Active and passive dual-mode control system of hydraulic actuator

Abstract

The utility model relates to the technical field of hydraulic systems, in particular to an active and passive dual-mode control system of a hydraulic actuator, which comprises an oil cylinder, a hydraulic actuator, a control system and a control system, and is characterized in that the oil cylinder is provided with a rodless cavity and a rod cavity; the reversing valve is used for switching the direction of an oil way so as to control the oil cylinder to extend or retract; the first speed regulating valve and the second speed regulating valve are connected in series in an oil path of the reversing valve and are used for respectively regulating the extension speed and the retraction speed of the oil cylinder; the first balance valve and the second balance valve are connected to the first speed regulating valve and the second speed regulating valve in parallel and used for stabilizing the action of the oil cylinder under the negative load working condition; switching between an active operation mode and a passive maintenance mode can be achieved, in the active mode, the stretching and retracting speed and direction of the oil cylinder can be accurately controlled, the power output requirements under various working conditions are met, in the passive mode, the oil cylinder can be rapidly decompressed to enter a floating state, and the service life of the oil cylinder is prolonged. And maintenance, debugging and overhaul of equipment are facilitated.

Description

Technical Field

[0001] This application relates to the field of hydraulic system technology, and in particular to an active and passive dual-mode control system for a hydraulic actuator. Background Technology

[0002] In modern industrial production and mechanical equipment operation, hydraulic actuators, as key power output devices, are widely used in many fields such as engineering machinery, ships, and aerospace.

[0003] However, existing hydraulic actuators cannot quickly bring the cylinders to a safe state during equipment maintenance and debugging, making operation extremely inconvenient. Furthermore, traditional systems exhibit cylinder vibration under heavy load conditions, such as when a crane lowers a heavy object or a hydraulic lifting platform descends, which can damage the equipment and pose safety hazards. This project aims to develop an active and passive dual-mode control system for hydraulic actuators to solve these problems. Utility Model Content

[0004] In view of at least one of the above technical problems, this application provides an active and passive dual-mode control system for a hydraulic actuator, adopting the following technical solution to solve the above problems.

[0005] According to one aspect of this application, an active and passive dual-mode control system for a hydraulic actuator is provided, comprising:

[0006] Hydraulic cylinder, having rodless chamber and rod chamber;

[0007] A directional valve is used to switch the direction of the oil circuit to control the extension or retraction of the hydraulic cylinder.

[0008] The first speed control valve and the second speed control valve are connected in series in the oil circuit of the directional valve to adjust the extension speed and retraction speed of the oil cylinder, respectively.

[0009] The first balance valve and the second balance valve are connected in parallel with the first speed control valve and the second speed control valve, and are used to stabilize the cylinder operation under negative load conditions.

[0010] The first and second solenoid ball valves are connected in parallel to the directional valve to pre-release the rodless chamber and rod chamber of the oil cylinder respectively, so that they are in a depressurized state.

[0011] The first solenoid valve and the second solenoid valve are linked to the first hydraulic check valve and the second hydraulic check valve respectively, and are used to control the opening and closing of the first hydraulic check valve and the second hydraulic check valve.

[0012] The oil return port is connected to the oil cylinder through a first hydraulic check valve and a second hydraulic check valve.

[0013] Preferably, the reversing valve has an inlet, a first outlet, a second outlet, and a third outlet. The inlet is connected to the pressure oil port, the first outlet is connected to the return oil port, the second outlet is connected to the rodless chamber interface of the cylinder, and the third outlet is connected to the rod chamber interface of the cylinder. The bidirectional action of the cylinder is achieved by switching the on and off states of the second outlet and the third outlet.

[0014] Preferably, the opening of the first speed control valve and the second speed control valve is adjustable to control the extension speed and retraction speed of the hydraulic cylinder, respectively, and the installation positions of the first speed control valve and the second speed control valve are located between the reversing valve and the rodless chamber interface and the rod chamber interface of the hydraulic cylinder.

[0015] Preferably, the first and second balance valves are set in the same direction as the movement direction of the hydraulic cylinder, which is used to prevent vibration through unidirectional throttling when the hydraulic cylinder is under a negative load.

[0016] Preferably, the first solenoid ball valve and the second solenoid ball valve are connected to the rodless chamber and the rod chamber of the cylinder respectively through parallel oil circuits, and are used to open and release the pressure in the rodless chamber and the rod chamber of the cylinder when energized, so that the cylinder is in a depressurized state.

[0017] Preferably, the first hydraulic check valve and the second hydraulic check valve achieve reverse conduction through the control of the first solenoid valve and the second solenoid valve. When the first hydraulic check valve and the second hydraulic check valve open in reverse, the rodless chamber interface and the rod chamber interface of the cylinder are connected through the oil return port, and the cylinder enters a floating state.

[0018] Preferably, it also includes a pressure sensor, which is installed on the inlet and outlet circuit of the oil cylinder to monitor the internal pressure of the oil cylinder in real time and feed the signal back to the control system to dynamically adjust the working status of the directional valve, the first speed control valve and the second speed control valve, as well as the first solenoid ball valve and the second solenoid ball valve.

[0019] Preferably, it also includes a safety relief valve, which is connected in series between the pressure oil port and the directional valve, for automatically relieving pressure when the system pressure exceeds a preset threshold.

[0020] This application has the following technical effects: This application can realize the switching between two modes: active operation and passive maintenance. In active mode, it can accurately control the extension and retraction speed and direction of the hydraulic cylinder to meet the power output requirements under various working conditions, making it more stable and less prone to vibration under heavy load conditions. In passive mode, the hydraulic cylinder can quickly depressurize and enter a floating state, which facilitates the maintenance, debugging and repair of the equipment. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0022] Figure 1 This is a system architecture diagram of this application.

[0023] Figure label:

[0024] 1. Pressure oil port; 2. Return oil port; 3. Directional control valve; 4. First speed control valve; 5. Second speed control valve; 6. First balance valve; 7. Second balance valve; 8. First solenoid ball valve; 9. Second solenoid ball valve; 10. Rodless chamber interface of hydraulic cylinder; 11. Rod chamber interface of hydraulic cylinder; 12. First hydraulic check valve; 13. Second hydraulic check valve; 14. First solenoid valve; 15. Second solenoid valve; 16. Hydraulic cylinder. Detailed Implementation

[0025] Please see Figure 1 It should be understood that the structures, proportions, sizes, etc., illustrated in the accompanying drawings are merely for illustrative purposes to aid those skilled in the art and to facilitate understanding and reading. They are not intended to limit the scope of the invention and therefore have no substantial technical significance. Any modifications to the structure, changes in proportions, or adjustments to size, without affecting the effectiveness and objectives of the invention, should still fall within the scope of the technical content disclosed herein. Furthermore, the technical terms used in this specification are merely for clarity and not intended to limit the scope of the invention. Changes or adjustments to their relative relationships, without substantially altering the technical content, should also be considered within the scope of the invention's implementation.

[0026] The specific embodiments of this application will now be described in detail with reference to the accompanying drawings. Numerous specific details are set forth in the following description to provide a thorough understanding of this application.

[0027] In this embodiment of the application, as Figure 1 A dual-mode control system for a hydraulic actuator, comprising active and passive modes, is provided, including:

[0028] Hydraulic cylinder 16 has a rodless chamber and a rod chamber;

[0029] The reversing valve 3 is used to switch the direction of the oil circuit to control the extension or retraction of the oil cylinder 16;

[0030] The first speed control valve 4 and the second speed control valve 5 are connected in series in the oil circuit of the reversing valve 3 to adjust the extension speed and retraction speed of the oil cylinder 16 respectively.

[0031] The first balance valve 6 and the second balance valve 7 are connected in parallel to the first speed control valve 4 and the second speed control valve 5, and are used to stabilize the operation of the oil cylinder 16 under negative load conditions.

[0032] The first electromagnetic ball valve 8 and the second electromagnetic ball valve 9 are connected in parallel to the directional valve 3 to pre-release the rodless chamber and rod chamber of the oil cylinder 16 respectively, so that they are in a depressurized state.

[0033] The first solenoid valve 14 and the second solenoid valve 15 are linked with the first hydraulic check valve 12 and the second hydraulic check valve 13 respectively, and are used to control the opening and closing of the first hydraulic check valve 12 and the second hydraulic check valve 13.

[0034] The oil return port 2 is connected to the oil cylinder 16 through the first hydraulic check valve 12 and the second hydraulic check valve 13.

[0035] It should be noted that this solution achieves precise control of the cylinder 16's movement through the coordinated operation of components such as directional valve 3, first speed control valve 4 and second speed control valve 5, first balance valve 6 and second balance valve 7, first solenoid ball valve 8 and second solenoid ball valve 9, first hydraulic check valve 12 and second hydraulic check valve 13. In active mode, directional valve 3 switches the oil circuit direction, first speed control valve 4 and second speed control valve 5 adjust the extension and retraction speeds of cylinder 16 respectively, and first balance valve 6 and second balance valve 7 ensure stability under heavy load conditions. In passive mode, first solenoid ball valve 8 and second solenoid ball valve 9 pre-depressurize, and first solenoid valve 14 and second solenoid valve 15 control first hydraulic check valve 12 and second hydraulic check valve 13 to reverse the flow, allowing the rodless chamber and rod chamber of cylinder 16 to connect through return port 2, entering a floating state. This architecture achieves precise bidirectional control of cylinder 16, supports switching between active operation and passive maintenance modes, and the multi-valve redundancy design improves the system's safety and reliability.

[0036] In one embodiment of this application, the reversing valve 3 has an inlet, a first outlet, a second outlet, and a third outlet. The inlet is connected to the pressure oil port 1, the first outlet is connected to the return oil port 2, the second outlet is connected to the rodless chamber interface 10 of the cylinder, and the third outlet is connected to the rod chamber interface 11 of the cylinder. The bidirectional operation of the cylinder 16 is achieved by switching the on / off states of the second outlet and the third outlet.

[0037] It should be noted that the inlet of the reversing valve 3 is connected to the pressure oil port 1 to introduce pressure oil, the first outlet is connected to the return oil port 2 to achieve oil return, the second outlet is connected to the rodless chamber interface 10 of the cylinder, and the third outlet is connected to the rod chamber interface 11 of the cylinder. By switching the on / off state of the second and third outlets, when the second outlet is connected to the inlet and the third outlet is connected to the first outlet, pressure oil enters the rodless chamber of the cylinder 16, and oil returns from the rod chamber, causing the cylinder 16 to extend; conversely, it retracts. This design simplifies the oil circuit switching logic, achieves efficient control of the bidirectional movement of the cylinder 16, and reduces the system complexity.

[0038] In one embodiment of this application, the opening of the first speed control valve 4 and the second speed control valve 5 is adjustable to control the extension speed and retraction speed of the hydraulic cylinder 16, respectively, and the installation positions of the first speed control valve 4 and the second speed control valve 5 are located between the reversing valve 3 and the rodless chamber interface 10 and the rod chamber interface 11 of the hydraulic cylinder.

[0039] It should be noted that the first speed control valve 4 and the second speed control valve 5 are connected in series between the reversing valve 3 and the rodless chamber interface 10 and the rod chamber interface 11 of the hydraulic cylinder, respectively. Internally, each valve consists of a pressure reducing valve and a throttle valve. The flow rate is changed by adjusting the opening of the throttle valve, and the pressure reducing valve automatically stabilizes the pressure difference across the throttle valve, ensuring stable flow. By adjusting the opening of the two speed control valves separately, the extension and retraction speeds of the hydraulic cylinder 16 can be independently controlled, solving the problem that a traditional single speed control valve cannot simultaneously meet bidirectional speed regulation requirements.

[0040] In one embodiment of this application, the first balance valve 6 and the second balance valve 7 are arranged in the same direction as the movement direction of the hydraulic cylinder 16, and are used to prevent vibration by unidirectional throttling when the hydraulic cylinder 16 is subjected to a negative load.

[0041] It should be noted that the first balance valve 6 and the second balance valve 7 are connected in parallel to the first speed control valve 4 and the second speed control valve 5, and their orientation is consistent with the movement direction of the hydraulic cylinder 16, employing a one-way throttling structure. When the hydraulic cylinder 16 is under a negative load, such as when a crane lowers a heavy object, the load causes the pressure in the rod chamber of the hydraulic cylinder 16 to increase. After sensing the pressure change, the first balance valve 6 and the second balance valve 7 limit the return oil speed through one-way throttling, preventing the hydraulic cylinder 16 from overspeeding or vibrating due to the load, thus enhancing the stability and reliability of the system under complex working conditions.

[0042] In one embodiment of this application, the first electromagnetic ball valve 8 and the second electromagnetic ball valve 9 are connected to the rodless chamber and the rod chamber of the oil cylinder 16 respectively through parallel oil circuits, and are used to open and release the pressure in the rodless chamber and the rod chamber of the oil cylinder 16 when energized, so that the oil cylinder 16 is in a depressurized state.

[0043] It should be noted that the first solenoid ball valve 8 and the second solenoid ball valve 9 are connected to the rodless chamber and rod chamber of the cylinder 16 respectively via parallel oil circuits, and are installed on the parallel branch of the first speed regulating valve 4 and the second speed regulating valve 5 with the rodless chamber interface 10 and the rod chamber interface 11 of the cylinder. When the first solenoid ball valve 8 and the second solenoid ball valve 9 are energized, the electromagnet generates electromagnetic force to attract the valve core to move, the valve opens, and the pressure oil in the two chambers of the cylinder 16 quickly flows back through the return oil port 2 to release pressure, so that the cylinder 16 is in a depressurized state, which facilitates equipment maintenance and debugging and avoids the safety risks caused by high pressure residue.

[0044] In one embodiment of this application, the first hydraulic check valve 12 and the second hydraulic check valve 13 are reverse-directed by the control of the first solenoid valve 14 and the second solenoid valve 15. When the first hydraulic check valve 12 and the second hydraulic check valve 13 are opened in reverse, the rodless chamber interface 10 and the rod chamber interface 11 of the cylinder are connected through the oil return port 2, and the cylinder 16 enters a floating state.

[0045] It should be noted that the first solenoid valve 14 and the second solenoid valve 15 are linked with the first hydraulic control check valve 12 and the second hydraulic control check valve 13 respectively. Under normal conditions, the first hydraulic control check valve 12 and the second hydraulic control check valve 13 prevent the oil from flowing in the opposite direction. When the first solenoid valve 14 and the second solenoid valve 15 are energized, control oil enters the hydraulic control device, causing the first hydraulic control check valve 12 and the second hydraulic control check valve 13 to open in the opposite direction. At this time, the rodless chamber interface 10 and the rod chamber interface 11 of the hydraulic cylinder 16 are connected through the oil return port 2, and the hydraulic cylinder 16 can move freely under the action of external force to meet the requirements of the movement state of the hydraulic cylinder 16 under special working conditions.

[0046] In one embodiment of this application, a pressure sensor is also included, which is disposed on the inlet and outlet circuit of the hydraulic cylinder 16, for real-time monitoring of the internal pressure of the hydraulic cylinder 16 and feeding the signal back to the control system to dynamically adjust the working state of the reversing valve 3, the first speed regulating valve 4 and the second speed regulating valve 5, as well as the first solenoid ball valve 8 and the second solenoid ball valve 9.

[0047] It should be noted that the pressure sensor is installed on the inlet and outlet circuit of the hydraulic cylinder 16. Based on the piezoresistive or piezoelectric effect, it converts the pressure signal into an electrical signal, monitors the internal pressure of the hydraulic cylinder 16 in real time, and feeds it back to the control system. The control system dynamically adjusts the working status of components such as the reversing valve 3, the first speed control valve 4, the second speed control valve 5, the first solenoid ball valve 8, and the second solenoid ball valve 9 according to the pressure signal. For example, if the pressure is too high, the speed control valve is adjusted to reduce the flow rate, or the solenoid ball valve is controlled to release pressure. This realizes real-time monitoring and closed-loop control of the operating status of the hydraulic cylinder 16, improving the system response speed and fault early warning capability.

[0048] In one embodiment of this application, a safety relief valve is also included, which is connected in series between the pressure oil port 1 and the reversing valve 3, for automatically relieving pressure when the system pressure exceeds a preset threshold.

[0049] It should be noted that the safety relief valve is connected in series between the pressure oil port 1 and the reversing valve 3. It consists of a valve body, a valve core, and a spring, and the pressure threshold is set by the spring force. When the system pressure is normal, the valve core closes under the action of the spring force to prevent oil overflow. When the system pressure exceeds the preset threshold, the oil pressure overcomes the spring force to open the valve core, and the excess oil flows back to the return port 2 through the safety relief valve to relieve pressure, preventing the system from being damaged by excessive pressure and ensuring the safety and long-term stability of the system operation.

[0050] Active mode working principle: When the system is in active mode, pressurized oil enters the directional valve 3 from the pressurized oil port 1. By controlling the position of the valve core of the directional valve 3, the oil circuit direction is switched, thereby controlling the extension or retraction of the cylinder 16. Specifically, when the directional valve 3 is switched to a specific position, connecting the second outlet with the inlet and the third outlet with the first outlet, pressurized oil enters the rodless chamber of the cylinder 16 through the second outlet and the first speed control valve 4, pushing the piston rod to extend. At the same time, the oil in the rod chamber of the cylinder 16 flows back to the return port 2 through the third outlet, the second speed control valve 5, and the first outlet. Conversely, when the directional valve 3 is switched to another position, pressurized oil enters the rod chamber, realizing the retraction of the cylinder 16. During this process, the first speed control valve 4 and the second speed control valve 5 respectively adjust the extension and retraction speed of the cylinder 16, control the flow rate by adjusting the opening of its internal throttle valve, and the pressure reducing valve automatically stabilizes the pressure difference before and after the throttle valve to ensure stable flow. When the hydraulic cylinder 16 is under a negative load, the first balance valve 6 and the second balance valve 7 come into play. Their one-way throttling structure limits the return oil speed, preventing the hydraulic cylinder 16 from dropping too fast or shaking due to the load, thus ensuring the stable operation of the system.

[0051] Passive mode working principle: In passive mode, firstly, the first solenoid ball valve 8 and the second solenoid ball valve 9 are energized, opening the oil circuits connecting the rodless chamber and the rod chamber of cylinder 16 respectively. This allows the pressurized oil in both chambers of cylinder 16 to quickly return through the return port 2, achieving pre-pressure relief and placing cylinder 16 in a pressure-free state. Next, the first solenoid valve 14 and the second solenoid valve 15 are energized, controlling the first hydraulic check valve 12 and the second hydraulic check valve 13 to reverse their conduction. At this time, the rodless chamber interface 10 and the rod chamber interface 11 of cylinder 16 are connected through the return port 2, and cylinder 16 enters a floating state, allowing it to move freely under external force, facilitating equipment maintenance and debugging or meeting special working conditions.

[0052] The above are merely preferred embodiments of this application and do not constitute any limitation on this application. Any person skilled in the art can make many possible variations and modifications to the technical solution of this application, or modify it into equivalent embodiments, without departing from the scope of the technical solution of this application. Therefore, all equivalent changes made based on the shape, structure, and principle of this application without departing from the content of the technical solution of this application should be covered within the protection scope of this application.

Claims

1. A dual-mode control system for a hydraulic actuator, characterized in that, include: The hydraulic cylinder (16) has a rodless chamber and a rod chamber; The reversing valve (3) is used to switch the direction of the oil circuit to control the extension or retraction of the oil cylinder (16); The first speed control valve (4) and the second speed control valve (5) are connected in series in the oil circuit of the reversing valve (3) to adjust the extension speed and retraction speed of the oil cylinder (16) respectively. The first balance valve (6) and the second balance valve (7) are connected in parallel to the first speed control valve (4) and the second speed control valve (5) to stabilize the operation of the oil cylinder (16) under negative load conditions. The first electromagnetic ball valve (8) and the second electromagnetic ball valve (9) are connected in parallel to the reversing valve (3) to pre-release the rodless chamber and the rod chamber of the oil cylinder (16) respectively, so that they are in a pressureless state; The first solenoid valve (14) and the second solenoid valve (15) are linked with the first hydraulic check valve (12) and the second hydraulic check valve (13) respectively, and are used to control the opening and closing of the first hydraulic check valve (12) and the second hydraulic check valve (13); The return port (2) is connected to the oil cylinder (16) through the first hydraulic check valve (12) and the second hydraulic check valve (13).

2. The active and passive dual-mode control system for a hydraulic actuator according to claim 1, characterized in that: The reversing valve (3) has an inlet, a first outlet, a second outlet and a third outlet. The inlet is connected to the pressure oil port (1), the first outlet is connected to the return oil port (2), the second outlet is connected to the rodless chamber interface (10) of the cylinder, and the third outlet is connected to the rod chamber interface (11) of the cylinder. The cylinder (16) can be moved bidirectionally by switching the on and off states of the second outlet and the third outlet.

3. The active and passive dual-mode control system for a hydraulic actuator according to claim 1, characterized in that: The opening of the first speed control valve (4) and the second speed control valve (5) is adjustable to control the extension speed and retraction speed of the cylinder (16) respectively. The installation positions of the first speed control valve (4) and the second speed control valve (5) are located between the reversing valve (3) and the rodless chamber interface (10) and the rod chamber interface (11) of the cylinder.

4. The active and passive dual-mode control system for a hydraulic actuator according to claim 1, characterized in that: The first balance valve (6) and the second balance valve (7) are set in the same direction as the movement direction of the oil cylinder (16) to prevent shaking by unidirectional throttling when the oil cylinder (16) is under negative load.

5. The active and passive dual-mode control system for a hydraulic actuator according to claim 1, characterized in that: The first electromagnetic ball valve (8) and the second electromagnetic ball valve (9) are connected to the rodless chamber and the rod chamber of the oil cylinder (16) respectively through parallel oil circuits. They are used to open and release the pressure of the rodless chamber and the rod chamber of the oil cylinder (16) when energized, so that the oil cylinder (16) is in a pressure-free state.

6. The active and passive dual-mode control system for a hydraulic actuator according to claim 1, characterized in that: The first hydraulic check valve (12) and the second hydraulic check valve (13) are reverse-directed by the control of the first solenoid valve (14) and the second solenoid valve (15). When the first hydraulic check valve (12) and the second hydraulic check valve (13) are opened in reverse, the rodless chamber interface (10) and the rod chamber interface (11) of the cylinder are connected through the return port (2), and the cylinder (16) enters the floating state.

7. The active and passive dual-mode control system for a hydraulic actuator according to claim 1, characterized in that: It also includes a pressure sensor, which is installed on the inlet and outlet circuit of the oil cylinder (16) to monitor the internal pressure of the oil cylinder (16) in real time and feed the signal back to the control system to dynamically adjust the working status of the reversing valve (3), the first speed control valve (4) and the second speed control valve (5), as well as the first solenoid ball valve (8) and the second solenoid ball valve (9).

8. The active and passive dual-mode control system for a hydraulic actuator according to claim 1, characterized in that: It also includes a safety relief valve, which is connected in series between the pressure oil port (1) and the reversing valve (3) to automatically relieve pressure when the system pressure exceeds a preset threshold.

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