Hydraulic control system

Abstract

The utility model provides a hydraulic control system. The hydraulic control system comprises an oil tank, a power pump, a plug-in mounting type integrated mechanical valve, a pressure adjusting electromagnetic valve, a hydraulic actuator and an electric control unit. The oil tank is connected with the power pump, the plug-in type integrated mechanical valve is communicated with the power pump and the hydraulic actuator through an oil inlet P and an oil outlet A, and the pressure adjusting electromagnetic valve achieves accurate oil pressure adjustment and control through the electric control unit. According to the system, through cooperative work of the large-flow on-off capacity of the plug-in mounting type mechanical valve and the precise pressure regulating characteristic of the electromagnetic valve, the problem of flow limitation of a traditional electromagnetic valve is solved, the response speed and the pressure control precision in a large-flow scene are remarkably improved, and the system is suitable for high-pressure large-flow working conditions such as a vehicle braking system.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic control technology, and more specifically, to a hydraulic control system. Background Technology

[0002] In the actuator control stage of current vehicle hydraulic control systems, the scheme of using a single solenoid valve to control the pressure of the main oil circuit is quite common. A solenoid valve mainly consists of a solenoid coil, valve body, and valve core. It uses electromagnetic force to drive the valve core, thereby regulating the flow of hydraulic oil. It has advantages such as simple structure, reliable operation, and rapid response, and is widely used in hydraulic systems.

[0003] However, this solution has significant limitations. From a physical perspective, solenoid valves are limited by electromagnetic force and stroke, resulting in insufficient flow regulation capability. In scenarios with high flow demands, a single solenoid valve cannot provide sufficient hydraulic oil in a short time, directly restricting the actuator's output power and response speed. Taking the braking system of heavy vehicles as an example, a large amount of hydraulic oil is needed to drive the brake calipers during braking to achieve a rapid and powerful braking effect. However, existing single solenoid valves cannot meet this high flow demand in time, leading to delayed braking response, increased braking distance, and a potential threat to driving safety.

[0004] Furthermore, after the actuator completes the depressurization and oil discharge action, the system urgently needs to quickly fill and pressurize to ensure that the actuator can quickly return to a working state and meet subsequent operational requirements. However, due to the flow limitation of a single solenoid valve, the filling process is time-consuming, making rapid pressurization impossible. This drawback severely impacts the equipment's efficiency. Each time the actuator completes a work cycle, a considerable amount of time is required for filling and pressurization, significantly reducing the continuity of the entire operation and greatly restricting the equipment's performance. Therefore, there is an urgent need to develop a new technical solution to overcome the flow limitation problem inherent in existing vehicle hydraulic control systems where a single solenoid valve controls the main oil circuit pressure, meeting the requirements for high flow rates and rapid filling and pressurization, and improving the overall performance of the vehicle hydraulic control system. Utility Model Content

[0005] The purpose of this application is to provide a hydraulic control system that has the advantages of solving the flow limitation problem of traditional solenoid valves, improving system response speed and pressure regulation accuracy.

[0006] This application provides a hydraulic control system, including an oil tank, a power pump, a cartridge-type integrated mechanical valve, a pressure regulating solenoid valve, a hydraulic actuator, and an electronic control unit (ECU). The oil tank is connected to the power pump and supplies oil to the hydraulic actuator through the power pump. The inlet (P port) of the cartridge-type integrated mechanical valve is connected to the outlet of the power pump, and the outlet (A port) of the cartridge-type integrated mechanical valve is connected to the hydraulic actuator, for providing the hydraulic actuator with a large flow of pressure-adjustable oil. The inlet of the pressure regulating solenoid valve is connected to the outlet of the power pump, and the outlet of the pressure regulating solenoid valve is connected to the cartridge-type integrated mechanical valve, for regulating the oil pressure at the outlet of the cartridge-type integrated mechanical valve. The ECU is electrically connected to the pressure regulating solenoid valve and is used to regulate the oil pressure at the outlet of the pressure regulating solenoid valve.

[0007] Compared with existing technologies, the hydraulic control system proposed in this application has the following advantages: the power pump provides a large flow of oil to the hydraulic actuator, and the pressure regulating solenoid valve precisely controls the oil circuit pressure of the cartridge-type integrated mechanical valve, solving the problem of insufficient flow of existing single solenoid valves and meeting the rapid response requirements in high-flow scenarios; the electronic control unit achieves dynamic adjustment of oil pressure through electrical connection with the pressure regulating solenoid valve, improving the system control accuracy, avoiding the lag in response of traditional mechanical valves, and supporting automated control to adapt to complex working conditions.

[0008] In one possible implementation, the cartridge-type integrated mechanical valve includes a valve body, a normally closed valve core, and a spring. The valve body has an inlet port P and an outlet port A. The normally closed valve core is slidably disposed within the valve body along the axial direction. The normally closed valve core has an oil guide channel for connecting the inlet port P and the outlet port A. The normally closed valve core axially divides the interior of the valve body into a left position chamber and a right position chamber. The spring is disposed in the left position chamber to drive the normally closed valve core to move towards the right position chamber, thereby disconnecting the inlet port P and the outlet port A. The right position chamber is connected to the outlet of a pressure regulating solenoid valve. The oil from the outlet of the pressure regulating solenoid valve drives the normally closed valve core to move towards the left position chamber, thereby connecting the inlet port P and the outlet port A through the oil guide channel. Compared with existing technologies, the normally closed valve core and spring structure design allows the cartridge-type integrated mechanical valve to remain closed when not in use. When pressurized oil (from the pressure regulating solenoid valve) is introduced into the right position chamber, the valve core compresses the spring and moves, connecting the inlet P port and outlet A port through the oil guide channel, which can quickly release a large flow of oil and significantly improve the response speed of the actuator. Relying on hydraulic driving force rather than electromagnetic force to drive the valve core overcomes the flow limitation caused by the limited electromagnetic force of solenoid valves, making it especially suitable for heavy equipment that requires high pressure and large flow.

[0009] In one possible implementation, the valve body is further provided with a feedback oil passage, the two ends of which are connected to the oil outlet A port and the left position cavity, respectively. Compared with the prior art, the feedback oil passage connects the oil outlet A port and the left position cavity, so that the oil pressure at the oil outlet A port directly acts on one side of the left position cavity of the valve core, forming a pressure feedback mechanism; when the system pressure fluctuates, the feedback oil passage can automatically adjust the force on both sides of the valve core to maintain stable output pressure, avoid shocks or pressure runaway caused by load changes, and improve system reliability.

[0010] In one possible implementation, an accumulator for stabilizing oil pressure is provided between the oil outlet of the pressure regulating solenoid valve and the right-position chamber. Compared with the prior art, the accumulator between the pressure regulating solenoid valve and the right-position chamber can absorb pressure fluctuations (such as oil pressure shocks during the opening and closing of the solenoid valve), ensuring stable oil pressure in the right-position chamber, avoiding vibration or jamming of the valve core due to sudden pressure changes, and further improving the opening and closing stability and service life of the cartridge mechanical valve.

[0011] In one possible implementation, an oil pressure sensor is installed between the oil outlet A and the hydraulic actuator, and the oil pressure sensor is electrically connected to the electronic control unit (ECU). Compared with the prior art, the oil pressure sensor collects oil pressure data from the oil outlet A to the hydraulic actuator in real time and feeds it back to the ECU, forming a closed-loop control system. The ECU can dynamically adjust the pressure regulating solenoid valve according to the difference between the actual pressure and the target pressure, achieving high-precision pressure control, while also facilitating fault diagnosis and system debugging.

[0012] In one possible implementation, a filter for filtering the oil is provided between the oil tank and the power pump. Compared with the prior art, the filter, located between the oil tank and the power pump, can trap particulate impurities, metal shavings, and other contaminants in the oil, preventing impurities from entering the power pump, mechanical valves, and actuators, reducing wear on moving parts, lowering the risk of leakage, and improving the overall reliability and service life of the system.

[0013] In one possible implementation, the valve body is further provided with a return oil port T, which is connected to the oil tank. The normally closed valve core has a return oil channel for connecting the return oil port T and the outlet oil port A. Compared with the prior art, the T return oil port is connected to the outlet oil port A through the return oil channel. When the actuator needs to release pressure after completing its action, the oil can flow directly back to the oil tank through the return oil channel, avoiding the resistance loss of the traditional pressure relief path, achieving rapid unloading, shortening the system cycle, and improving working efficiency. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the structure of this application;

[0015] Figure 2 This is a schematic diagram of a cartridge-type integrated mechanical valve.

[0016] Explanation of reference numerals in the attached figures:

[0017] 1. Oil tank; 2. Power pump; 3. Cartridge-type integrated mechanical valve; 31. Oil inlet P port; 32. Oil outlet A port; 33. Normally closed valve core; 34. Spring; 35. Oil guide channel; 36. Feedback oil passage; 37. Oil return T port; 38. Oil return channel; 4. Pressure regulating solenoid valve; 5. Hydraulic actuator; 6. Accumulator; 7. Oil pressure sensor; 8. Filter. Detailed Implementation

[0018] First, those skilled in the art should understand that these embodiments are merely used to explain the technical principles of the embodiments of this application and are not intended to limit the scope of protection of the embodiments of this application. Those skilled in the art can make adjustments as needed to adapt to specific application scenarios.

[0019] In the description of the embodiments of this application, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; 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. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this application based on the specific circumstances.

[0020] In the embodiments of this application, unless otherwise expressly 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," "on top of," and "over" 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.

[0021] The present application will now be described in further detail with reference to the accompanying drawings and specific embodiments.

[0022] See Figure 1 and Figure 2This application discloses a hydraulic control system, including an oil tank 1, a power pump 2, a cartridge-type integrated mechanical valve 3, a pressure regulating solenoid valve 4, a hydraulic actuator 5, and an electronic control unit. The oil tank 1 is connected to the power pump 2 and supplies oil to the hydraulic actuator 5 through the power pump 2. The oil inlet P port 31 of the cartridge-type integrated mechanical valve 3 is connected to the oil outlet of the power pump 2, and the oil outlet A port 32 of the cartridge-type integrated mechanical valve 3 is connected to the hydraulic actuator 5, for providing the hydraulic actuator 5 with a large flow of pressure-adjustable oil. The oil inlet of the pressure regulating solenoid valve 4 is connected to the oil outlet of the power pump 2, and the oil outlet of the pressure regulating solenoid valve 4 is connected to the cartridge-type integrated mechanical valve 3, for regulating the oil pressure at the oil outlet of the cartridge-type integrated mechanical valve 3. The electronic control unit is electrically connected to the pressure regulating solenoid valve 4, for regulating the oil pressure at the oil outlet of the pressure regulating solenoid valve 4.

[0023] Specifically, the cartridge-type integrated mechanical valve 3 adopts a two-position three-way cartridge valve structure, which controls the oil circuit opening and closing through axial displacement; the pressure regulating solenoid valve 4 can be a proportional solenoid valve, which can realize continuous oil pressure regulation; the electronic control unit can include a PID controller, which realizes closed-loop control by collecting pressure feedback signals; the power pump 2 can be a gear pump, vane pump or piston pump, which can dynamically adjust the output flow according to system requirements, and the oil outlet of the power pump 2 is equipped with a check valve; the hydraulic actuator 5 can be a hydraulic cylinder or a hydraulic motor, which can be selected according to the application scenario.

[0024] As mentioned above, the cartridge-type integrated mechanical valve 3 is responsible for controlling the on / off flow of high-flow oil, while the pressure regulating solenoid valve 4 focuses on precise oil pressure regulation. The combination of the two ensures both the high flow rate requirement of the system and precise pressure control. Compared with existing technologies, this solution significantly improves the response speed and output power of the hydraulic actuator 5, especially showing obvious advantages in application scenarios that require rapid pressure build-up and high flow rate supply. At the same time, through the intelligent adjustment of the electronic control unit, the system can dynamically adjust the pressure parameters according to the actual working conditions, further optimizing the control performance.

[0025] See also Figure 2In this embodiment, the cartridge-type integrated mechanical valve 3 includes a valve body, a normally closed valve core 33, and a spring 34. The valve body is provided with an oil inlet P port 31 and an oil outlet A port 32. The normally closed valve core 33 is slidably disposed in the valve body along the axial direction. The normally closed valve core 33 is provided with an oil guide channel 35 for connecting the oil inlet P port 31 and the oil outlet A port 32. The normally closed valve core 33 divides the interior of the valve body into a left position cavity and a right position cavity along the axial direction. The spring 34 is disposed in the left position cavity to drive the normally closed valve core 33 to move towards the right position cavity, so that the oil inlet P port 31 and the oil outlet A port 32 are disconnected. The right position cavity is connected to the oil outlet of the pressure regulating solenoid valve 4. The oil from the oil outlet of the pressure regulating solenoid valve 4 drives the normally closed valve core 33 to move towards the left position cavity, so that the oil inlet P port 31 and the oil outlet A port 32 are connected to each other through the oil guide channel 35. Specifically, the valve body is made of high-strength alloy, and its internal structure is precision-machined to ensure smooth movement of the normally closed valve core 33. The spring 34 can be made of stainless steel, and its preload can be precisely adjusted via an adjusting screw. A high-pressure hose connects the right-position chamber to the pressure regulating solenoid valve 4, and a quick connector is provided at the connection for easy maintenance. The dynamic balance between the force of the spring 34 and the hydraulic force ensures the precise displacement of the normally closed valve core 33. Compared with existing technologies, this solution combines the small-flow control advantage of solenoid valves with the large-flow throughput capacity of mechanical valves, retaining the rapid response characteristics of electromagnetic control while solving the problem of insufficient flow in traditional single solenoid valves. Specifically, when the actuator requires a large flow of oil, the pressure regulating solenoid valve 4 only needs to output a small flow of control oil pressure to open the normally closed valve core 33, allowing the main oil circuit to directly achieve a large flow rate through the mechanical valve. When it is necessary to cut off the oil circuit, the force of the spring 34 causes the normally closed valve core 33 to quickly reset, avoiding the delay problem caused by flow limitation in traditional solenoid valves.

[0026] In this embodiment, the valve body is also provided with a feedback oil passage 36, the two ends of which are connected to the oil outlet A port 32 and the left position cavity, respectively. That is, the pressure oil of the oil outlet A port 32 is introduced into the left position cavity in real time through the feedback oil passage 36, so that the oil pressure in the left position cavity and the pressure of the oil outlet A port 32 are dynamically balanced.

[0027] In this embodiment, an accumulator 6 for stabilizing oil pressure is provided between the oil outlet and the right-side chamber of the pressure regulating solenoid valve 4. Specifically, the accumulator 6 is a device capable of storing hydraulic energy and releasing it when needed. In the hydraulic system, the accumulator 6 can absorb pressure fluctuations and maintain system pressure stability. When the hydraulic actuator 5 requires a rapid response, the accumulator 6 can quickly replenish the oil, preventing pressure drops caused by the flow restriction of the pressure regulating solenoid valve 4; and when the hydraulic actuator 5 stops working, the accumulator 6 can absorb excess oil pressure, preventing a sudden rise in system pressure. Therefore, this solution not only improves the response speed and stability of the hydraulic actuator 5, but also reduces the workload of the pressure regulating solenoid valve 4 and extends its service life.

[0028] In this embodiment, an oil pressure sensor 7 is provided between the oil outlet A port 32 and the hydraulic actuator 5, and the oil pressure sensor 7 is electrically connected to the electronic control unit. Specifically, the oil pressure sensor 7 can be a piezoresistive, piezoelectric, or capacitive pressure sensing element, and is installed in the oil inlet line of the hydraulic actuator 5. That is, by monitoring the oil inlet pressure of the hydraulic actuator 5 in real time, the pressure signal is fed back to the electronic control unit to form a closed-loop control.

[0029] In this embodiment, a filter 8 for filtering the hydraulic fluid is provided between the oil tank 1 and the power pump 2. Specifically, the filter 8 prevents solid particulate contaminants in the hydraulic fluid from entering the power pump 2 and subsequent hydraulic components by intercepting them. This solves the problem of component wear caused by hydraulic fluid contamination in the hydraulic system, significantly extends the service life of components such as the power pump 2, and maintains the stability of the system's operating pressure.

[0030] In this embodiment, the valve body is also provided with a return oil T-port 37, which is connected to the oil tank 1. The normally closed valve core 33 is provided with a return oil channel 38 for connecting the return oil T-port 37 and the oil outlet A-port 32. By adding a return oil channel, the hydraulic actuator 5 can quickly discharge the oil back to the oil tank 1 during the pressure relief phase. That is, when the normally closed valve core 33 is reset under the action of the spring 34, the oil outlet A-port 32 is connected to the return oil T-port 37 through the return oil channel 38, and the oil in the cavity of the hydraulic actuator 5 quickly flows back to the oil tank 1 under the action of the pressure difference, thus completing the reset action of the hydraulic actuator 5 more quickly and significantly improving the system's response speed and working efficiency.

[0031] In the description of the embodiments of this application, it should be noted that the terms "inner" and "outer" and other terms indicating direction or positional relationship are based on the direction or positional relationship shown in the drawings. This is only for the convenience of description and does not indicate or imply that the device or component must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation of this application.

[0032] In the description of this application, the references to terms such as "an embodiment," "some embodiments," "in this embodiment," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this application. 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 a suitable manner in any 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.

[0033] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A hydraulic control system, characterized in that, Includes oil tank, power pump, cartridge integrated mechanical valve, pressure regulating solenoid valve, hydraulic actuator and electrical control unit; The oil tank is connected to the power pump, and the power pump supplies oil to the hydraulic actuator. The inlet P port of the cartridge-type integrated mechanical valve is connected to the outlet port of the power pump, and the outlet A port of the cartridge-type integrated mechanical valve is connected to the hydraulic actuator to provide the hydraulic actuator with a large flow of pressure-adjustable oil. The oil inlet of the pressure regulating solenoid valve is connected to the oil outlet of the power pump, and the oil outlet of the pressure regulating solenoid valve is connected to a cartridge-type integrated mechanical valve for regulating the oil pressure at the oil outlet of the cartridge-type integrated mechanical valve. The electronic control unit is electrically connected to the pressure regulating solenoid valve and is used to regulate the oil pressure at the outlet of the pressure regulating solenoid valve.

2. The hydraulic control system according to claim 1, characterized in that, The cartridge-type integrated mechanical valve includes a valve body, a normally closed valve core, and a spring. The valve body has an inlet port P and an outlet port A. The normally closed valve core is slidably disposed within the valve body along the axial direction. The normally closed valve core has an oil guide channel for connecting the inlet port P and the outlet port A. The normally closed valve core divides the interior of the valve body into a left position chamber and a right position chamber along the axial direction. The spring is disposed in the left position chamber to drive the normally closed valve core to move towards the right position chamber, thereby disconnecting the inlet port P and the outlet port A. The right position chamber is connected to the outlet of a pressure regulating solenoid valve. The oil from the outlet of the pressure regulating solenoid valve drives the normally closed valve core to move towards the left position chamber, thereby connecting the inlet port P and the outlet port A through the oil guide channel.

3. The hydraulic control system according to claim 2, characterized in that, The valve body is also provided with a feedback oil passage, and the two ends of the feedback oil passage are respectively connected to the oil outlet A port and the left position cavity.

4. The hydraulic control system according to claim 2, characterized in that, An accumulator for stabilizing oil pressure is provided between the oil outlet and the right-side chamber of the pressure regulating solenoid valve.

5. The hydraulic control system according to claim 1, characterized in that, An oil pressure sensor is installed between the oil outlet A port and the hydraulic actuator, and the oil pressure sensor is electrically connected to the electronic control unit.

6. The hydraulic control system according to claim 1, characterized in that, A filter for filtering oil is provided between the oil tank and the power pump.

7. The hydraulic control system according to claim 2, characterized in that, The valve body is also provided with an oil return port T, which is connected to the oil tank. The normally closed valve core is provided with an oil return channel for connecting the oil return port T and the oil outlet port A.

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