Propulsion and flexible braking hydraulic system for heavy load production line

Abstract

This invention belongs to the field of hydraulic control technology, specifically relating to a propulsion and flexible braking hydraulic system for heavy-duty production lines. The system adopts a modular design, reducing the types of components while meeting performance requirements, resulting in low cost, simple control, and easy maintenance. The system uses a variable displacement piston pump combined with an energy storage device to further reduce installed power. The braking force required for the production line is passively generated by the system, eliminating the need for the system to provide it itself, thus effectively achieving braking for heavy-duty production lines. The system's output force is designed to meet only the needs of the production line's static start-up and operation, significantly reducing the installed power of the production line system. The system control employs a combination of displacement closed-loop control and force closed-loop control, effectively improving work efficiency and control accuracy. It can achieve both propulsion and buffered flexible braking of the production line according to different process requirements.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic control technology, specifically relating to a propulsion and flexible braking hydraulic system for heavy-duty production lines. Background Technology

[0002] With the rapid development of the national economy, various types of machinery have been widely used. Industrial automated production lines are even more prevalent in mass production. Automated production lines are driven by electric, pneumatic, and hydraulic systems. Electric drives offer smooth operation, precise positioning, and automated control; pneumatic drives are energy-efficient, fast, and easy to operate, and are primarily used for applications with relatively small loads. Hydraulic drives offer greater load capacity, precise control, and stable speed, and are typically used in applications requiring heavy loads and high-precision control, but their equipment costs are higher and maintenance is more difficult. Heavy-duty production lines, such as casting production lines for large mechanical parts, require significant braking force due to the large product mass and inertia, making control technically challenging. Summary of the Invention

[0003] To address the aforementioned shortcomings of existing technologies, this invention provides a propulsion and flexible braking hydraulic system for heavy-duty production lines. This system primarily addresses the propulsion and buffer flexible braking control required for heavy-duty production lines, meeting the operational conditions of such lines. Furthermore, it features low installed power, low cost, simple control, and convenient use and maintenance.

[0004] To achieve the above objectives, the present invention adopts the following technical solution:

[0005] A propulsion and flexible braking hydraulic system for a heavy-duty production line includes an oil tank device, a left-side actuator cylinder, a right-side actuator cylinder, and a measurement and control system. The left-side actuator cylinder and the right-side actuator cylinder are respectively connected to the inlet and outlet ends of the mechanical parts of the production line. One pipeline of the oil tank device is equipped with a pump unit and a check valve as the oil inlet pipeline of the hydraulic system, and the other pipeline connected to the oil tank device is equipped with a return oil filter, a check valve, and a water cooler.

[0006] An accumulator, a high-pressure oil filter I, and a high-pressure oil filter II are installed on the oil inlet pipeline. The accumulator stores the hydraulic oil and hydraulic energy output by the pump unit when the required flow rate of the hydraulic system is small; when the required flow rate of the system is large, it releases the hydraulic oil and hydraulic energy. The high-pressure oil filter I and the high-pressure oil filter II filter the hydraulic oil entering the hydraulic system.

[0007] The system hydraulic oil enters the rodless chamber of the left actuator cylinder through the high-pressure oil filter and the proportional directional valve. The hydraulic oil in the rod chamber of the left actuator cylinder returns to the oil tank through the electro-hydraulic directional valve, the proportional directional valve, the cartridge pressure valve, the water cooler, and the return oil filter.

[0008] The system hydraulic oil enters the rod chamber of the right actuator cylinder through the high-pressure oil filter II, the proportional directional valve II, and the electro-hydraulic directional valve II. The hydraulic oil in the rodless chamber of the right actuator cylinder returns to the oil tank through the proportional directional valve II, the cartridge pressure valve II, the water cooler, and the return oil filter.

[0009] The pipeline between check valve one installed on the oil inlet pipeline and check valve two installed on the oil return pipeline is connected by an electromagnetic relief valve.

[0010] The measurement and control system includes a power cabinet and a control cabinet. The measurement and control system is used to receive and process signals in real time, issue instructions according to process requirements, and realize closed-loop control of system displacement and closed-loop control of force.

[0011] Furthermore, pressure sensors are installed on the pipes leading to and from the left and right actuator cylinders; the actuator cylinders integrate displacement and force sensors, with the displacement sensors monitoring and providing feedback on the position and speed of the actuator cylinders in real time, and the force sensors monitoring and providing feedback on the force between the actuator cylinders and the mechanical parts of the production line in real time.

[0012] Furthermore, the electromagnetic relief valve sets the system's safe pressure; before the pump unit starts, the electromagnetic relief valve is energized, the system is in an unloaded state, and the pump unit starts flexibly; when the electromagnetic relief valve is de-energized, the system is under load and pressurized, preparing for normal operation.

[0013] Furthermore, the tank unit integrates an air filter, level gauge, temperature sensor, filter, heater, and hydraulic accessories.

[0014] Furthermore, the hydraulic system also includes a proportional pressure valve, which serves as a pilot valve for the cartridge pressure valve, and achieves stepless pressure adjustment by changing the electrical signal.

[0015] Furthermore, the system also includes an electromagnetic directional valve, which operates in different positions to change the direction of hydraulic oil flow.

[0016] Furthermore, proportional directional valve one and proportional directional valve two are equipped with amplifiers, which can control the direction, speed and acceleration of the actuator cylinder by acquiring the displacement signal of the actuator cylinder.

[0017] Furthermore, a damping orifice is provided between the oil inlet A and the oil return port B of the cartridge pressure valve.

[0018] The beneficial effects of this invention are as follows:

[0019] (1) The force required for production line braking is passively generated by the system and does not need to be provided by the system itself, which can effectively realize the braking of heavy-duty product production lines; the output force of the system design only needs to meet the needs of the production line to start and run at rest, which greatly reduces the installed power of the production line system.

[0020] (2) The system adopts a modular design, which reduces the types of components while meeting performance requirements. It is low-cost, easy to control and maintain. It can realize the advancement and buffering flexible braking of the production line according to different process requirements.

[0021] (3) A damping hole is provided between the oil inlet A and the oil return port B of the cartridge pressure valve. When the production line is in operation or when it is not used for a long time, the high pressure generated by braking is reduced through the damping hole, so that the system is kept at a relatively low pressure and the system is protected.

[0022] (4) The system adopts a design that combines a variable displacement piston pump with an energy storage device, which further reduces the installed power;

[0023] (5) The system control adopts a combination of displacement closed-loop control and force closed-loop control, which effectively improves working efficiency and control accuracy. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the system of the present invention;

[0025] Figure 2 This is a schematic diagram of the production line moving to the right.

[0026] Figure 3 A schematic diagram showing the active retraction of the hydraulic cylinder on the right side as the production line moves to the right.

[0027] Figure 4 This is a schematic diagram of the production line moving to the left.

[0028] The components include: 1. Oil tank unit; 2. Pump unit; 3. Check valve one; 4. Accumulator; 5. Solenoid relief valve; 6. Check valve two; 7. Water cooler; 8. Return oil filter; 9. High-pressure oil filter one; 10. High-pressure oil filter two; 11. Check valve three; 12. Check valve four; 13. Proportional directional valve one; 14. Proportional directional valve two; 15. Cartridge pressure valve one; 16. Cartridge pressure valve two; 17. Proportional pressure valve one; 18. Proportional pressure valve two; 19. Solenoid directional valve one; 20. Solenoid directional valve two; 21. Electro-hydraulic directional valve one; 22. Electro-hydraulic directional valve two; 23. Pressure sensor; 24. Left-side actuator cylinder; 25. Right-side actuator cylinder; 26. Measurement and control system. Detailed Implementation

[0029] To enable those skilled in the art to better understand the present invention, the technical solution of the present invention will be further described below in conjunction with the accompanying drawings and embodiments.

[0030] Example 1:

[0031] Reference Figure 1 As shown, the present invention provides a propulsion and flexible braking hydraulic system for heavy-duty production lines. The system mainly includes an oil tank device 1, a pump unit 2, a first check valve 3, an accumulator 4, an electromagnetic relief valve 5, a second check valve 6, a water cooler 7, a return oil filter 8, a first high-pressure oil filter 9, a second high-pressure oil filter 10, a third check valve 11, a fourth check valve 12, a first proportional directional valve 13, a second proportional directional valve 14, a first cartridge pressure valve 15, a second cartridge pressure valve 16, a first proportional pressure valve 17, a second proportional pressure valve 18, a first electromagnetic directional valve 19, a second electromagnetic directional valve 20, a first electro-hydraulic directional valve 21, a second electro-hydraulic directional valve 22, a pressure sensor 23, a left-side actuator cylinder 24, a right-side actuator cylinder 25, and a measurement and control system 26.

[0032] The oil tank unit 1 is a storage device for the hydraulic system's transmission medium, primarily storing oil, dissipating heat, settling impurities in the oil, and releasing air mixed in with the oil. Oil tank unit 1 integrates hydraulic accessories such as an air filter, level gauge, temperature sensor, and heater. Pump unit 2 mainly consists of a motor and a variable displacement piston pump, providing the power source for the hydraulic system.

[0033] Accumulator 4 stores hydraulic oil. When the required flow rate of the hydraulic system is small, it stores the hydraulic oil and hydraulic energy output by pump unit 2; when the required flow rate of the system is large, it releases the hydraulic oil and hydraulic energy to meet the system requirements.

[0034] The electromagnetic relief valve 5 sets the system safety pressure. Before the pump unit 2 is started, the electromagnetic relief valve 5 is energized, the system is in an unloaded state, and the pump unit 2 starts flexibly without load; when the electromagnetic relief valve 5 is de-energized, the system is under load and pressurized to prepare for normal operation.

[0035] The water cooler 7 can perform heat exchange, using water as the cooling medium to cool the hydraulic oil in the hydraulic system, ensuring that the hydraulic oil in the system operates at an appropriate temperature.

[0036] Check valve 2 (6) is a bypass valve with an opening pressure of 6 bar. When the hydraulic oil flow through water cooler 7 increases or the water cooler's oil supply capacity is insufficient, the hydraulic oil pressure through water cooler 7 will rise. When it rises to 6 bar, check valve 2 (6) will open, allowing hydraulic oil to return to the oil tank 1, protecting water cooler 7 from excessive pressure shock. Check valve 2 (6) allows hydraulic oil to flow in one direction, completely preventing reverse flow.

[0037] High-pressure oil filter 9 and high-pressure oil filter 10 filter the hydraulic oil entering the hydraulic system to prevent impurities from entering hydraulic components such as proportional valves that require high oil cleanliness; return oil filter 8 filters the hydraulic oil returning to the oil tank device 1.

[0038] The proportional directional valve 13 and proportional directional valve 2 are equipped with amplifiers. By acquiring the displacement signal of the actuator cylinder, the direction, speed and acceleration of the actuator cylinder can be controlled.

[0039] Proportional pressure valve 17 and proportional pressure valve 28 serve as pilot valves for cartridge pressure valve 15 and cartridge pressure valve 26, and can achieve stepless pressure adjustment by changing the electrical signal.

[0040] Electromagnetic directional valve 19 and electromagnetic directional valve 20, as well as electro-hydraulic directional valve 11 and electro-hydraulic directional valve 22, can operate in different working positions to change the direction of hydraulic oil flow.

[0041] The left-side actuator cylinder 24 and the right-side actuator cylinder 25 can drive the production line to move according to the process flow. The actuator cylinders integrate displacement sensors LC1-LC2 and force sensors YL1-YL2. The displacement sensors can monitor and provide feedback on the position and speed of the actuator cylinder in real time, and the force sensors can monitor and provide feedback on the force between the actuator cylinder and the mechanical parts of the production line in real time.

[0042] The measurement and control system 26 includes a power cabinet and a control cabinet, which are used to receive and process various signals in real time, issue various commands according to the input process requirements, and realize closed-loop control of system displacement and closed-loop control of force.

[0043] The working principle of the propulsion and flexible braking hydraulic system for heavy-duty production lines of this invention is as follows:

[0044] When the electromagnet DT1 of the electromagnetic relief valve 5 is energized, the pump unit 2 starts without load and provides oil. When the electromagnet DT1 of the electromagnetic relief valve 5 is de-energized, the hydraulic system builds up pressure.

[0045] When the production line moves to the right, the proportional solenoid BDT1 of proportional directional valve 13 applies a signal, the solenoid DT2 of electro-hydraulic directional valve 21 is energized, the proportional solenoid BDT5 of proportional directional valve 24 applies a maximum signal, the solenoid DT5 of solenoid directional valve 19 is energized, and the proportional solenoid BDT6 of proportional pressure valve 28 applies a signal. The system pressure oil enters the rodless chamber of the left actuator cylinder 24 through the high-pressure oil filter 9 and the proportional directional valve 13. The hydraulic oil in the rod chamber of the left actuator cylinder 24 returns to the oil tank device 1 through the electro-hydraulic directional valve 21, the proportional directional valve 13, the cartridge pressure valve 15, the water cooler 7, and the return oil filter 8, causing the piston rod of the left actuator cylinder 24 to extend and move to the right, pushing the production line to move to the right. At this time, by adjusting the magnitude of the signal applied by the proportional solenoid BDT1 of proportional directional valve 13, the flow rate entering the rodless chamber of the left actuator cylinder 24 can be adjusted, thereby adjusting the movement speed according to the process requirements. Simultaneously, driven by the left-side actuator cylinder 24, the right-side actuator cylinder 25 passively retracts. Part of the hydraulic oil in its rodless chamber returns to the oil tank 1 via the proportional directional valve 14, cartridge pressure valve 16, water cooler 7, and return oil filter 8. The remaining hydraulic oil enters the rod chamber of the right-side actuator cylinder 25 via the check valve 12 and electro-hydraulic directional valve 22, preventing the rod chamber from becoming empty. During operation, displacement sensor LC1, force sensors YL1-YL2, and pressure sensor 23 transmit displacement, velocity, force, and pressure signals to the measurement and control system 26 in real time. The measurement and control system 26 receives and processes these signals in real time, issuing various commands based on the input process requirements to achieve closed-loop control of system displacement and force. By adjusting the applied signal of the proportional electromagnet BDT6 in the proportional pressure valve 18, the pressure of the cartridge pressure valve 16 can be steplessly adjusted, thereby adjusting the braking force of the production line. This ensures that the components in the production line contact and operate according to the required force, achieving buffered and flexible operation of the production line. When the production line needs to stop at a certain position, a signal can be increased to the proportional pressure valve 18 and the proportional solenoid BDT6 according to a set linear ratio. This causes the system to generate a gradually increasing braking force, allowing the production line to brake gently and stop at the required position. For specific operation details, refer to... Figure 2 As shown.

[0046] During the above actions, according to process requirements, the right-side actuator cylinder 25 can also actively retract. A signal is applied to the proportional solenoid BDT5 of the proportional directional valve 14, energizing the solenoid DT4 of the electro-hydraulic directional valve 22 and de-energizing the solenoid DT5 of the electromagnetic directional valve 20. System pressure oil enters the rod chamber of the right-side actuator cylinder 25 through the high-pressure oil filter 10, proportional directional valve 14, and electro-hydraulic directional valve 22. Hydraulic oil in the rodless chamber of the right-side actuator cylinder 25 returns to the oil tank device 1 through the proportional directional valve 14, cartridge pressure valve 16, water cooler 7, and return oil filter 8, causing the right-side actuator cylinder 25 to actively retract. For specific actions, refer to... Figure 3 As shown.

[0047] When the production line moves to the left, the proportional solenoid BDT4 of proportional directional valve 214 applies a signal, the solenoid DT4 of electro-hydraulic directional valve 22 is energized, the proportional solenoid BDT2 of proportional directional valve 13 applies a maximum signal, the solenoid DT3 of solenoid directional valve 19 is energized, and the proportional solenoid BDT3 of proportional pressure valve 17 applies a signal. The system pressure oil enters the rodless chamber of the right-side actuator cylinder 25 through the high-pressure oil filter 210 and proportional directional valve 214. The hydraulic oil in the rod chamber of the right-side actuator cylinder 25 returns to the oil tank device 1 through electro-hydraulic directional valve 22, proportional directional valve 214, cartridge pressure valve 216, water cooler 7, and return oil filter 8, causing the piston rod of the right-side actuator cylinder 25 to extend and move to the left, pushing the production line to move to the left. At this time, by adjusting the magnitude of the signal applied by the proportional solenoid BDT4 of proportional directional valve 214, the flow rate entering the rodless chamber of the right-side actuator cylinder 25 can be adjusted, thereby adjusting the movement speed according to the process requirements. Simultaneously, driven by the right-side actuator cylinder 25, the left-side actuator cylinder 24 passively retracts. Part of the hydraulic oil in its rodless chamber returns to the oil tank 1 via the proportional directional valve 13, cartridge pressure valve 15, water cooler 7, and return oil filter 8. The remaining hydraulic oil enters the rod chamber of the left-side actuator cylinder 24 via the check valve 11 and electro-hydraulic directional valve 21, preventing the rod chamber from becoming empty. During operation, displacement sensor LC2, force sensors YL1-YL2, and pressure sensor 23 transmit displacement, velocity, force, and pressure signals to the measurement and control system 26 in real time. The measurement and control system 26 receives and processes these signals in real time, issuing various commands based on the input process requirements to achieve closed-loop control of system displacement and force. By adjusting the applied signal of the proportional electromagnet BDT3 in the proportional pressure valve 17, the pressure of the cartridge pressure valve 15 can be steplessly adjusted, thereby adjusting the braking force of the production line. This ensures that the components in the production line contact and operate according to the force requirements of the process, achieving buffered and flexible operation of the production line. When the production line needs to stop at a certain position, a signal can be increased to the proportional pressure valve-17 proportional solenoid BDT3 according to a set linear ratio. This causes the system to generate a gradually increasing braking force, allowing the production line to brake gently and stop at the required position. For specific operation details, refer to... Figure 4 As shown.

[0048] During the above actions, the left-side hydraulic cylinder 24 can also actively retract according to process requirements.

[0049] In the system return oil line, a connection is made between the oil inlet A and the oil return port B of cartridge pressure valve 15 and cartridge pressure valve 2 16. The damping orifice is relatively small and will not have any impact during normal operation and braking of the production line. When the production line is in operation or when it is not used for a long time, the hydraulic oil in the rodless chamber of the actuator cylinder and the system pipeline will slowly leak from the damping orifice to the oil tank device 1, thereby reducing the high pressure generated by braking and keeping the system at a relatively low pressure to protect the system safety.

[0050] The various embodiments in this specification are described in a progressive manner. Each embodiment focuses on the differences from other embodiments. The same or similar parts between the various embodiments can be referred to each other.

[0051] The terms "upper," "lower," "outer," "inner," etc., used in the specification, claims, and accompanying drawings of this invention are used to distinguish relative positional relationships and are not necessarily qualitative. It should be understood that such data can be interchanged where appropriate so that embodiments of the invention described herein can be implemented in orders other than those illustrated or described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0052] The above description of the disclosed embodiments enables those skilled in the art to make or use the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A propulsion and flexible braking hydraulic system for a heavy-duty production line, comprising an oil tank device (1), a left-side actuator cylinder (24), a right-side actuator cylinder (25), and a measurement and control system (26), wherein the left-side actuator cylinder (24) and the right-side actuator cylinder (25) are respectively connected to the inlet and outlet ends of the mechanical parts of the production line; characterized in that, The oil tank device (1) has a pump unit (2) and a check valve (3) installed on one pipeline as the oil inlet pipeline of the hydraulic system. The other pipeline connected to the oil tank device (1) is the oil return pipeline, and is equipped with an oil return filter (8), a check valve (6), and a water cooler (7). An accumulator (4), a high-pressure oil filter one (9), and a high-pressure oil filter two (10) are installed on the oil inlet pipeline. The accumulator (4) stores the hydraulic oil and hydraulic energy output by the pump unit (2) when the required flow rate of the hydraulic system is small; and releases the hydraulic oil and hydraulic energy when the required flow rate of the system is large. The high-pressure oil filter one (9) and the high-pressure oil filter two (10) filter the hydraulic oil entering the hydraulic system. The system hydraulic oil enters the rodless chamber of the left actuator cylinder (24) through the high-pressure oil filter (9) and the proportional directional valve (13). The hydraulic oil in the rod chamber of the left actuator cylinder (24) returns to the oil tank device (1) through the electro-hydraulic directional valve (21), the proportional directional valve (13), the cartridge pressure valve (15), the water cooler (7), and the return oil filter (8). The system hydraulic oil enters the rod chamber of the right actuator cylinder (25) through the high-pressure oil filter (10), the proportional directional valve (14), and the electro-hydraulic directional valve (22). The hydraulic oil in the rodless chamber of the right actuator cylinder (25) returns to the oil tank device (1) through the proportional directional valve (14), the cartridge pressure valve (16), the water cooler (7), and the return oil filter (8). The pipeline between the one-way valve 1 (3) installed on the oil inlet pipeline and the one-way valve 2 (6) installed on the oil return pipeline is connected by an electromagnetic relief valve (5); The measurement and control system (26) receives and processes signals in real time, issues instructions according to process requirements, and realizes closed-loop control of system displacement and closed-loop control of force.

2. The propulsion and flexible braking hydraulic system for a heavy-duty production line according to claim 1, characterized in that, Pressure sensors (23) are installed on the pipes leading to and from the left actuator cylinder (24) and the right actuator cylinder (25); the actuator cylinder integrates a displacement sensor and a force sensor. The displacement sensor monitors and provides feedback on the position and speed of the actuator cylinder in real time, and the force sensor monitors and provides feedback on the force between the actuator cylinder and the mechanical parts of the production line in real time.

3. The propulsion and flexible braking hydraulic system for a heavy-duty production line according to claim 1, characterized in that, The electromagnetic overflow valve (5) sets the system safety pressure; before the pump unit (2) is started, the electromagnetic overflow valve (5) is energized, the system is in an unloaded state, and the pump unit (2) is started flexibly; the electromagnetic overflow valve (5) is de-energized, the system is under load and pressurized, and is ready for normal operation.

4. The propulsion and flexible braking hydraulic system for a heavy-duty production line according to claim 1, characterized in that, The tank unit (1) integrates an air filter, a level gauge, a temperature sensor, a filter, and a heater.

5. The propulsion and flexible braking hydraulic system for a heavy-duty production line according to claim 1, characterized in that, The hydraulic system also includes a proportional pressure valve, which acts as a pilot valve for the cartridge pressure valve and achieves stepless pressure adjustment by changing the electrical signal.

6. The propulsion and flexible braking hydraulic system for a heavy-duty production line according to claim 1, characterized in that, The system also includes a solenoid directional valve, which, along with the electro-hydraulic directional valve, is used to change the direction of hydraulic oil flow.

7. The propulsion and flexible braking hydraulic system for a heavy-duty production line according to claim 1, characterized in that, The proportional directional valve one (13) and the proportional directional valve two (14) are equipped with amplifiers to collect the displacement signal of the actuator cylinder and realize the control of the direction, speed and acceleration of the actuator cylinder.

8. The propulsion and flexible braking hydraulic system for a heavy-duty production line according to claim 1, characterized in that, A damping orifice is provided between the oil inlet A and the oil return port B of the cartridge pressure valve.

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