Dual mode pilot operated counter brake valve

Abstract

The utility model relates to vehicle hydraulic braking technical field, concretely relates to a kind of double mode hydraulic control reverse brake valve, including valve body, valve body includes piston cavity and valve core cavity, and main valve core is equipped in valve core cavity and is connected with tank oil port T, pressure oil port P and brake oil port A;Valve body is equipped with the operating mechanism that can drive main valve core axial motion, operating mechanism includes mechanical brake assembly and hydraulic control brake assembly, mechanical brake assembly is located in piston cavity, hydraulic control brake assembly is located at the bottom of valve body and is formed with hydraulic control cavity between the bottom of valve body, and hydraulic control brake assembly includes hydraulic control port PP, and the high-pressure hydraulic oil is connected with hydraulic control port PP and is connected with hydraulic control cavity;By integrating the two operating modes of mechanical brake and hydraulic control brake in the same valve body, and the two operating modes are independent of each other, the technical limitation that only relying on artificial pedal brake in the prior art is solved, and technical support is provided for realizing remote control and automatic driving of underground transport equipment.

Description

Technical Field

[0001] This utility model relates to the field of vehicle hydraulic braking technology, specifically to a dual-mode hydraulically controlled reverse braking valve. Background Technology

[0002] Trackless rubber-tired vehicles play an important role in underground transportation due to their high flexibility and adaptability. However, the narrow environment of underground tunnels, the dense equipment layout, and the complex operating routes bring continuous operational pressure to drivers, leading to frequent cases of fatigue driving and seriously affecting transportation safety.

[0003] Currently, engineering machinery vehicles typically employ braking systems that match a hydraulic power reverse brake valve with a spring-loaded hydraulic release brake. For example, patent application number 202122216617.5, entitled "A Reverse Brake Valve Applied to a Hydraulic Braking System," describes a system where the reverse brake valve outputs braking force to the hydraulic brake via a pedal. While this meets basic braking requirements, its single pedal operation mode has significant limitations: on the one hand, it is difficult to meet the requirements of automation and intelligence development in underground transportation equipment; on the other hand, it is difficult for drivers to guarantee the accuracy and reliability of braking operations under long-term, high-intensity working conditions.

[0004] Therefore, while ensuring the existing pedal control mode, it is particularly urgent to develop a new braking system that combines remote control and automatic driving assistance. Utility Model Content

[0005] The purpose of this invention is to provide a dual-mode hydraulic reverse braking valve to solve the existing technical problems mentioned above.

[0006] The technical solution provided by this utility model is as follows: a dual-mode hydraulic reverse braking valve is provided, including a valve body. The inner cavity of the valve body includes a piston cavity and a valve core cavity arranged sequentially. The valve body is provided with an oil tank port T, a pressure port P, and a brake port A that are connected to the valve core cavity. A main valve core is provided in the valve core cavity. An operating mechanism that can drive the main valve core to move axially is provided on the valve body. The operating mechanism includes a mechanical braking component and a hydraulic braking component. The mechanical braking component is located in the piston cavity. The hydraulic braking component is located at the bottom of the valve body and forms a hydraulic control cavity with the bottom of the valve body. The hydraulic control braking component includes a hydraulic control port PP. The hydraulic control port PP is connected to high-pressure hydraulic oil and is connected to the hydraulic control cavity. When the operating mechanism is in normal operation, the main valve core is in a stable force balance position, and the main valve core disconnects the oil tank port T, the pressure port P, and the brake port A from each other. When the operating mechanism is in operation, the main valve core is in the upper working position, and the main valve core connects the oil tank port T with the brake oil port A.

[0007] Based on the above technical solution, the hydraulic control brake assembly includes a screw plug connector, a screw plug damping hole, and a hydraulic control valve core. The screw plug connector is fixedly installed at the bottom of the valve body. The hydraulic control port PP and the screw plug damping hole are installed on the screw plug connector. The hydraulic control port PP is connected to the hydraulic control cavity through the screw plug damping hole. The hydraulic control valve core is fixedly connected to the top of the screw plug connector.

[0008] Based on the above technical solution, a second steel ball is also included. The end of the main valve core away from the piston chamber is recessed inward along the axial direction to form a blind hole. The main valve core is provided with a hydraulic damping hole that connects the blind hole and the brake oil port A. The blind hole includes a spring cavity, a steel ball limiting cone surface, and a hydraulic valve core mating surface arranged in sequence. A second return spring is provided in the spring cavity. The second steel ball is located in the space enclosed by the steel ball limiting cone surface and abuts against the steel ball limiting cone surface. The inner diameter of the top of the steel ball limiting cone surface is smaller than the diameter of the second steel ball. The hydraulic valve core mating surface is slidably sleeved on the outside of the hydraulic valve core. One end of the second return spring, the second steel ball, and the hydraulic valve core abut against each other in sequence.

[0009] Preferably, the outer surface of the main valve core is provided with an annular groove. When the main valve core is in the upper working position, the annular groove connects the oil tank port T with the brake oil port A; when the main valve core is in the lower working position, the annular groove connects the pressure oil port P with the brake oil port A.

[0010] Preferably, the mechanical braking assembly includes a pedal, a transition block, a lifting seat, and a spring assembly arranged in sequence. The pedal is hinged to the transition block, the transition block is fixedly connected to the top of the lifting seat, the lifting seat is slidably sleeved in the piston cavity, and a first return spring is sleeved on the outer side of the lifting seat. One end of the first return spring abuts against the top surface of the piston cavity, and the other end of the first return spring abuts against the bottom of the lifting seat.

[0011] Based on the above technical solution, the bottom of the lifting seat is recessed inward along the axial direction to form an inverted U-shaped groove. The spring assembly is located in the inverted U-shaped groove. The spring assembly includes a pressure regulating spring and a spring seat. One end of the pressure regulating spring abuts against the top of the inverted U-shaped groove, and the other end of the pressure regulating spring abuts against the spring seat. The top of the main valve core is provided with a conical groove. A third steel ball is provided between the bottom of the spring seat and the conical groove. The third steel ball is rotatably abuts against the spring seat and the main valve core.

[0012] Preferably, a valve cover is provided on the upper part of the piston chamber, the valve cover is fixedly connected to the valve body, the valve cover is sleeved on the outside of the lifting seat, the lifting seat slides axially relative to the valve cover, and a dustproof sleeve is provided between the outer end face of the lifting seat and the valve cover.

[0013] Based on the above technical solution, the bottom of the lifting seat is provided with a limiting shoulder, one end of the first return spring abuts against the bottom of the valve cover, and the other end of the first return spring abuts against the limiting shoulder.

[0014] Preferably, the valve body is further provided with a pressure relief oil chamber, which is connected to both the brake oil port A and the pressure oil port P. The pressure relief oil chamber is provided with a one-way valve that allows oil to flow from the brake oil port A to the pressure oil port P.

[0015] Based on the above technical solution, the pressure relief oil chamber has an opening on the valve body, the opening is sealed by a screw plug, and the one-way valve includes a first steel ball and a third return spring. One end of the third return spring abuts against the first steel ball, and the other end of the third return spring abuts against the screw plug.

[0016] The beneficial effects of the technical solution provided by this utility model are as follows: (1) By integrating mechanical braking and hydraulic braking into the same valve body, and with the two operating modes working independently, the technical limitation of relying solely on manual pedal braking in the prior art is solved, providing technical support for realizing remote control operation and automatic driving of underground transportation equipment.

[0017] (2) Connect the hydraulic control port and the hydraulic control cavity through the screw plug damping hole so that the hydraulic control pressure is buffered and acts smoothly on the bottom of the main valve core. This not only ensures the timeliness of the braking response, but also significantly reduces the vibration and noise caused by hydraulic shock, making the system work more smoothly and reliably.

[0018] (3) The design of the main valve core directly cooperating with the valve body eliminates the valve sleeve component, reduces manufacturing costs, and simplifies the process. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the overall structure of this utility model; Figure 2 This is a cross-sectional structural schematic diagram of the front view of the reverse braking valve in this utility model; Figure 3 This is a cross-sectional structural schematic diagram of the valve body front view in this utility model; Figure 4 This is a cross-sectional structural schematic diagram of the main valve core front view in this utility model; Figure 5 This is a schematic diagram of the structure of the main valve core and the hydraulic control brake assembly in this utility model. Detailed Implementation

[0020] The present invention will be further described below with reference to the accompanying drawings and embodiments: In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," 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 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. For those skilled in the art, the specific meaning of the above terms in this utility model can be understood according to the specific circumstances.

[0021] In the description of this utility model, it should be understood that the terms "left", "right", "front", "rear", "top", "bottom", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not 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 utility model.

[0022] like Figures 1 to 5 As shown, a dual-mode hydraulic reverse brake valve includes a valve body 1. The inner cavity of the valve body 1 includes a piston cavity 11 and a valve core cavity 12 arranged sequentially. The valve body 1 is provided with an oil tank port T, a pressure port P and a brake port A that are connected to the valve core cavity 12. The other end of the brake port A is connected to a reverse hydraulic brake.

[0023] The valve core cavity 12 is equipped with a main valve core 6, which is designed to directly mate with the valve body 1, eliminating the need for a valve sleeve component, reducing manufacturing costs, and simplifying the process. Specifically, the outer surface of the main valve core 6 is provided with an annular groove 65. When the main valve core 6 is in the upper working position, the annular groove 65 connects the oil tank port T with the brake oil port A, realizing the pressure relief of the brake oil port A; when the main valve core 6 is in the lower working position, the annular groove 65 connects the pressure oil port P with the brake oil port A, realizing the pressure increase of the brake oil port A. The end of the main valve core 6 away from the piston cavity 11 is recessed inward along the axial direction to form a blind hole. The blind hole includes a spring cavity 61, a steel ball limiting cone surface 62, and a hydraulic control valve core mating surface 63 arranged in sequence. The spring cavity 61 is equipped with a second return spring 8 for resetting the main valve core 6. The second steel ball 9 is located within the space enclosed by the steel ball limiting cone surface 62 and abuts against the steel ball limiting cone surface 62. The inner diameter of the top of the steel ball limiting cone surface 62 is smaller than the diameter of the second steel ball 9. The second steel ball 9 is limited by the steel ball limiting cone surface 62, ensuring the precise positioning of the second steel ball 9. The hydraulic control valve core mating surface 63 is slidably sleeved on the outside of the hydraulic control valve core 10. The second return spring 8, the second steel ball 9, and the hydraulic control valve core 10 abut against each other in sequence. The main valve core 6 is equipped with a hydraulic control damping hole 64 that connects the blind hole and the brake oil port A. The hydraulic control damping hole 64 introduces the braking pressure of the brake oil port A into the spring cavity 61, forming a hydraulic feedback force acting on the main valve core 6. At the same time, the hydraulic control damping hole 64 can effectively buffer the fluctuation of the brake oil pressure and improve the stability of the system.

[0024] The valve body 1 is provided with an operating mechanism that can drive the main valve core 6 to move axially. The operating mechanism includes a mechanical braking component and a hydraulic braking component.

[0025] The mechanical braking assembly is located within the piston chamber 11. The mechanical braking assembly includes a pedal 19, a transition block 18, a lifting seat 2, and a spring assembly arranged sequentially. The pedal 19 is hinged to the transition block 18, and the transition block 18 is fixedly connected to the top of the lifting seat 2. The lifting seat 2 is slidably fitted within the piston chamber 11. A first return spring 7 is fitted onto the outer side of the lifting seat 2. One end of the first return spring 7 abuts against the inner top surface of the piston chamber 11, and the other end abuts against the bottom of the lifting seat 2. The first return spring 7 is used to reset the lifting seat 2. Preferably, a valve cover 17 is provided on the upper part of the piston chamber 11. The valve cover 17 is fixedly connected to the valve body 1 and is fitted onto the outside of the lifting seat 2. The lifting seat 2 slides axially relative to the valve cover 17. A dust cover 23 is provided between the outer end faces of the lifting seat 2 and the valve cover 17. The valve cover 17 and the dust cover 16 together provide sealing and dust prevention. Preferably, the bottom of the lifting seat 2 is provided with a limiting shoulder 22, one end of the first return spring 7 abuts against the bottom of the valve cover 17, and the other end of the first return spring 7 abuts against the limiting shoulder 22.

[0026] The bottom of the lifting seat 2 is recessed inward along the axial direction to form an inverted U-shaped groove 21, and the spring assembly is located in the inverted U-shaped groove 21. The spring assembly includes a pressure adjusting spring 3 and a spring seat 4. One end of the pressure adjusting spring 3 abuts against the top of the inverted U-shaped groove 21, and the other end of the pressure adjusting spring 3 abuts against the spring seat 4. The top of the main valve core 6 is provided with a conical groove 66, and a third steel ball 5 is provided between the bottom of the spring seat 4 and the conical groove 66. The third steel ball 5 is rotatably abuts against the spring seat 4 and the main valve core 6, which can effectively compensate for the slight axial difference that may exist during installation and movement.

[0027] The hydraulic brake assembly operates independently of the pedal brake assembly. Located at the bottom of the valve body 1, it forms a hydraulic control chamber 24 with the bottom of the valve body 1. The hydraulic brake assembly includes a hydraulic control port PP, which is connected to high-pressure hydraulic oil and communicates with the hydraulic control chamber 24. Specifically, the hydraulic brake assembly also includes a screw plug connector 20, a screw plug damping hole 201, and a hydraulic control valve core 10. The screw plug connector 20 is fixedly installed at the bottom of the valve body 1. The hydraulic control port PP and the screw plug damping hole 201 are installed on the screw plug connector, and the hydraulic control port PP communicates with the hydraulic control chamber 24 through the screw plug damping hole 201. The hydraulic control port PP is externally connected to an electro-hydraulic proportional brake valve, which can output the required hydraulic pressure according to the input current value, achieving remote control. The hydraulic control valve core 10 is fixedly connected to the top of the screw plug connector 20.

[0028] The valve body 1 is also provided with a pressure relief oil chamber 13, which is connected to both the brake oil port A and the pressure oil port P. The pressure relief oil chamber 13 contains a one-way valve that allows oil to flow from the brake oil port A to the pressure oil port P. The pressure relief oil chamber 13 has an opening on the valve body, which is sealed by a screw plug 16. This opening facilitates the machining of the pressure relief oil chamber 13 and the assembly of the one-way valve. The one-way valve includes a first steel ball 14 and a third return spring 15. One end of the third return spring 15 abuts against the first steel ball 14, and the other end abuts against the screw plug 16. When the oil pressure at the brake oil port A is greater than that at the pressure oil port P, the pressure relief oil chamber 13 can relieve pressure, preventing excessively high oil pressure in the brake oil port A from damaging the reverse brake.

[0029] Work process: (1) When the operating mechanism is in normal operation The main valve core 6 is in a stable force balance position. The main valve core 6 disconnects the oil tank port T, pressure port P and brake port A from each other. The brake port A outputs and maintains the set braking pressure. At this time, the force balance relationship of the main valve core is: the downward spring force Fs1 generated by the pressure regulating spring is equal to the upward spring force Fs2 generated by the second return spring 8 and the upward hydraulic feedback force Fh1 generated by the brake port A acting on the spring cavity 61.

[0030] This state features automatic pressure stabilization. If the braking pressure at brake port A decreases, Fh1 decreases, disrupting the force balance of the main valve core 6. The main valve core 6 moves down to the lower working position and connects brake port A and pressure port P through the annular groove 65. Pressure oil from pressure port P replenishes brake port A, causing the braking pressure at brake port A to rise back to the set value. The main valve core then resets to a stable force balance position. If the braking pressure at brake port A exceeds the set value, Fh1 increases, disrupting the force balance of the main valve core 6. The main valve core 6 moves up to the upper working position and connects brake port A and oil tank port T through the annular groove 65 to release pressure, causing the pressure at brake port A to drop to the set value. The main valve core then resets to a stable force balance position.

[0031] (2) When the operating mechanism is in working condition Mode 1: Mechanical Braking When the driver depresses pedal 19, pedal 19 drives the lifting seat 2 to move upward along piston chamber 11 via adapter block 18. The first return spring 7 is compressed, and the preload of pressure regulating spring 3 is released, causing Fs1 to drop. At this time, the force balance of main valve core 6 is broken, and main valve core 6 moves upward to the upper working position. Main valve core 6 connects brake fluid port A and oil tank port T through annular groove 65 to release pressure, reducing the braking pressure at brake fluid port A, which in turn causes Fh1 to drop accordingly, and the force balance of main valve core 6 is restored. The depressing angle of pedal 19 is inversely proportional to the braking pressure at brake fluid port A, achieving reverse braking. After releasing pedal 19, under the action of the first return spring 7, the reverse braking valve returns to the normal pressure-stabilized state.

[0032] Mode 2: Hydraulic Control The hydraulic control port PP receives hydraulic pressure output by the electro-hydraulic proportional brake valve based on the input current value. This pressurized oil enters the hydraulic control chamber 24 through the screw plug damping hole 201 and acts on the bottom end face of the main valve core 6, generating an upward hydraulic control force Fh2. At this time, the force balance relationship of the main valve core 6 is: Fs1 = Fs2 + Fh1 + Fh2. Under the premise that Fs1 and Fs2 remain unchanged, when the hydraulic control pressure increases, Fh2 increases accordingly. To maintain balance, Fh1 needs to decrease. Therefore, the main valve core 6 moves upward to the upper working position. The main valve core 6 connects the brake oil port A and the oil tank port T through the annular groove 65 to release pressure, thereby reducing the braking pressure at the brake oil port A. When the hydraulic control pressure increases sufficiently, the braking pressure at the brake oil port A drops to zero.

[0033] The foregoing has shown and described the basic principles and main features of this utility model. It is obvious to those skilled in the art that this utility model is not limited to the details of the above exemplary embodiments. Therefore, the embodiments should be regarded as exemplary and non-limiting. The scope of this utility model is defined by the appended claims rather than the foregoing description. Therefore, it is intended to include all changes that fall within the meaning and scope of the equivalents of the claims within this utility model.

[0034] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. A dual-mode hydraulically controlled reverse braking valve, characterized in that, The valve body (1) includes a valve body (1) with a piston chamber (11) and a valve core chamber (12) arranged in sequence. The valve body (1) is provided with an oil tank port T, a pressure port P and a brake port A that are connected to the valve core chamber (12). The valve core chamber (12) is provided with a main valve core (6). The valve body (1) is provided with an operating mechanism that can drive the main valve core (6) to move axially. The operating mechanism includes a mechanical braking assembly and a hydraulic braking assembly. The mechanical braking assembly is located in the piston chamber (11). The hydraulic braking assembly is located at the bottom of the valve body (1) and forms a hydraulic control chamber (24) between it and the bottom of the valve body (1). The hydraulic control assembly includes a hydraulic control port PP. The hydraulic control port PP is connected to high-pressure hydraulic oil and is connected to the hydraulic control chamber (24). When the operating mechanism is in normal operation, the main valve core (6) is in a stable force balance position, and the main valve core (6) disconnects the oil tank port T, the pressure port P and the brake port A from each other. When the operating mechanism is in working condition, the main valve core (6) is in the upper working position, and the main valve core (6) connects the oil tank port T with the brake oil port A.

2. The dual-mode hydraulically controlled reverse braking valve according to claim 1, characterized in that, The hydraulic control braking assembly includes a screw plug connector (20), a screw plug damping hole (201), and a hydraulic control valve core (10). The screw plug connector (20) is fixedly installed at the bottom of the valve body (1). The hydraulic control port PP and the screw plug damping hole (201) are installed on the screw plug connector (20). The hydraulic control port PP is connected to the hydraulic control cavity (24) through the screw plug damping hole (201). The hydraulic control valve core (10) is fixedly connected to the top of the screw plug connector (20).

3. A dual-mode hydraulically controlled reverse braking valve according to claim 2, characterized in that, It also includes a second steel ball (9). The end of the main valve core (6) away from the piston chamber (11) is recessed inward along the axial direction to form a blind hole. The main valve core (6) is provided with a hydraulic damping hole (64) that connects the blind hole and the brake oil port A. The blind hole includes a spring cavity (61), a steel ball limiting cone surface (62) and a hydraulic valve core mating surface (63) arranged in sequence. The spring cavity (61) is provided with a second return spring (8). The second steel ball (9) is located in the space enclosed by the steel ball limiting cone surface (62) and abuts against the steel ball limiting cone surface (62). The inner diameter of the top of the steel ball limiting cone surface (62) is smaller than the diameter of the second steel ball (9). The hydraulic valve core mating surface (63) is slidably sleeved on the outside of the hydraulic valve core (10). The second return spring (8), the second steel ball (9) and the hydraulic valve core (10) abut against each other in sequence.

4. A dual-mode hydraulically controlled reverse braking valve according to claim 1, characterized in that, The outer side of the main valve core (6) is provided with an annular groove (65). When the main valve core (6) is in the upper working position, the annular groove (65) connects the oil tank port T with the brake oil port A. When the main valve core (6) is in the lower working position, the annular groove (65) connects the pressure oil port P with the brake oil port A.

5. A dual-mode hydraulically controlled reverse braking valve according to claim 1, characterized in that, The mechanical braking assembly includes a pedal (19), a transition block (18), a lifting seat (2), and a spring assembly arranged in sequence. The pedal (19) is hinged to the transition block (18), and the transition block (18) is fixedly connected to the top of the lifting seat (2). The lifting seat (2) is slidably sleeved in the piston cavity (11). A first return spring (7) is sleeved on the outer side of the lifting seat (2). One end of the first return spring (7) abuts against the top surface inside the piston cavity (11), and the other end of the first return spring (7) abuts against the bottom of the lifting seat (2).

6. A dual-mode hydraulically controlled reverse braking valve according to claim 5, characterized in that, The bottom of the lifting seat (2) is recessed inward along the axial direction to form an inverted U-shaped groove (21). The spring assembly is located in the inverted U-shaped groove (21). The spring assembly includes a pressure regulating spring (3) and a spring seat (4). One end of the pressure regulating spring (3) abuts against the top of the inverted U-shaped groove (21), and the other end of the pressure regulating spring (3) abuts against the spring seat (4). The top of the main valve core (6) is provided with a conical groove (66). A third steel ball (5) is provided between the bottom of the spring seat (4) and the conical groove (66). The third steel ball (5) is rotatably abutted between the spring seat (4) and the main valve core (6).

7. A dual-mode hydraulically controlled reverse braking valve according to claim 5, characterized in that, The piston chamber (11) is provided with a valve cover (17) at the top. The valve cover (17) is fixedly connected to the valve body (1). The valve cover (17) is sleeved on the outside of the lifting seat (2). The lifting seat (2) slides axially relative to the valve cover (17). A dust cover (23) is provided between the outer end face of the lifting seat (2) and the valve cover (17).

8. A dual-mode hydraulically controlled reverse braking valve according to claim 7, characterized in that, The bottom of the lifting seat (2) is provided with a limiting shoulder (22), one end of the first return spring (7) abuts against the bottom of the valve cover (17), and the other end of the first return spring (7) abuts against the limiting shoulder (22).

9. A dual-mode hydraulically controlled reverse braking valve according to claim 1, characterized in that, The valve body (1) is also provided with a pressure relief oil chamber (13), which is connected to both the brake oil port A and the pressure oil port P. The pressure relief oil chamber (13) is provided with a one-way valve that allows oil to flow from the brake oil port A to the pressure oil port P.

10. A dual-mode hydraulically controlled reverse braking valve according to claim 9, characterized in that, The pressure relief oil chamber (13) has an opening on the valve body, which is sealed by a screw plug (16). The one-way valve includes a first steel ball (14) and a third return spring (15). One end of the third return spring (15) abuts against the first steel ball (14), and the other end of the third return spring (15) abuts against the screw plug (16).

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