Hydraulic control system of people ascending three-way stacking machine

Abstract

The utility model discloses a hydraulic control system of a three-way stacker for people to go up, which relates to the technical field of logistics storage and comprises a hydraulic power mechanism, an actuating mechanism connected with the hydraulic power mechanism and a control valve mechanism connected with the hydraulic power mechanism and the actuating mechanism, the hydraulic power mechanism conveys hydraulic oil to the executing mechanism through the control valve mechanism. According to the hydraulic control system of the human ascending three-way stacking machine, modular design is adopted, the executing mechanism comprises at least one oil cylinder, the lifting requirements of different stacking machines can be flexibly met, and the hydraulic control system is suitable for storage and carrying scenes of various goods. The intelligent control and efficient response characteristics of the system are especially suitable for application requirements in the field of efficient and intelligent warehousing.

Description

Technical Field

[0001] This utility model relates to the field of logistics and warehousing technology, specifically to a hydraulic control system for a three-way stacker crane with a human-mounted upward movement. Background Technology

[0002] As a highly efficient and intelligent warehousing equipment, the three-way stacker crane with upward movement can be widely used in various storage and handling scenarios for goods. Traditional stacker cranes mainly rely on hydraulic systems to complete lifting and handling operations, playing an important role in the logistics and warehousing field.

[0003] However, these traditional equipment have revealed some problems and shortcomings in use. First, the lifting and lowering operation precision of traditional stacker cranes is relatively low, especially when making small-scale positioning adjustments, making it difficult to achieve high-precision control. This deficiency not only reduces the efficiency of goods storage and retrieval but may also lead to the accumulation of goods positioning errors, thus affecting the accuracy and smoothness of overall logistics operations. Second, the response speed of the hydraulic system of traditional stacker cranes is slow, especially when facing frequent starts and stops or load changes. The hydraulic control system is prone to delays and cannot quickly adjust to the target state. This lag directly affects the efficiency of warehousing operations and makes it difficult to meet the demands of the modern warehousing industry for high-efficiency operations. In addition, due to the relatively simple design of traditional hydraulic control systems, they lack the ability to accurately adjust the operating status and provide real-time feedback, which can easily lead to unstable control under complex operating conditions and even reduce the safety of equipment operation. Utility Model Content

[0004] The purpose of this invention is to provide a hydraulic control system for a three-way stacker crane that can effectively solve the shortcomings of traditional equipment in terms of accuracy, response speed and control stability, while improving the intelligence level of warehousing equipment.

[0005] To achieve the above objectives, this utility model provides the following technical solution: a hydraulic control system for a three-way stacker crane with upward movement of personnel, the system comprising:

[0006] Hydraulic power mechanism;

[0007] The actuator connected to the hydraulic power mechanism;

[0008] Control valve mechanism connected to hydraulic power mechanism and actuator;

[0009] The hydraulic power mechanism delivers hydraulic oil to the actuator through a control valve mechanism.

[0010] Preferably, the hydraulic power mechanism includes a gear pump, which is connected to a pump motor and an oil tank.

[0011] Preferably, the actuator includes at least one hydraulic cylinder.

[0012] Preferably, the control valve mechanism includes at least one solenoid valve, which is connected to a gear pump, and the solenoid valve is connected to a bidirectional flow limiting valve, which is connected to a one-way valve.

[0013] Preferably, the one-way valve is connected to the hydraulic cylinder.

[0014] Preferably, the gear pump is connected to an oil filter, the oil filter is connected to an overflow valve, and the overflow valve is connected to a two-way flow limiting valve and a solenoid valve.

[0015] Preferably, one of the solenoid valves is connected to a pressure-compensated proportional valve, which is connected to the hydraulic cylinder.

[0016] As can be seen from the above technical solution, this utility model has the following beneficial effects:

[0017] The hydraulic control system of this three-way stacker crane utilizes a combination of pressure-compensated proportional valves and solenoid valves. This allows for precise adjustment of the hydraulic oil flow and velocity based on analog signals from the control handle, improving the lifting accuracy of the cylinders. High-precision control is particularly effective for small-amplitude positioning adjustments, significantly reducing cargo positioning errors and enhancing overall logistics accuracy. The design employs a gear pump, bidirectional flow-limiting valve, and solenoid valve for coordinated control. By optimizing hydraulic circuit switching and flow regulation, it effectively reduces the response delay of traditional hydraulic systems, significantly improving the stacker crane's reaction speed in scenarios with frequent starts and stops or load changes. This meets the demands of modern logistics warehousing for high-efficiency operations. Furthermore, the use of check valves, relief valves, and bidirectional flow-limiting valves ensures stable hydraulic circuit pressure under complex operating conditions, preventing control instability caused by pressure fluctuations or hydraulic oil backflow, thus improving system reliability. Furthermore, the bidirectional flow-limiting valve design, which closes upon power failure, automatically cuts off the oil circuit in the event of a power outage, ensuring equipment safety. The system is equipped with an overflow valve and an emergency operation channel. If the solenoid valve or proportional valve in the descent oil circuit malfunctions, manual operation can ensure the oil return path of the cylinder remains unobstructed, enabling emergency descent of the gantry and ensuring normal operation and safety. The oil filter and overflow valve effectively filter impurities in the hydraulic oil and promptly release pressure when the system is overloaded, reducing the load on the gear pump and other hydraulic components, thereby extending the service life of the hydraulic system and improving overall system energy efficiency. The system adopts a modular design, with the actuator containing at least one cylinder, allowing for flexible adaptation to the lifting requirements of different stacker cranes and making it suitable for various cargo storage and handling scenarios. Its intelligent control and high-efficiency response characteristics are particularly suitable for applications in the field of efficient and intelligent warehousing. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the overall structure of this utility model.

[0019] In the diagram: 1. Hydraulic power mechanism; 11. Gear pump; 12. Oil filter; 2. Actuator; 21. Oil cylinder; 3. Control valve mechanism; 31. Solenoid valve; 32. Two-way flow limiting valve; 33. Check valve; 34. Relief valve; 35. Pressure-compensated proportional valve. Detailed Implementation

[0020] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0021] like Figure 1 As shown, a hydraulic control system for a three-way stacker crane with upward movement of personnel is disclosed. The system includes: a hydraulic power unit 1; an actuator 2 connected to the hydraulic power unit 1; and a control valve mechanism 3 connected to both the hydraulic power unit 1 and the actuator 2. The hydraulic power unit 1 delivers hydraulic oil to the actuator 2 via the control valve mechanism 3. This hydraulic control system utilizes the hydraulic oil provided by the hydraulic power unit 1 as its power source. The hydraulic power unit 1 provides high-pressure hydraulic oil via a pump set, which is connected to the control valve mechanism 3 through pipelines. The control valve mechanism 3 can adjust the flow rate and direction of the hydraulic oil according to control signals, delivering the hydraulic oil to the actuator 2. Upon receiving the hydraulic oil, the actuator 2 converts the hydraulic energy into mechanical energy, driving the stacker crane to achieve upward movement of personnel and three-way stacking operations. The entire system achieves multi-directional operational stability and efficiency optimization through precise valve control technology. Through the cooperation of the hydraulic power unit 1 and the control valve mechanism 3, the movement of the actuator 2 can be controlled efficiently and precisely, improving stacking operation efficiency. Utilizing the characteristics of hydraulic transmission, the system can maintain stable operation under different load conditions, reducing equipment wear and extending service life. Three-way stacker cranes can operate in multiple directions and easily cope with complex working environments through their hydraulic control system, meeting diverse usage needs. The hydraulic system is rationally designed with highly interchangeable components, facilitating maintenance and repair, and reducing operating costs.

[0022] The hydraulic power mechanism 1 can employ different types of hydraulic pumps, such as gear pumps, vane pumps, or piston pumps, selecting the most suitable pump type to optimize performance based on specific operating conditions. The control valve mechanism 3 can use proportional valves, servo valves, or ordinary directional valves. Servo valves are suitable for scenarios with higher precision requirements, while ordinary directional valves reduce costs and are suitable for general needs. The actuator 2 can be a hydraulic cylinder, hydraulic motor, or other suitable actuator, with its specifications and installation method adjusted according to the specific design of the stacker crane. To adapt to special environments such as high or low temperatures, hydraulic oil with excellent temperature resistance can be selected, and system seals can use high-temperature or cold-resistant materials. The connection between the control valve mechanism 3 and the hydraulic power mechanism 1 and actuator 2 can be designed as a modular structure for easy disassembly and maintenance.

[0023] The hydraulic power unit 1 includes a gear pump 11, which is connected to a pump motor and an oil tank. The hydraulic power unit 1 provides the power source for hydraulic oil through the gear pump 11. The pump motor drives the gear pump 11 to rotate at high speed, drawing hydraulic oil from the oil tank into the pump chamber and outputting it in high-pressure form through the gear pump's discharge port. The high-pressure hydraulic oil is directed to the actuator 2 via the control valve mechanism 3, driving the stacker crane to complete the corresponding actions. The pump motor provides stable mechanical energy to the gear pump 11, while the oil tank serves as a storage and return device for the hydraulic oil, supporting the continuous operation of the hydraulic system. The entire power unit achieves efficient and stable hydraulic transmission through optimized design. The gear pump 11 has high mechanical and volumetric efficiency, enabling it to quickly provide a stable hydraulic oil flow rate, thereby improving the response speed of the stacker crane operation. The gear pump 11 has a compact structure and low manufacturing cost, making it suitable as a hydraulic power source in three-way stacker cranes, reducing the overall system cost. Due to its simple design and use of standardized components, the gear pump 11 is easy to maintain and replace, reducing system downtime and maintenance costs. The pump motor works in conjunction with the oil tank to ensure a stable supply of hydraulic oil, avoid system abnormalities caused by oil supply interruptions, and improve the reliability of the hydraulic control system.

[0024] The gear pump 11 of the hydraulic power mechanism 1 can be replaced with a piston pump or a vane pump according to actual needs. The piston pump is suitable for high-pressure operations, while the vane pump is suitable for medium-pressure applications with high noise requirements. The pump motor can use motors of different power specifications or protection levels, such as explosion-proof motors, to adapt to special operating environments. The capacity, material, and shape of the oil tank can be adjusted according to the operating conditions. For example, adding a filtration and cooling device can ensure the cleanliness and temperature control of the hydraulic oil, improving system operating efficiency and durability. The hydraulic oil can be replaced with high-temperature resistant, low-pour-point, or biodegradable hydraulic media depending on temperature, pressure, and other operating conditions, suitable for different operating environments. The gear pump 11, pump motor, and oil tank can be designed as modular units, facilitating quick installation or replacement in different situations, improving system adaptability and maintenance convenience.

[0025] The actuator 2 includes at least one hydraulic cylinder 21. The hydraulic cylinder 21, as the main hydraulic actuator, moves via hydraulic oil supplied by the hydraulic power mechanism 1. The hydraulic oil enters different chambers of the cylinder 21 through the control valve mechanism 3, pushing the piston rod to extend and retract under pressure. The extension and retraction of the cylinder 21 directly drives various operating components of the stacker crane, enabling personnel to move upwards and three-way stacking operations. The control valve mechanism 3 precisely controls the speed, displacement, and direction of the cylinder 21 by adjusting the flow and direction of the hydraulic oil, thereby completing the required complex operations. Through precise control of the hydraulic system, the cylinder 21 achieves smooth and accurate extension and retraction, meeting the high-precision operation requirements of the stacker crane. The design of the cylinder 21 provides a large thrust or pull force, suitable for the heavy-load and frequent operation requirements of the stacker crane. By combining multiple cylinders, the actuator 2 can achieve multi-dimensional movements, providing the stacker crane with more flexible operating capabilities. The cylinder 21 has a simple structure, high durability, adaptability to various harsh working conditions, and reduces maintenance costs and failure rates.

[0026] Hydraulic cylinder 21 can be selected as a single-acting or double-acting cylinder according to specific needs. Single-acting cylinders are suitable for scenarios requiring only unidirectional drive, while double-acting cylinders provide bidirectional drive functionality. Piston cylinders, plunger cylinders, or telescopic cylinders can be selected to adapt to different stroke and load requirements. The cylinder body and piston rod of hydraulic cylinder 21 can be made of high-strength alloy steel or lightweight aluminum alloy, with strength and weight optimized according to working conditions. Seals can be made of materials with high temperature resistance, low temperature resistance, or high wear resistance to improve the sealing performance and lifespan of the cylinder. The working pressure, stroke length, or piston rod diameter of the cylinder can be adjusted as needed to achieve different mechanical characteristics. In special application scenarios, the action performance of hydraulic cylinder 21 can be further optimized by using limit devices or buffer devices. In addition to hydraulic cylinder 21, actuator 2 can also include other actuators such as hydraulic motors to complete rotation or special action requirements. The combined use of hydraulic cylinder 21 with other actuators can improve the functional versatility and operational efficiency of the stacker crane. The hydraulic cylinder 21 can be designed as a quick-change module, facilitating flexible adjustments during maintenance or when needs change. The supporting piping and control system can also be designed as a modular structure, further improving the system's adaptability and ease of maintenance.

[0027] The control valve mechanism 3 includes at least one solenoid valve 31, which is connected to the gear pump 11. The solenoid valve 31 is connected to a bidirectional flow-limiting valve 32, and the bidirectional flow-limiting valve 32 is connected to a one-way valve 33. The control valve mechanism 3 regulates the flow direction and on / off state of the hydraulic oil through the solenoid valve 31, thereby controlling the action of the actuator 2. The function of the solenoid valve 31: The solenoid valve 31 receives an electrical signal to control its opening and closing state. When the solenoid valve 31 is open, hydraulic oil is output from the gear pump 11 and enters the subsequent valve group through the solenoid valve 31; when the solenoid valve 31 is closed, the flow of hydraulic oil is blocked. The function of the bidirectional flow-limiting valve 32: The bidirectional flow-limiting valve 32 restricts the flow rate of hydraulic oil in both directions, ensuring stable flow velocity in both directions, thereby achieving precise control of the action speed of the actuator 2. The function of the one-way valve 33: The one-way valve 33 ensures unidirectional flow of hydraulic oil, preventing reverse pressure in the hydraulic circuit and protecting the safety and stability of the system. The valves mentioned above are connected by pipelines to form a logically sound hydraulic circuit, enabling the stacker crane to achieve rapid and stable hydraulic transmission under different operational requirements. The solenoid valve 31, in conjunction with the two-way flow-limiting valve 32, enables precise control of the hydraulic oil flow and direction, improving the stacker crane's operational flexibility and response speed. The one-way valve 33 prevents shocks caused by hydraulic oil backflow, reducing damage to hydraulic components and extending the system's service life. The two-way flow-limiting valve 32 effectively avoids actuator vibration caused by flow fluctuations, improving the stability of stacker crane operation. The electrical signal control method of the solenoid valve 31 makes system operation more convenient and suitable for highly automated scenarios. The system design is modular, with clearly defined functions and reasonable connections for each valve group, adaptable to different hydraulic power requirements and operating conditions.

[0028] Solenoid valve 31 can be replaced with a proportional solenoid valve for more precise flow and pressure control, suitable for scenarios requiring higher actuation accuracy. For enhanced durability, explosion-proof or high-pressure solenoid valves can be selected to adapt to special operating conditions. The bidirectional flow-limiting valve 32 can be replaced with a proportional valve with integrated flow control, simplifying circuit design and improving control performance. In scenarios where precise speed adjustment is not required, the bidirectional flow-limiting valve can be simplified to a standard throttle valve to reduce costs. The check valve 33 can be a composite valve with overflow protection, further enhancing system safety. In some scenarios, the check valve can be replaced by adding a bypass line to meet specific flow path requirements. Adding multiple sets of solenoid valves 31 enables more diverse flow direction control, supporting complex hydraulic operation processes. Introducing logic valves optimizes valve group coordination, reduces energy loss in hydraulic circuits, and improves system efficiency. Solenoid valves, bidirectional flow-limiting valves, and check valves can all be modularly designed for quick replacement or adjustment in case of failure. The piping design can incorporate quick-connect fittings to further simplify maintenance and improve system reliability.

[0029] One-way valve 33 is connected to cylinder 21. The connection between one-way valve 33 and cylinder 21 forms a stable hydraulic circuit. Hydraulic oil is delivered to cylinder 21 through one-way valve 33, enabling the actuator to drive the mechanism. After flowing out from the two-way flow-limiting valve 32, the hydraulic oil enters cylinder 21 through one-way valve 33. One-way valve 33 ensures that the hydraulic oil flows in only one direction, preventing backflow into the circuit due to pressure fluctuations. When hydraulic oil enters the working chamber of cylinder 21 through one-way valve 33, it pushes the cylinder piston to extend and retract, realizing the lifting, moving, or stacking actions of the stacker crane. One-way valve 33 prevents hydraulic oil from flowing back to control valve mechanism 3, improving the system's pressure stability and protecting the safety and reliability of cylinder 21 during circuit operation. One-way valve 33 ensures that the hydraulic oil flows in a single direction, avoiding damage to cylinder 21 from backflow or reverse pressure, thus improving the system's safety and stability. The one-way control of check valve 33 ensures more stable pressure within cylinder 21, guaranteeing smooth and shock-free actuator operation. The connection design between check valve 33 and cylinder 21 simplifies the hydraulic circuit, enhancing system reliability and adapting to high-load operation requirements under various conditions. The modular connection design between check valve 33 and cylinder 21 facilitates fault diagnosis and component replacement, reducing system downtime.

[0030] The check valve 33 can be replaced with a check valve with pressure compensation function to further improve the stability of the hydraulic system under high load or complex working conditions. A check valve with an anti-clogging design can be used to avoid flow path blockage caused by impurities in the hydraulic oil. The connection between the check valve 33 and the cylinder 21 can be achieved through high-pressure hoses or rigid pipelines, allowing for flexible or fixed connection methods depending on the actual application requirements. The addition of a quick-connect design eliminates the need to disassemble a large number of pipelines during maintenance or replacement of the check valve 33, improving maintenance efficiency. The check valve 33 can be used in conjunction with a relief valve to automatically activate relief protection when the hydraulic oil flow or pressure is abnormal, further ensuring the safety of the cylinder 21. A parallel check valve circuit design allows the hydraulic oil to switch flow directions as needed, adapting to various operating modes. Integrating the check valve 33 and the cylinder 21 into a single module reduces installation complexity and lowers the overall size of the hydraulic system. The check valve can be designed as a replaceable component to adapt to different cylinder specifications, improving system compatibility and flexibility. Depending on the operational requirements of the stacker crane, different types of hydraulic cylinders 21 can be selected (such as telescopic hydraulic cylinders or servo hydraulic cylinders), and they can be matched with one-way valves 33 to adjust the flow and pressure characteristics.

[0031] Gear pump 11 is connected to oil filter 12, which is connected to relief valve 34. Relief valve 34 is connected to bidirectional flow limiting valve 32 and solenoid valve 31. Gear pump 11 provides power: the high-pressure hydraulic oil output by gear pump 11 is first filtered through oil filter 12 to remove impurities and particles from the hydraulic oil, ensuring the cleanliness and safety of the hydraulic system. The filtering function of oil filter 12: Oil filter 12 prevents impurities from entering the hydraulic circuit, providing protection for solenoid valve 31, bidirectional flow limiting valve 32, and other precision components, extending their service life. The safety protection function of relief valve 34: When the pressure in the hydraulic system exceeds the set value, relief valve 34 automatically opens, returning excess hydraulic oil to the oil tank to avoid system overload and equipment damage. Simultaneously, relief valve 34 also forms a loop with bidirectional flow limiting valve 32 and solenoid valve 31 to ensure smooth flow of hydraulic oil under different pressures and reliable system operation. The linkage of the control valve mechanism: Hydraulic oil, regulated by the relief valve 34, is delivered to the two-way flow limiting valve 32 and the solenoid valve 31, further controlling the direction and flow of the hydraulic oil to drive the actuator to complete precise stacking operations. The oil filter 12 filters impurities in the hydraulic oil, effectively protecting hydraulic system components, reducing wear or blockage caused by impurities, and improving system reliability. The relief valve 34 can quickly relieve pressure when the system pressure is too high, protecting the gear pump 11, pipelines, and other components, extending system life. The relief valve 34, in conjunction with the two-way flow limiting valve 32, ensures stable hydraulic oil flow under different loads, preventing actuator vibration or instability. The linkage control design of the relief valve 34 and the solenoid valve 31 makes the hydraulic circuit safer, adaptable to changing working environments, and prevents damage to equipment from accidental operation. The oil filter 12 extends the service life of hydraulic oil and components, reduces the frequency of component replacement and maintenance, and lowers overall operating costs.

[0032] Oil filter 12 can be replaced with a high-precision cartridge filter for more stringent impurity filtration requirements. In special environments, a self-cleaning oil filter can be used to reduce manual maintenance. Relief valve 34 can be a pilot-operated relief valve with adjustment function to meet different operating pressure requirements. Adding a pressure monitoring device to display the relief valve's operating status in real time enhances the intelligence of operation. A modular design can be adopted between gear pump 11, oil filter 12, and relief valve 34 for easy installation and disassembly. Relief valve 34 can achieve dual functions of pressure regulation and overload protection by adding a bypass circuit, adapting to more complex working conditions. Adding a buffer circuit between relief valve 34 and bidirectional flow restrictor valve 32 further optimizes the hydraulic oil's pressure regulation function. Adding a temperature control device to cool or heat the hydraulic oil ensures stable operation of the hydraulic system under different temperature conditions. Gear pump 11 can be replaced with a more efficient piston pump or vane pump to meet different pressure and flow requirements. Solenoid valve 31 and bidirectional flow restrictor valve 32 can be integrated into an integrated control module, simplifying system design and improving integration.

[0033] One of the solenoid valves 31 is connected to a pressure-compensated proportional valve 35, which is connected to the hydraulic cylinder 21. The solenoid valve 31 has the following control function: it receives a control signal, adjusts the flow direction and opening / closing state of the hydraulic oil, and guides the hydraulic oil to the pressure-compensated proportional valve 35. The pressure-compensated proportional valve 35 has the following adjustment function: it dynamically adjusts the hydraulic oil flow rate according to the input control signal and the actual pressure state of the hydraulic system, while maintaining a constant pressure difference across the hydraulic cylinder 21. This pressure compensation function allows the hydraulic oil to enter the hydraulic cylinder 21 at a constant flow rate, ensuring smooth operation of the cylinder 21 regardless of load changes. The hydraulic cylinder 21's execution function: the stable hydraulic oil output from the pressure-compensated proportional valve 35 enters the hydraulic cylinder 21, pushing the cylinder piston to achieve precise extension and retraction, thereby completing the complex operations of the stacker crane. The pressure-compensated proportional valve 35 can also dynamically adjust the cylinder's operating speed and force output according to changes in external load. Through the constant flow control of the pressure-compensated proportional valve 35, the cylinder 21 can achieve smooth and shock-free movement, avoiding vibration or loss of control caused by load changes. The pressure-compensated proportional valve 35 can precisely adjust the hydraulic oil flow based on the signal from the solenoid valve 31, achieving precise control of the cylinder 21's operating speed and meeting high-precision operation requirements. The dynamic adjustment function of the pressure-compensated proportional valve 35 reduces hydraulic oil waste, improves the energy utilization efficiency of the hydraulic system, and lowers operating costs. Regardless of changes in external load, the pressure-compensated proportional valve 35 always maintains stable pressure and flow in the cylinder 21, improving the reliability and safety of system operation. The system design is flexible; through the adjustment of the pressure-compensated proportional valve 35, it can easily cope with different working conditions, expanding the application scenarios of the stacker crane.

[0034] The pressure-compensated proportional valve 35 can be replaced with an electronic proportional valve with intelligent control functions to achieve more complex control logic and data monitoring. If constant flow requirements are not high, a regular proportional valve can be used instead of the pressure-compensated proportional valve to simplify system design and reduce costs. The connection between the solenoid valve 31 and the pressure-compensated proportional valve 35 can be achieved through quick couplings or modular design for easy replacement and maintenance. A filter or vibration damper can be added to the connection line between the pressure-compensated proportional valve 35 and the cylinder 21 to further improve system safety and stability. Depending on the stacker crane's operational requirements, the cylinder 21 can be replaced with an intelligent cylinder with a position sensor to achieve higher precision motion feedback and control. When multi-functional execution is required, multiple pressure-compensated proportional valves and cylinders can be combined to achieve multi-directional and multi-mode stacking operations. Adding a pressure sensor before the pressure-compensated proportional valve 35 allows for real-time monitoring and feedback of system pressure status, improving the intelligence level of the hydraulic system. In conjunction with a programmable logic controller, the collaborative logic between the pressure-compensated proportional valve 35 and the solenoid valve 31 can be optimized to support more complex automated operations. Using a solenoid valve 31 with a higher response speed further improves the control accuracy and reaction speed of the hydraulic system. The pressure compensation proportional valve 35 can be made of corrosion-resistant materials to meet the long-term operating requirements in harsh environments.

[0035] Working Process: When a lifting signal is received, the controller receives the signal and sends a command to the pump motor. The gear pump 11, connected to the pump motor, starts operating, pumping hydraulic oil from the oil tank into the hydraulic system. When the main lifting valve lever is operated, the controller controls the pump motor to operate at a set speed according to the signal, while simultaneously closing and opening the main lifting solenoid valve (e.g., solenoid valve 31). Hydraulic oil enters the main lifting cylinder 21 through the two-way flow limiting valve 32 and the one-way valve 33, pushing the piston of the main lifting cylinder to move, thereby realizing the main lifting action of the stacker crane. When the auxiliary lifting valve lever is operated, the controller receives the signal and controls the pump motor to operate at a set speed. At this time, the auxiliary lifting solenoid valve (e.g., solenoid valve 31) is closed and opened. Hydraulic oil flows to the auxiliary lifting cylinder (another actuator) through the hydraulic circuit, realizing the auxiliary lifting action. When the main or auxiliary lifting valve lever returns to the zero position, the controller will reduce the pump motor speed, slowing it down to below the rated speed. The controller simultaneously adjusts the valve core opening size via a proportional solenoid valve (e.g., proportional valve 31) and energizes the return oil solenoid valve (e.g., solenoid valve 31), allowing hydraulic oil to return to the oil tank via the return oil line, thus controlling the smooth descent of the main or auxiliary cylinder. When the hydraulic control system is stationary, the pump motor stops running, and all solenoid valves 31 are de-energized. At this time, the oil circuit in the multi-way valve is in a pressure-holding state, and the hydraulic oil flows back to the oil tank. The entire system remains stationary and does not perform any actions. When the descent control handle is opened, the controller adjusts the pressure proportional solenoid valve 35 via the analog signal input from the handle, controlling the valve core opening size. Simultaneously, the descent solenoid valve (e.g., solenoid valve 31) is closed, and the descent oil circuit solenoid valve (e.g., solenoid valve 31) is opened. Hydraulic oil returns from the main lifting cylinder 21 or the auxiliary lifting cylinder to the oil tank via the circuit, thus controlling the smooth descent of the gantry. When the descent control handle returns to the zero position, the pressure compensation proportional valve 35 closes, the descent solenoid valve 31 is de-energized and closed, cutting off the descent oil circuit of the gantry and stopping the descent action. When a valve in the descent oil circuit (such as the descent solenoid valve 31) malfunctions, causing the gantry to fail to descend, the descent oil circuit can be opened manually using an auxiliary valve (such as the relief valve 34) to assist the gantry in completing the descent operation, ensuring the safety and reliability of the system.

[0036] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A hydraulic control system for a three-way stacker crane with upward movement, characterized in that, The system includes: Hydraulic power mechanism (1); The actuator (2) is connected to the hydraulic power mechanism (1); A control valve mechanism (3) connected to the hydraulic power mechanism (1) and the actuator (2); The hydraulic power mechanism (1) delivers hydraulic oil to the actuator (2) through the control valve mechanism (3).

2. The hydraulic control system of a three-way stacker crane with upward movement according to claim 1, characterized in that: The hydraulic power mechanism (1) includes a gear pump (11), which is connected to a pump motor and an oil tank.

3. The hydraulic control system for a three-way stacker crane with upward movement according to claim 2, characterized in that: The actuator (2) includes at least one hydraulic cylinder (21).

4. The hydraulic control system of a three-way stacker crane for upward movement according to claim 3, characterized in that: The control valve mechanism (3) includes at least one solenoid valve (31), which is connected to the gear pump (11). The solenoid valve (31) is connected to a bidirectional flow limiting valve (32), and the bidirectional flow limiting valve (32) is connected to a one-way valve (33).

5. The hydraulic control system of a three-way stacker crane for upward movement according to claim 4, characterized in that: The one-way valve (33) is connected to the oil cylinder (21).

6. The hydraulic control system of a three-way stacker crane for upward movement according to claim 4, characterized in that: The gear pump (11) is connected to an oil filter (12), the oil filter (12) is connected to an overflow valve (34), and the overflow valve (34) is connected to a two-way flow limiting valve (32) and a solenoid valve (31).

7. The hydraulic control system of a three-way stacker crane for upward movement according to claim 4, characterized in that: One of the solenoid valves (31) is connected to a pressure-compensated proportional valve (35), which is connected to the cylinder (21).

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