a one-way assembly, the outer circumferential surface of a balance piston is provided with an oil passing port in communication with the pressure relief flow channel, a movable rod penetrating through the balance piston is slidably connected to the balance piston, one end of the movable rod is located in the pressure relief flow channel, the other end of the movable rod or the middle section of the movable rod is always provided with a sealing ring capable of being sealingly matched with the balance piston in the circumferential direction, the sealing ring is provided with an annular boss protruding towards the position of the other end of the movable rod in the axial direction, the annular boss is arranged around the outer periphery of the movable rod, the edge of the annular boss is provided with a small-diameter necking, the necking is sealingly matched with the movable rod in the circumferential direction, and the movable rod can slide towards the one-way assembly in the axial direction relative to the annular boss and top the one-way assembly. The brake valve has a longer service life.

Description

Technical Field

[0001] The invention belongs to the technical field of brake valves and relates to a balancing structure of a brake valve. Background Art

[0002] Automobile brake valves are divided into pneumatic brake valves and hydraulic brake valves. The proper functioning of brake valves is crucial for vehicle braking, providing technical support for smooth braking. The development of this technology is of vital importance to both automobile manufacturing and road traffic safety.

[0003] For example, Chinese patent application number CN200920306571.2 discloses a fully hydraulic brake valve, which includes a valve member with an inner cavity, an oil inlet port connected to the oil tank, and a working oil port connected to the brake. A piston assembly that controls the flow of oil and a linkage piston connected to the brake pedal are installed within the valve member. When the driver depresses the brake pedal, the linkage piston drives the piston assembly to achieve braking. To make braking easier and ensure sufficient braking force, a brake valve with power assist is designed. This valve is typically equipped with a pressurizing mechanism that pressurizes the working area during braking and relieves the pressure after braking.

[0004] Existing brake valves require valve control for pressurization and depressurization. This switching between states can easily lead to wear and tear of associated components, shortening their service life. To address this, those skilled in the art would likely consider: 1. Improving the strength and wear resistance of associated components to extend their service life; 2. Simplifying the structure of associated components to reduce positional deviation during movement. Summary of the Invention

[0005] The present invention aims to solve the above-mentioned problems existing in the prior art and provides a balancing structure for a brake valve. The technical problem to be solved by the present invention is that the existing brake valve has a short service life.

[0006] The purpose of the present invention can be achieved through the following technical solutions:

[0007] A balancing structure of a brake valve, the brake valve includes a valve body with an oil inlet hole, and a main piston and a balancing piston are arranged in the valve body, which are in contact with each other, and the characteristic is that the balancing structure includes a pressure relief channel located in the balancing piston and a one-way component located between the main piston and the balancing piston and blocking the communication between the pressure relief channel and the oil inlet hole, the outer peripheral surface of the balancing piston has an oil passage port connected to the pressure relief channel, a movable rod is slidably connected to the balancing piston and passes through the balancing piston, one end of the movable rod is located in the pressure relief channel, the outer periphery of the other end of the movable rod or the outer periphery of the middle section of the movable rod is always sleeved with a sealing ring that can be sealed with the balancing piston along the circumferential direction, the sealing ring has an annular boss protruding axially toward the position of the other end of the movable rod, the annular boss is arranged around the outer periphery of the movable rod, the edge of the annular boss has a closing end with a smaller inner diameter, the closing end is sealed with the movable rod along the circumferential direction, and the movable rod can slide axially relative to the annular boss toward the one-way component and push the one-way component open.

[0008] The oil inlet hole can be connected to the oil cup to supply oil to the brake valve. The main piston arranged in the valve body can drive the balance piston to slide under the action of the oil pressure. The balance piston slides under the action of the main piston so that a working chamber can be formed between its end and the inner wall of the valve body. The working chamber is connected with the brake through the working oil hole on the valve body. At the same time, an oil supply chamber separated from the working chamber can be formed between the end face of the main piston and the outer periphery of the balance piston and the inner wall of the valve body. The oil supply chamber can be connected with the working chamber during braking to serve as a supplementary source of hydraulic fluid in the working chamber, which is conducive to ensuring sufficient braking force and balance. After the pressure replenishment is completed, the pressure in the working chamber is built up and the pressure will gradually increase due to the greater reduction ratio of the working chamber volume. At this time, the movable rod is kept in the balancing piston by the action of the limiting component, and one end of the movable rod is always located in the pressure relief channel connected to the oil supply chamber through the oil port and is affected by the oil supply. Under the action of the pressure in the cavity, the other end of the movable rod extends out of the end of the balancing piston into the working cavity and forms a sealing fit between the outer periphery and the sealing ring, so that the movable rod slides toward the one-way component under the action of the pressure difference at both ends and overcomes the preset resistance of the one-way component to trigger the one-way component to open, and the pressure relief channel is connected with the oil inlet hole, so that the oil in the oil supply cavity is discharged so that the balancing piston can continue to slide; the sealing ring is mostly a soft elastic material part, by providing an annular boss protruding axially toward the position of the other end of the movable rod on the sealing ring, and providing the inner edge of the closing on the annular boss to seal with the outer periphery of the movable rod, so that a certain distance is maintained between the inner wall of the annular boss and the movable rod, and only the closing area is in sealing contact with the movable rod. In the later stage of braking, the inner edge of the closing and the movable rod seal ensures smooth sliding of the movable rod under the condition of ensuring the pressure difference. At the same time, since the pressure in the working chamber is greater at this time, the outer periphery of the annular boss will be subjected to radial inward pressure and deformed so that the closing area fully maintains contact with the movable rod, while ensuring the sealing effect, it can also supplement the friction loss caused by the relative sliding of the movable rod, which is conducive to extending the working life.

[0009] In the aforementioned brake valve's balanced structure, a valve plate is installed around the outer circumference of the movable rod, which is sealed against the sealing ring at all times. The annular boss is located on the side of the sealing ring away from the valve plate. This provides skeletal support for the sealing ring, allowing the inner cavity of the annular boss, from the valve plate to the closing area, to form a relatively sealed cavity with the outer circumference of the movable rod. Whether the brake valve is braking or resetting, the pressure within this cavity remains lower than the external oil pressure. This prevents the closing area from opening and being damaged during brake pressure replenishment, thus ensuring the stability and service life of the closing area.

[0010] In the aforementioned brake valve's balanced structure, the annular boss is shaped like a trumpet, with the larger end facing the valve plate. This helps ensure greater structural stability when the annular boss is under pressure, preventing large-area contact between the inner wall of the annular boss and the movable rod. This ensures a stable internal cavity volume, allowing the oil pressure to continuously seal the annular boss and the movable rod.

[0011] In the balancing structure of the above-mentioned brake valve, the outer peripheral surface of the balancing piston has a balancing flow channel connected to the end of the balancing piston away from the main piston. The end of the balancing piston away from the main piston is provided with a one-way sealing member that only allows the fluid in the balancing flow channel at this location to flow out. A spring seat is provided in the valve body, which always abuts against the end of the balancing piston away from the main piston. The one-way sealing member includes a spring member, a support plate, the sealing ring and the valve plate. The two ends of the spring member act on the sealing ring and the support plate respectively so that the sealing ring and the valve plate close the port of the balancing flow channel. The support plate abuts against the spring seat under the action of the spring member. The balancing flow channel is controlled by a one-way sealing member to control the flow of fluid in the oil supply chamber toward the working chamber. In this way, when braking, the main piston pushes the balancing piston to move and compresses the working chamber, and at the same time the space in the oil supply chamber will also be limited. Since the working chamber is connected to the brake, the pressure in the oil supply chamber is larger than that in the working chamber at the beginning of braking. During the braking process, the high-pressure fluid in the oil supply chamber can be continuously replenished to the working chamber to ensure sufficient and stable braking pressure. In this way, under the condition that the sealing ring and the valve plate provide a seal to maintain the pressure difference between the movable rod and the balancing piston, it also participates in the braking pressure replenishment of the balancing flow channel as part of the one-way sealing member to provide a control effect, making the structure more compact.

[0012] In the aforementioned brake valve's balancing structure, the one-way sealing member further includes a spring washer that abuts against the side of the sealing ring with the annular boss. The spring washer has an annular flange that projects toward the side of the support plate. The spring element is sleeved around the outer periphery of the annular flange, with one end acting on the spring washer. The outer peripheral surface of the annular flange has an annular step groove arranged circumferentially. This allows the spring washer to directly interact with the spring element, preventing damage to the sealing ring. The annular flange also protects and positions the inner and outer annular bosses and the spring element, respectively, reducing the likelihood of interference and scraping between the spring element and the outer periphery of the spring washer when the spring element moves relative to it, thereby extending its service life.

[0013] In the above-mentioned balancing structure of the brake valve, the other end of the movable rod abuts against the support plate, so that the support plate can provide a position limit for the other end of the movable rod, prevent the movable rod from separating from the balancing piston, and ensure smooth sliding.

[0014] In the aforementioned brake valve's balancing structure, the support disc has a sliding hole, and the other end of the movable rod is connected to a T-shaped stopper. The stopper extends through the sliding hole and can slide relative to the support disc along with the movable rod. The stopper abuts against the side of the support disc away from the annular valve member, axially limiting the movable rod. In this way, the support disc provides radial restraint for the other end of the movable rod, ensuring its stable direction of movement and facilitating more stable operation of the brake valve. Furthermore, the stopper cooperates with the support disc to limit the range of travel of the movable rod, preventing excessive extension of the movable rod that could affect the opening and closing life of the one-way assembly.

[0015] As another solution, the other end of the movable rod is fixedly connected to the support plate. The other end of the movable rod is fixedly connected to the support plate, that is, when the movable rod pushes open the valve block, it drives the support plate to move along the axial direction of the movable rod toward the one-way component. In this way, after braking is completed, the support plate will move synchronously with the movable rod. During this process, the support plate will gradually compress the spring part, gradually increasing the resistance to the movement of the movable rod, while also stirring the surrounding fluid in a larger range, preventing the movable rod from causing impact damage and abnormal noise to the one-way component, extending the service life of the one-way component, and when the movable rod drives the support plate to reset, the movable plate has a greater resistance to the movement of the fluid, which is beneficial to reducing the kinetic energy of the reset impact, reducing the probability of deformation of the support plate, and ensuring the service life.

[0016] In the above-mentioned brake valve balancing structure, the support plate is provided with an annular positioning sleeve, and the other end of the movable rod is positioned and inserted into the annular positioning sleeve. In this way, the annular positioning sleeve can further guide the sliding of the other end of the movable rod, making its radial position and sliding direction more stable and reliable.

[0017] In the aforementioned brake valve's balancing structure, the spring seat is cylindrical and sleeved around the support plate. A drainage notch is defined at the junction of the balancing piston and the spring seat, connecting the inner and outer sides of the spring seat. This facilitates the full release of high-pressure fluid into the working chamber through the drainage notch and the inner cavity of the spring seat when the balancing flow passage is opened, improving response speed and ensuring safe pressure compensation.

[0018] Compared with the prior art, the advantages of the present invention are as follows:

[0019] In the balance structure of this brake valve, a certain distance is maintained between most of the inner walls of the annular boss and the movable rod. After the braking is completed, the closing area and the movable rod seal ensure that the movable rod slides smoothly under the condition of ensuring the pressure difference. At the same time, since the pressure in the working chamber is greater at this time, the outer periphery of the annular boss will be subjected to radial inward pressure to enable the closing area to fully maintain contact with the movable rod. While ensuring the sealing effect, it can also compensate for the friction loss caused by the relative sliding of the movable rod, which is conducive to extending the working life. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1It is a schematic diagram of the cross-sectional structure during the pressurization process of Example 1.

[0021] Figure 2 yes Figure 1 Enlarged view of part A in .

[0022] Figure 3 yes Figure 2 Enlarged view of part B in .

[0023] Figure 4 It is a schematic cross-sectional structure diagram of the first embodiment in the late braking stage.

[0024] Figure 5 yes Figure 4 Enlarged view of part C in .

[0025] Figure 6 Schematic diagram of the three-dimensional structure of Example 1.

[0026] Figure 7 It is a schematic cross-sectional view of the local structure of the second embodiment.

[0027] Figure 8 It is a schematic cross-sectional view of the local structure of the third embodiment.

[0028] In the figure, 1, valve body; 11, oil inlet hole; 12, working oil hole

[0029] 2. Main piston;

[0030] 3. Balancing piston; 31. Pressure relief channel; 32. Balancing channel; 33. Discharge notch; 34. Oil transfer port;

[0031] 4. Working chamber; 5. Oil supply chamber;

[0032] 6. Spring seat; 61. Positioning step groove; 62. Liquid hole;

[0033] 7. One-way assembly; 71. Valve block; 72. Compression spring;

[0034] 8. Movable rod; 81. Top rod section; 82. Connecting section; 83. Limiting piece;

[0035] 9. One-way blocking member, 91. Sealing ring; 911. Annular boss; 912. Closure; 92. Valve plate; 93. Support plate; 931. Through hole; 932. Sliding hole; 933. Annular positioning sleeve; 94. Spring member; 95. Spring washer; 951. Annular flange; 952. Annular step groove;

[0036] 20. Pedal connecting rod assembly; 30. Control oil hole; 40. Oil return hole; 50. Return spring; 60. Spring base; 70. Guide rod. DETAILED DESCRIPTION

[0037] The following are specific embodiments of the present invention and the accompanying drawings to further describe the technical solutions of the present invention, but the present invention is not limited to these embodiments. Example 1:

[0038] like Figure 1As shown, in the balancing structure of the brake valve, the brake valve includes a valve body 1, the outer periphery of the valve body 1 is provided with an oil inlet hole 11 and a working oil hole 12, and the valve body 1 is provided with a main piston 2 and a balancing piston 3 that are in abutment with each other, and the maximum outer diameter of the main piston 2 is larger than the outer diameter of the balancing piston 3, that is, the radial dimension of the inner cavity of the valve body 1 in the sliding area of ​​the main piston 2 is larger than the radial dimension of the inner cavity of the valve body 1 in the sliding area of ​​the balancing piston 3. When braking, the balancing piston 3 slides its end face away from the main piston 2 and forms a working chamber 4 connected to the working oil hole 12 between the inner wall of the valve body 1, and the outer periphery of the balancing piston 3 can form an oil supply chamber 5 that can replenish the pressure of the working chamber 4 between the inner wall of the valve body 1 through a sealing structure, and the volume of the oil supply chamber 5 changes as the balancing piston 3 slides, and the balancing piston 3 has a pressure relief channel 31 that can connect the oil supply chamber 5 and the oil inlet hole 11 and a pressure relief channel 31 that can connect the oil supply chamber 5 and the oil inlet hole 11. The balancing flow channel 32 of the oil supply chamber 5 and the working chamber 4, one end of the pressure relief flow channel 31 is located on the end surface of the balancing piston 3 facing the main piston 2, the oil port 34 is the other end of the pressure relief flow channel 31, and there are multiple oil ports 34. The pressure relief flow channel 31 between the main piston 2 and the balancing piston 3 is provided with a one-way component 7 that closes the pressure relief flow channel 31, and a spring seat 6 that always presses against the balancing piston 3 is provided in the working chamber 4. A return spring 50, a spring base 60 and a guide rod 70 are also provided in the working chamber 4. The two ends of the return spring 50 act on the spring seat 6 and the spring base 60 respectively, and the spring base 60 rests on the bottom surface of the working chamber 4. The guide rod 70 is axially connected to the spring base 60 and is slidably connected to the spring seat 6 to provide guidance for the movement of the balancing piston 3. The return spring 50 can push the balancing piston 3 to reset after the braking is completed. The working chamber 4 is provided with a one-way blocking member 9 that blocks the port of the balancing flow channel 32. A movable rod 8 is also slidably inserted into the balancing piston 3. The main piston 2 and the balancing piston 3 are arranged in the valve body 1. The driver steps on the driving pedal connecting rod assembly 20 to move, control the oil inlet of the oil hole 30 and act on the end face of the main piston 2, so that the main piston 2 and the balancing piston 3 that are against each other slide synchronously. The oil return hole 40 is used to discharge the fluid acting on the end face of the main piston 2 after the braking is completed. The oil inlet hole 11 is used to connect the oil cup. The working chamber 4 is connected to the working oil hole 12. Directly involved in supplying oil to the brake, the connection between the oil supply chamber 5 and the working chamber 4 changes according to the travel of the balancing piston 3 and the internal pressure. A movable rod 8, inserted within the balancing piston 3, can abut against a valve block 71 under the pressure differential between the working chamber 4 and the oil supply chamber 5, opening the pressure relief passage 31. This allows the fluid in the oil supply chamber 5 to be depressurized and flow back during the later stages of braking, allowing the balancing piston 3 to continue sliding and braking. The inner wall of the spring seat 6 has a radially extending fluid hole 62, located near the end of the spring seat 6 facing away from the primary piston 2. This allows high-pressure fluid released from the balancing passage 32 to be directly released deep into the working chamber 4, facilitating rapid and stable pressure equalization.

[0039] like Figure 2As shown, the one-way assembly 7 includes a valve block 71 and a compression spring 72. The valve block 71 is spherical. Under the elastic force of the compression spring 72, the valve block 71 always has a tendency to close the pressure relief channel 31; the one-way sealing member 9 includes a valve plate 92, a sealing ring 91, a spring member 94 and a support plate 93. The sealing ring 91 is a rubber material member, and the valve plate 92 is a rigid material member. The movable rod 8 includes an integrally connected top rod section 81 and a connecting section 82. The diameter of the top rod section 81 is smaller than the diameter of the connecting section 82. The sealing ring 91 is sealingly sleeved on the outer periphery of the connecting section 82. The spring member 94 is a compression spring 72 and its two ends act on the sealing ring 91 and the support plate 93 respectively. Under the action of the spring member 94, the sealing ring 91 cooperates with the valve plate 92 to abut against the balancing piston 3 to close the balancing channel 32. The support plate 93 abuts against the spring seat 6, and the connecting section 82 abuts against the support plate 93. The sealing ring 91 includes an annular boss 911 that protrudes axially toward the other end of the movable rod 8. The inner edge of the end of the annular boss 911 seals against the movable rod 8 circumferentially. By providing the annular boss 911 on the sealing ring 91, which protrudes axially toward the other end of the movable rod 8, and sealing the inner edge of the end of the annular boss 911 circumferentially against the outer periphery of the movable rod 8, a certain distance is maintained between the inner wall of the annular boss 911 and the movable rod 8, allowing the movable rod 8 to slide smoothly after braking. At the same time, because the pressure in the working chamber 4 is higher at this time, the outer periphery of the annular boss 911 is subjected to radial inward pressure, causing the closing portion 912 to maintain full contact with the movable rod 8. This ensures a good seal while compensating for friction losses caused by relative sliding between the sealing portion and the movable rod 8. Furthermore, an oil film is formed on the surface of the movable rod 8, further reducing friction damage to the annular boss 911 and thereby extending its service life. The annular boss 911 is located on the side of the sealing ring 91 away from the valve plate 92. In this way, the valve plate 92 can provide a skeleton support for the sealing ring 91, so that the inner cavity of the annular boss 911 from the valve plate 92 to the inner wall of the annular boss 911 closure 912 area and the outer periphery of the movable rod 8 form a relatively sealed cavity, and the pressure in the cavity is smaller than the external oil pressure, that is, the inner cavity pressure of the annular boss 911 will not be higher than the external pressure during the braking pressure replenishment, so that the annular boss 911 will not be tilted and damaged, thereby ensuring the stability and service life of the annular boss 911. The end face of the spring seat 6 facing the balance piston 3 has a positioning step groove 61, and the support plate 93 abuts against the bottom surface of the positioning step groove 61, and the shape of the support plate 93 is adapted to the shape of the positioning step groove 61. The spring seat 6 is cylindrical and is sleeved on the outer periphery of the support plate 93. The joint surface between the balance piston 3 and the spring seat 6 has a drainage notch 33, and the drainage notch 33 can connect the inner and outer sides of the spring seat 6. This facilitates the full release of high-pressure fluid into the working chamber 4 through the discharge notch 33 and the inner cavity of the spring seat 6 when the balancing flow channel 32 is opened, improving response speed and ensuring pressure replenishment safety. The support plate 93 has a plurality of through holes 931 extending through both sides. The inner edges of the through holes 931 are chamfered, and the outer edges of the support plate 93 are also chamfered.This facilitates direct release of fluid within the balanced flow channel 32 through the through-hole 931 of the support disc 93 and through the spring seat 6, while also reducing friction between the support disc 93 and the spring seat 6, thereby extending its service life. The one-way sealing member 9 also includes a spring washer 95 that abuts against the side of the sealing ring 91 having the annular boss 911. The spring washer 95 has an annular flange 951 that protrudes toward the side of the support disc 93. The spring member 94 is sleeved around the outer periphery of the annular flange 951, with one end acting on the spring washer 95. The outer peripheral surface of the annular flange 951 has an annular step groove 952 arranged circumferentially. In this way, the spring washer 95 can directly interact with the spring member 94, preventing the spring member 94 from damaging the sealing ring 91. The annular flange 951 also provides protection and positioning for the inner and outer annular bosses 911 and the spring member 94, respectively, reducing the probability of interference and friction between the spring member 94 and the spring washer 95 when it moves relative to the outer periphery, thereby extending its service life.

[0040] like Figure 3 As shown, the annular boss 911 is in the shape of a trumpet with the larger end facing the side where the valve plate 92 is located. This helps ensure that the annular boss 911 has stronger structural stability when under pressure, avoids large-area contact between the inner wall of the annular boss 911 and the movable rod 8, and ensures the stability of the internal cavity volume so that the oil pressure can continuously act on the annular boss 911 and the movable rod 8 to seal. The edge of the annular boss 911 has a closing opening 912 with a smaller inner diameter, and the closing opening 912 forms a linear seal with the movable rod 8 around the circumference. In this way, since the end of the annular boss 911 is more prone to deformation, continuous squeezing of the closing opening 912 area is ensured when subjected to a pressure difference.

[0041] like Figure 4 As shown, this is the structural state of the brake valve after the pressure replenishment is completed. At this time, the pressure in the working chamber 4 gradually becomes higher than the pressure in the oil supply chamber 5, so that the movable rod 8 slides toward the one-way component 7 relative to the annular boss 911 under the action of the pressure difference at both ends and overcomes the preset resistance of the one-way component 7 to trigger the one-way component 7 and open the pressure relief channel 21, so that the oil inlet hole 11 is connected with the oil supply chamber 5 to relieve pressure.

[0042] like Figure 5 As shown, at this time, the movable rod 8 slides relative to the annular boss 911 so that the push rod section 81 abuts against the valve block 72, and the hydraulic oil can flow through the pressure relief channel 21 to achieve pressure relief and backflow.

[0043] like Figure 6 As shown, the pedal connecting rod assembly 20 can be an existing assembly component with a pedal, which is connected and arranged at the bottom of the valve body 1. Example 2:

[0044] like Figure 7As shown, this embodiment is basically the same as the first embodiment, except that: the end of the movable rod 8 away from the valve block 71 is connected to the support plate 93, and the movable rod 8 can drive the support plate 93 to move toward the valve block 71 along the axial direction of the movable rod 8 and make the movable rod 8 press against the valve block 71 to open the pressure relief channel 31. By connecting the end of the movable rod 8 away from the valve block 71 to the support plate 93, when the movable rod 8 pushes the valve block 71 open, it drives the support plate 93 to move along the axial direction of the movable rod 8 toward the valve block 71. After braking is completed, the pressure in the working chamber 4 is greater than the pressure in the oil supply chamber 5, causing the movable rod 8 to slide toward the valve member, and the support plate 93 will move synchronously with the movable rod 8. During this process, the support plate 93 gradually compresses the spring member 94, which is used to control the annular valve member and gradually increases the resistance to the movement of the movable rod 8. At the same time, it also stirs the surrounding fluid to a greater extent, preventing the movable rod 8 from causing impact damage and abnormal noise on the valve block 71, thereby extending the service life of the valve member. Moreover, when the movable rod 8 drives the support plate 93 to reset, the movable plate also has greater resistance to the movement of the fluid, which helps to reduce the kinetic energy of the reset impact, reduce the probability of deformation of the support plate 93, and ensure the service life of the valve member. In this way, the position of the support plate 93 during movement is effectively constrained by the positioning step groove 61, so that the support plate 93 moves stably and does not deviate, while enhancing the deceleration effect of the support plate 93 and ensuring stable and reliable operation. Specifically, the depth of the positioning step groove 61 is greater than the distance between the end of the movable rod 8 and the valve block 71. This ensures that the movable rod 8 is always constrained by the positioning step groove 61 during the movement of the support plate 93, thereby improving working stability. Example 3:

[0045] like Figure 8 As shown, this embodiment is substantially identical to the first embodiment, differing in that a support plate 93 includes a sliding hole 932, and the other end of the movable rod 8 is connected to a T-shaped stopper 83. The stopper 83 extends through the sliding hole 932 and can slide relative to the support plate 93 along with the movable rod 8. The stopper 83 abuts against the side of the support plate 93 away from the annular valve member, axially limiting the movable rod 8. This support plate 93 provides radial restraint for the other end of the movable rod 8, ensuring its directional stability and facilitating more stable operation of the brake valve. Furthermore, the stopper 83 cooperates with the support plate 93 to limit the travel range of the movable rod 8, preventing excessive extension of the movable rod 8 and affecting the opening and closing life of the one-way assembly 7. The support plate 93 includes an annular locating sleeve 933, into which the other end of the movable rod 8 is positioned and inserted. This sleeve further guides the sliding of the other end of the movable rod 8, ensuring both its radial position and sliding direction are more stable and reliable.

[0046] The specific embodiments described herein are merely illustrative of the spirit of the present invention. Persons skilled in the art may make various modifications, additions, or substitutions to the described specific embodiments without departing from the spirit of the present invention or exceeding the scope of the appended claims.

Claims

1. A balancing structure of a brake valve, comprising a valve body (1) with an oil inlet hole (11), wherein a main piston (2) and a balancing piston (3) are provided in the valve body (1) and abut against each other, characterized in that: The balancing structure includes a pressure relief channel (31) located in the balancing piston (3) and a one-way component (7) located between the main piston (2) and the balancing piston (3) and blocking the communication between the pressure relief channel (31) and the oil inlet hole (11). The outer peripheral surface of the balancing piston (3) has an oil port (34) connected to the pressure relief channel (31). A movable rod (8) passing through the balancing piston (3) is slidably connected in the balancing piston (3). One end of the movable rod (8) is located in the pressure relief channel (31), and the outer periphery of the other end of the movable rod (8) or the outer periphery of the middle section of the movable rod (8) is connected to the pressure relief channel (31). The final sleeve is provided with a sealing ring (91) that can be sealed with the balance piston (3) along the circumferential direction. The sealing ring (91) has an annular boss (911) that protrudes axially toward the position where the other end of the movable rod (8) is located. The annular boss (911) is arranged around the periphery of the movable rod (8). The edge of the annular boss (911) has a closing opening (912) with a smaller inner diameter. The inner edge of the closing opening (912) is sealed with the movable rod (8) along the circumferential direction. The movable rod (8) can slide axially relative to the annular boss (911) toward the one-way component (7) and push the one-way component (7) up.

2. The balancing structure of the brake valve according to claim 1, characterized in that: The outer peripheral sealing sleeve of the movable rod (8) is provided with a valve plate (92), and the valve plate (92) is always in sealing contact with the sealing ring (91), and the annular boss (911) is located on the side of the sealing ring (91) away from the valve plate (92).

3. The balancing structure of the brake valve according to claim 2, characterized in that: The annular boss (911) is in the shape of a trumpet with the larger end facing the side where the valve plate (92) is located.

4. The balancing structure of the brake valve according to claim 2 or 3, characterized in that: The outer peripheral surface of the balancing piston (3) has a balancing flow channel (32) connected to the end of the balancing piston (3) away from the main piston (2), and the end of the balancing piston (3) away from the main piston (2) is provided with a one-way sealing member (9) that only allows the fluid in the balancing flow channel (32) to flow out. The valve body (1) is provided with a spring seat (6) that always abuts against the end of the balancing piston (3) away from the main piston (2). The one-way sealing member (9) includes a spring member (94), a support plate (93), the sealing ring (91) and the valve plate (92). The two ends of the spring member (94) act on the sealing ring (91) and the support plate (93) respectively so that the sealing ring (91) and the valve plate (92) close the port of the balancing flow channel (32). The support plate (93) abuts against the spring seat (6) under the action of the spring member (94).

5. The balancing structure of the brake valve according to claim 4, characterized in that: The one-way sealing member (9) further includes a spring washer (95) abutting against the side of the annular boss (911) of the sealing ring (91), the spring washer (95) having an annular flange (951) protruding toward the side where the support plate (93) is located, the spring member (94) is sleeved on the outer periphery of the annular flange (951) and one end acts on the spring washer (95), and the outer peripheral surface of the annular flange (951) has an annular step groove (952) arranged circumferentially.

6. The balancing structure of the brake valve according to claim 4, characterized in that: The other end of the movable rod (8) abuts against the support plate (93).

7. The balancing structure of the brake valve according to claim 6, characterized in that: The support plate (93) has a sliding hole (932), and the other end of the movable rod (8) is connected to a T-shaped limiting member (83). The limiting member (83) passes through the sliding hole (932) and can slide relative to the support plate (93) along with the movable rod (8). The limiting member (83) can abut against the side of the support plate (93) away from the annular valve member along the axial direction of the movable rod (8).

8. The balancing structure of the brake valve according to claim 4, characterized in that: The other end of the movable rod (8) is fixedly connected to the support plate (93).

9. The balancing structure of the brake valve according to claim 4, characterized in that: The support plate (93) is provided with an annular positioning sleeve (933), and the other end of the movable rod (8) is positioned and inserted into the annular positioning sleeve (933).

10. The balancing structure of the brake valve according to claim 4, characterized in that: The spring seat (6) is cylindrical and is sleeved on the periphery of the support plate (93). A drainage gap (33) is provided at the junction of the balancing piston (3) and the spring seat (6). The drainage gap (33) can connect the inner and outer sides of the spring seat (6).

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