A hydraulic system and control method for a ship lift sealing frame

Abstract

This invention discloses a hydraulic system and control method for a ship lift sealing frame, relating to the field of hydraulic system technology. The hydraulic system for the ship lift sealing frame includes: multiple active cylinders and multiple passive cylinders; a power supply assembly for drawing hydraulic oil from an oil tank; a throttling and reversing module, whose inlet end is connected to the outlet end of the power supply assembly, for regulating the flow direction of hydraulic oil into the active and passive cylinders; the throttling and reversing module is connected to the rodless chamber of the active cylinders through a first active oil circuit, which is connected to the first passive oil circuit through a sequence valve. In using the hydraulic system for the ship lift sealing frame provided in this application, during the extension of the sealing frame, only the synchronicity of the active cylinders needs to be ensured, reducing the number of cylinders requiring synchronicity, lowering the control difficulty of maintaining synchronicity, thereby reducing the cost of achieving synchronicity requirements and improving the synchronicity of the ship lift sealing frame hydraulic system.

Description

Technical Field

[0001] This invention relates to the field of hydraulic system technology, and more specifically, to a hydraulic system for a ship lift sealing frame. Furthermore, this invention also relates to a control method comprising the aforementioned hydraulic system for a ship lift sealing frame. Background Art

[0002] In the existing technology, the common sealing device for the docking of the ship lift's ship chamber and the lock head is a U-shaped sealing frame. The sealing device is arranged in the U-shaped groove on the upstream and downstream sides of the lock head or ship chamber of the ship lift, and consists of a U-shaped sealing frame with a box-shaped cross-section, a guide device, a rubber water-stop sealing ring (strip), a hydraulic cylinder, a disc spring box, a pump station, etc.

[0003] There are 11 hydraulic cylinders driving the movement of the sealing frame. The piston rods of the 11 cylinders are connected to the disc spring box by bolts. The disc spring box is fixedly connected to the U-shaped sealing frame, as shown in Chinese Patent Application No. 201520696536.1. The structural characteristics of the U-shaped sealing frame determine that the load at the bottom of the corners on both sides of the U-shape is large, and the frictional resistance is also large. This places high demands on the manufacturing and installation of the guiding device, which can easily cause uneven friction, making it difficult for the sealing frame to be pushed out or retracted, and also affecting the synchronous performance of the movement. In the prior art, in order to achieve high synchronization performance, the hydraulic system is complex and the cost is high.

[0004] In summary, how to improve the synchronization of the hydraulic system of the sealing frame of a ship lift while keeping costs low is a problem that urgently needs to be solved by those skilled in the art. Summary of the Invention

[0005] In view of this, the purpose of the present invention is to provide a hydraulic system for the sealing frame of a ship lift, which, during use, only restricts the synchronization of the active cylinder, greatly reducing the difficulty of synchronization control, reducing control costs, and effectively improving the synchronization of the hydraulic system for the sealing frame of a ship lift.

[0006] Another object of the present invention is to provide a control method for the hydraulic system of the sealing frame of the above-mentioned ship lift.

[0007] To achieve the above objectives, the present invention provides the following technical solution:

[0008] A hydraulic system for a ship lift sealing frame includes:

[0009] Multiple active hydraulic cylinders, whose piston rods are connected to a sealing frame;

[0010] Multiple passive hydraulic cylinders, whose piston rods are connected to the sealing frame;

[0011] The oil supply power assembly has its oil inlet connected to the oil tank for drawing hydraulic oil from the oil tank;

[0012] The throttling and reversing module has its inlet end connected to the outlet end of the oil supply power component, and is used to regulate the flow direction of hydraulic oil flowing into the active cylinder and the passive cylinder;

[0013] The throttling and reversing module is connected to the rodless chamber of the active cylinder through a first active oil circuit. The first active oil circuit is connected to the first passive oil circuit through a sequence valve. The first passive oil circuit is connected to the rodless chamber of the passive cylinder.

[0014] When the throttling and reversing module supplies oil to the first active oil circuit, and the pressure of the first active oil circuit is less than the opening pressure of the sequence valve, only the piston rod of the active oil cylinder extends.

[0015] When the throttling and reversing module supplies oil to the first active oil circuit, and the pressure of the first active oil circuit is greater than the opening pressure of the sequence valve, the piston rods of the active oil cylinder and the passive oil cylinder both extend.

[0016] Optionally, the throttling reversing module includes a first electromagnetic reversing valve and a second electromagnetic reversing valve arranged in parallel, and the P port of the first electromagnetic reversing valve and the P port of the second electromagnetic reversing valve are both connected to the oil outlet end of the oil supply power component; the T port of the first electromagnetic reversing valve and the T port of the second electromagnetic reversing valve are both connected to the return oil circuit that returns to the oil tank.

[0017] The first electromagnetic directional valve has its port A connected in sequence to a first speed control valve and a first hydraulically controlled check valve; the first electromagnetic directional valve has its port B connected to a second speed control valve; the second electromagnetic directional valve has its port B connected to a third speed control valve, and its port A is connected in sequence to a fourth speed control valve and a second hydraulically controlled check valve; both the first and second hydraulically controlled check valves are connected to the first active oil circuit, and the third speed control valve is connected to both the second active oil circuit (connected to the rod chamber of the active cylinder) and the second passive oil circuit (connected to the rod chamber of the passive cylinder).

[0018] Optionally, a first relief valve is connected between the third speed regulating valve and the second active oil circuit, and the other end of the first relief valve is connected to the oil tank;

[0019] A second relief valve is connected between the second hydraulic control check valve and the first active oil circuit, and the other end of the second relief valve is connected to the oil tank.

[0020] Optionally, it also includes a throttle valve, one end of which is connected to port A of the second solenoid directional valve, and the other end is connected to the first active oil circuit and the first passive oil circuit.

[0021] Optionally, it also includes a separate oil supply circuit, which supplies oil to the rod chamber of the passive cylinder when the active cylinder drives the sealing frame to retract and the sealing frame compresses the passive cylinder;

[0022] One end of the separate oil supply circuit is connected to the oil tank, and the other end is connected to the rod chamber of the passive cylinder. A first check valve is provided at the end of the separate oil supply circuit connected to the oil tank.

[0023] Optionally, the oil supply power assembly includes a motor, a variable pump connected to the motor via a coupling, an electromagnetic reversing relief valve group connected to the variable pump, and a second check valve. The oil inlet of the variable pump is connected to the oil tank, the oil outlet is connected to port A of the second check valve, and port B of the second check valve is connected to the oil inlet of the throttling reversing module.

[0024] The electromagnetic reversing overflow valve assembly is used to adjust the working pressure of the hydraulic system of the ship lift sealing frame.

[0025] Optionally, the first active oil circuit includes a fifth speed control valve, a sixth speed control valve, and a first solenoid ball valve connected in sequence. The fifth speed control valve is connected to the throttling reversing module, and the first solenoid ball valve is connected to the rodless chamber of the active oil cylinder.

[0026] The third check valve is connected in parallel with the sequence valve. The B port of the third check valve and the P port of the fifth speed control valve are both connected to the P port of the sequence valve. The A port of the sequence valve is connected to the A port of the third check valve. The K port of the sequence valve is connected to the P port of the sixth speed control valve. The T port of the sequence valve is connected to the return oil circuit connected to the oil tank.

[0027] Optionally, the rod chamber of the active cylinder is connected to the throttling reversing module, and the rod chamber of the active cylinder and the throttling reversing module are connected to the P port of the third relief valve. The T port of the third relief valve is connected to the T port of the sequence valve and the return oil circuit connected to the oil tank.

[0028] Optionally, the first passive oil circuit includes a third hydraulically controlled check valve and a second solenoid ball valve. The B port of the third hydraulically controlled check valve is connected to the P port of the second solenoid ball valve, the A port of the second solenoid ball valve is connected to the rodless chamber of the passive cylinder, and the A port of the sequence valve is connected to the P port of the second solenoid ball valve.

[0029] Optionally, the rod chamber of the passive cylinder is connected to the throttling module via a normally closed ball valve. The A port of the normally closed ball valve is connected to the B port of the normally open ball valve and the T port of the fourth relief valve. The A port of the normally open ball valve is connected to the A port of the third hydraulically controlled check valve and the P port of the fourth relief valve. The K port of the third hydraulically controlled check valve is connected to the B port of the normally closed ball valve.

[0030] A control method, applied to the hydraulic system of the ship lift sealing frame as described in any of the above claims, the control method comprising:

[0031] Control the start-up of the fuel supply power unit;

[0032] The control throttling and reversing module supplies oil to the rodless chamber of the active cylinder, so that the piston of the active cylinder extends;

[0033] When the pressure of the first active oil circuit is greater than the opening pressure of the sequence valve, oil is supplied to the rodless chamber of the passive oil cylinder;

[0034] Determine whether the sealing frame has been pushed out to the correct position. If yes, proceed to the next step. If no, control the throttling and reversing module to continuously supply oil to the rodless chamber of the active cylinder and the rodless chamber of the passive cylinder.

[0035] The oil supply power component and the throttling reversing module are controlled to enter the pressure holding state and remain in the pressure holding state for a preset time.

[0036] The control throttling and reversing module supplies oil to the rod chamber of the active cylinder, so that the piston of the active cylinder extends;

[0037] Determine whether the passive cylinder retracts synchronously with the active cylinder. If yes, control the piston rod of the active cylinder to continue retracting to the preset position; otherwise, proceed to the next step.

[0038] The control throttling and reversing module supplies oil to both the rod chamber of the passive cylinder and the rod chamber of the active cylinder until the passive cylinder and the active cylinder retract synchronously to the preset position.

[0039] In the process of using the hydraulic system of the ship lift sealing frame provided by this invention, oil is supplied to the throttling and reversing module through the oil supply power component. In the initial stage, the throttling and reversing module supplies oil to the first active oil circuit. At this time, the pressure of the first active oil circuit is less than the opening pressure of the sequence valve, and the first active oil circuit and the first passive oil circuit are not connected. The throttling and reversing module only supplies oil to the rodless chamber of the active cylinder. At this time, it is only necessary to control the piston rod of the active cylinder to extend synchronously to achieve synchronous control. When the pressure of the first active oil circuit is greater than the opening pressure of the sequence valve, the first active oil circuit and the first passive oil circuit are connected. Hydraulic oil enters the first passive oil circuit from the first active oil circuit and supplies oil to the rodless chamber of the passive cylinder. The piston rod of the active cylinder and the piston of the passive cylinder... All rods extend, pushing the sealing frame to the docking position and applying pressure to it. Once the sealing frame is in place, the hydraulic system of the ship lift sealing frame is kept in a pressure-holding state. When the ship lift is disconnected from the gate head and the sealing frame is ready to retract, the throttling and reversing module supplies oil to the rod chamber of the active cylinder, causing the piston rod of the active cylinder to retract and drive the sealing frame to retract. During this process, the piston rod of the passive cylinder can be driven back by the sealing frame. If the guide slider of the sealing frame is stuck due to manufacturing or installation reasons, or if the frictional resistance is too high or even cannot retract, the throttling and reversing module can be controlled to supply oil to both the rod chamber of the active cylinder and the rod chamber of the passive cylinder simultaneously to increase the pushing force of the sealing frame and ensure that the sealing frame retracts normally.

[0040] Compared with the prior art, in the process of using the hydraulic system for the sealing frame of the ship lift provided by the present invention, only the synchronization of the active oil cylinder needs to be ensured during the extension of the sealing frame. This reduces the number of oil cylinders that need to be synchronized, lowers the control difficulty of maintaining synchronization, thereby reducing the cost of achieving synchronization requirements and improving the synchronization of the hydraulic system for the sealing frame of the ship lift.

[0041] In addition, the present invention also provides a control method for the hydraulic system of the sealing frame of the above-mentioned ship lift. Attached Figure Description

[0042] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the provided drawings without creative effort.

[0043] Figure 1 This is a schematic diagram of the active and passive hydraulic cylinders in the present invention at the installation position of the sealing frame;

[0044] Figure 2 for Figure 1 Side view of the middle structure;

[0045] Figure 3 for Figure 1 A cross-sectional view along the AA direction;

[0046] Figure 4 A schematic diagram of a specific embodiment of the hydraulic system for the sealing frame of the ship lift provided by the present invention;

[0047] Figure 5 This is a flowchart illustrating the control method provided by the present invention.

[0048] Figures 1-5 middle:

[0049] 01 is the active hydraulic cylinder, 02 is the passive hydraulic cylinder, 03 is the sealing frame, 04 is the bolt, 05 is the slider, 06 is the disc spring box, 1 is the oil tank, 2 is the motor, 3 is the variable pump, 4 is the second check valve, 5 is the solenoid reversing relief valve assembly, 6 is the safety valve, 7 is the first check valve, 8 is the fourth check valve, 9 is the first solenoid reversing valve, 10 is the first speed control valve, 11 is the second speed control valve, 12 is the first relief valve, 13 is the first hydraulically controlled check valve, 14 is the third speed control valve, 15 is the second solenoid reversing valve, 16 is the throttle valve, 1 7 is the fourth speed control valve, 18 is the second hydraulic check valve, 19 is the second relief valve, 20 is the third hydraulic check valve, 21 is the second solenoid ball valve, 22 is the #1 passive cylinder, 23 is the second proximity switch, 24 is the fourth relief valve, 25 is the normally open ball valve, 26 is the normally closed ball valve, 27 is the sequence valve, 28 is the fifth speed control valve, 29 is the sixth speed control valve, 30 is the first solenoid ball valve, 31 is the #2 active cylinder, 32 is the first proximity switch, 33 is the displacement sensor, 34 is the third relief valve, and 35 is the third check valve. Detailed Implementation

[0050] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0051] The core of this invention is to provide a hydraulic system for the sealing frame of a ship lift. During use, only the synchronization of the active cylinder can be restricted, which greatly reduces the difficulty of synchronization control, reduces control costs, and effectively improves the synchronization of the hydraulic system for the sealing frame of the ship lift.

[0052] Another core aspect of this invention is to provide a control method for the hydraulic system of the aforementioned ship lift sealing frame.

[0053] Please refer to Figures 1 to 5 .

[0054] This specific embodiment discloses a hydraulic system for a ship lift sealing frame, including:

[0055] Multiple active hydraulic cylinders 01, whose piston rods are connected to the sealing frame 03;

[0056] Multiple passive hydraulic cylinders 02, whose piston rods are connected to a sealing frame 03;

[0057] The oil supply power unit has its oil inlet end connected to the oil tank 1 and is used to draw hydraulic oil from the oil tank 1.

[0058] The throttling and reversing module has its inlet end connected to the outlet end of the oil supply power component, and is used to regulate the flow direction of hydraulic oil into the active cylinder 01 and the passive cylinder 02.

[0059] The throttling reversing module is connected to the rodless chamber of the active cylinder 01 through the first active oil circuit. The first active oil circuit is connected to the first passive oil circuit through the sequence valve 27. The first passive oil circuit is connected to the rodless chamber of the passive cylinder 02.

[0060] When the throttling and reversing module supplies oil to the first active oil circuit, and the pressure of the first active oil circuit is less than the opening pressure of the sequence valve 27, only the piston rod of the active oil cylinder 01 extends.

[0061] When the throttling and reversing module supplies oil to the first active oil circuit, and the pressure of the first active oil circuit is greater than the opening pressure of the sequence valve 27, the piston rods of the active cylinder 01 and the passive cylinder 02 both extend.

[0062] In the process of using the hydraulic system of the ship lift sealing frame provided in this specific embodiment, oil is supplied to the throttling and reversing module through the oil supply power component. In the initial stage, the throttling and reversing module supplies oil to the first active oil circuit. At this time, the pressure of the first active oil circuit is less than the opening pressure of the sequence valve 27, and the first active oil circuit and the first passive oil circuit are not connected. The throttling and reversing module only supplies oil to the rodless chamber of the active cylinder 01. At this time, it is only necessary to control the piston rod of the active cylinder 01 to extend synchronously to achieve synchronous control. When the pressure of the first active oil circuit is greater than the opening pressure of the sequence valve 27, the first active oil circuit and the first passive oil circuit are connected. Hydraulic oil enters the first passive oil circuit from the first active oil circuit and supplies oil to the rodless chamber of the passive cylinder 02. The piston rods of both the active cylinder 01 and the passive cylinder 02 extend, pushing... The sealing frame 03 moves to the docking position and pressure is applied to it. After the sealing frame 03 is in place, the hydraulic system of the ship lift sealing frame is kept in a pressure-holding state. When the ship lift is disconnected from the gate head and the sealing frame 03 is about to retract, the throttling and reversing module is controlled to supply oil to the rod chamber of the active cylinder 01, causing the piston rod of the active cylinder 01 to retract and drive the sealing frame 03 to retract. During this process, the piston rod of the passive cylinder 02 can be driven back by the sealing frame 03. If the guide slider 05 of the sealing frame 03 is stuck due to manufacturing or installation reasons, and the frictional resistance is too large or even cannot be retracted, the throttling and reversing module can be controlled to supply oil to the rod chamber of the active cylinder 01 and the rod chamber of the passive cylinder 02 at the same time to increase the pushing force of the sealing frame 03 and ensure that the sealing frame 03 retracts normally.

[0063] Compared to existing technologies, in the process of using the hydraulic system of the ship lift sealing frame provided in this specific embodiment, only the synchronization of the active cylinder 01 needs to be ensured during the extension of the sealing frame 03. This reduces the number of cylinders that need to be synchronized, lowers the control difficulty of maintaining synchronization, thereby reducing the cost of achieving synchronization requirements and improving the synchronization of the hydraulic system of the ship lift sealing frame.

[0064] Preferred, such as Figure 3 As shown, the piston rods of the active cylinder 01 and the passive cylinder 02 are connected to the sealing frame 03 by bolts 04 and disc spring boxes 06. Slider 05 is provided at both ends of the sealing frame 03. The disc spring boxes 06 can prevent the connection between the piston rods of the active cylinder 01 and the passive cylinder 02 and the sealing frame 03 from loosening, thus achieving a certain pressure holding effect.

[0065] In one specific embodiment, such as Figure 1 , 2 As shown, the sealing frame 03 has a U-shaped structure and is equipped with 11 hydraulic cylinders, of which 4 are active hydraulic cylinders 01 and 7 are passive hydraulic cylinders 02. Of course, the number and position of the active hydraulic cylinders 01 and passive hydraulic cylinders 02 can be adjusted according to different actual situations.

[0066] In one specific embodiment, such as Figure 4 As shown, the throttling and reversing module includes a first electromagnetic reversing valve 9 and a second electromagnetic reversing valve 15 arranged in parallel, and the P port of the first electromagnetic reversing valve 9 and the P port of the second electromagnetic reversing valve 15 are both connected to the oil outlet end of the oil supply power component; the T port of the first electromagnetic reversing valve 9 and the T port of the second electromagnetic reversing valve 15 are both connected to the return oil circuit that returns to the oil tank 1.

[0067] The A port of the first solenoid directional valve 9 is sequentially connected to the first speed control valve 10 and the first hydraulically controlled check valve 13. The P port of the first speed control valve 10 is connected to the A port of the first solenoid directional valve 9, and the A port of the first speed control valve 10 is connected to the A port of the first hydraulically controlled check valve 13. The B port of the first hydraulically controlled check valve 13 is connected to the first active oil circuit, and the K port of the first hydraulically controlled check valve 13 is connected to the A port of the second speed control valve 11. The B port of the first solenoid directional valve 9 is connected to the P port of the second speed control valve 11. The B port of the second solenoid directional valve 15 is connected to the P port of the third speed control valve 14, and the A port of the second solenoid directional valve 15 is sequentially connected to... The system is equipped with a fourth speed control valve 17 and a second hydraulically controlled check valve 18. The A port of the second solenoid directional valve 15 is connected to the P port of the fourth speed control valve 17, the A port of the fourth speed control valve 17 is connected to the A port of the second hydraulically controlled check valve 18, the B port of the second hydraulically controlled check valve 18 is connected to the first active oil circuit, and the K port of the second hydraulically controlled check valve 18 is connected to the A port of the third speed control valve 14. The first hydraulically controlled check valve 13 and the second hydraulically controlled check valve 18 are both connected to the first active oil circuit. The third speed control valve 14 is connected to the second active oil circuit of the rod chamber of the active cylinder 01 and the second passive oil circuit of the rod chamber of the passive cylinder 02.

[0068] A first overflow valve 12 is connected between the third speed control valve 14 and the second active oil circuit, and the other end of the first overflow valve 12 is connected to the oil tank 1.

[0069] A second relief valve 19 is connected between the second hydraulic control check valve 18 and the first active oil circuit, and the other end of the second relief valve 19 is connected to the oil tank 1.

[0070] In practical use, when it is necessary to push the sealing frame 03 forward, the second solenoid directional valve 15 is generally opened and the first solenoid directional valve 9 is closed, so that the hydraulic oil flowing out from the oil supply power component enters the P port of the second solenoid directional valve 15 and flows out from the A port of the first solenoid directional valve 9. It then flows through the fourth speed control valve 17 and the second hydraulic control check valve 18 in sequence to enter the first active oil circuit, thereby entering the rodless chamber of the active cylinder 01 and pushing the piston rod of the active cylinder 01 to extend. When the pressure of the first active oil circuit is greater than the opening pressure of the sequence valve 27, the hydraulic oil of the first active oil circuit enters the first passive oil circuit through the third check valve 35, thereby flowing into the rodless chamber of the passive cylinder 02. The piston rods of both the active cylinder 01 and the passive cylinder 02 extend.

[0071] It also includes a throttle valve 16, one end of which is connected to port A of the second solenoid directional valve 15, and the other end is connected to the first active oil circuit and the first passive oil circuit. When the pressure of the hydraulic oil flowing out of port A of the second solenoid directional valve 15 is too high, the hydraulic oil will flow into port A of the throttle valve 16 and flow out from port B of the throttle valve 16, directly entering the rodless chamber of the passive cylinder 02, so as to avoid the pressure of the hydraulic oil flowing out of port A of the second solenoid directional valve 15 being too high.

[0072] In one specific embodiment, such as Figure 4 As shown, it also includes a separate oil supply circuit. When the active oil cylinder 01 drives the sealing frame 03 to retract and the sealing frame 03 compresses the passive oil cylinder 02, the separate oil supply circuit supplies oil to the rod chamber of the passive oil cylinder 02.

[0073] One end of the separate oil supply circuit is connected to the oil tank 1, and the other end is connected to the rod chamber of the passive oil cylinder 02. A first check valve 7 is provided at the end of the separate oil supply circuit connected to the oil tank 1.

[0074] The first check valve 7 and the fourth check valve 8 in the return oil circuit are arranged side by side. The A port of the first check valve 7 and the B port of the fourth check valve 8 are both connected to the oil tank 1, and the B port of the first check valve 7 and the A port of the fourth check valve 8 are both connected to the return oil circuit.

[0075] The oil supply power assembly includes a motor 2, a variable pump 3 connected to the motor 2 via a coupling, an electromagnetic reversing relief valve group 5 connected to the variable pump 3, and a second check valve 4. The oil inlet of the variable pump 3 is connected to the oil tank 1, the oil outlet is connected to the A port of the second check valve 4, and the B port of the second check valve 4 is connected to the oil inlet of the throttling reversing module.

[0076] The electromagnetic reversing relief valve assembly 5 is used to adjust the working pressure of the hydraulic system of the ship lift sealing frame. The A end of the electromagnetic reversing relief valve assembly 5 is connected to the variable pump 3, and the B end of the electromagnetic reversing relief valve assembly 5 is connected to the oil tank 1.

[0077] like Figure 4 As shown, the B port of the second check valve 4 is connected to the A port of the safety valve 6, and the B port of the safety valve 6 is connected to the B port of the first check valve 7 and the A port of the fourth check valve 8.

[0078] like Figure 4As shown, cylinders #2, #5, #7, and #10 are all active cylinders 01. Active cylinders #2 (31), #5, #7, and #10 are all equipped with a first proximity switch 32 and a displacement sensor 33. Passive cylinders #1 (22), #3, #4, #6, #8, #9, and #11 are all equipped with a second proximity switch 23. Cylinders #, #8, #9, and #11 are all passive cylinders 02. The first active oil circuit includes a fifth speed control valve 28, a sixth speed control valve 29, and a first solenoid ball valve 30 connected in sequence. The P port of the fifth speed control valve 28 is connected to the throttling reversing module, the A port of the fifth speed control valve 28 is connected to the P port of the sixth speed control valve 29, the A port of the sixth speed control valve 29 is connected to the P port of the first solenoid ball valve 30, and the A port of the first solenoid ball valve 30 is connected to the rodless chamber of the active cylinder 01.

[0079] The third check valve 35 is connected in parallel with the sequence valve 27. The B port of the third check valve 35 and the P port of the fifth speed control valve 28 are both connected to the P port of the sequence valve 27. The A port of the sequence valve 27 is connected to the A port of the third check valve 35. The K port of the sequence valve 27 is connected to the P port of the sixth speed control valve 29. The T port of the sequence valve 27 is connected to the return oil circuit connected to the oil tank 1.

[0080] The rod chamber of the active cylinder 01 is connected to the throttling reversing module, and the rod chamber of the active cylinder 01 is connected to the P port of the third relief valve 34. The T port of the third relief valve 34 is connected to the T port of the sequence valve 27 and the return oil circuit connected to the oil tank 1.

[0081] The first passive oil circuit includes a third hydraulically controlled check valve 20 and a second solenoid ball valve 21. The B port of the third hydraulically controlled check valve 20 is connected to the P port of the second solenoid ball valve 21. The A port of the second solenoid ball valve 21 is connected to the rodless chamber of the passive cylinder 02. The A port of the sequence valve 27 is connected to the P port of the second solenoid ball valve 21. The A port of the third hydraulically controlled check valve 20 is connected to the return oil circuit to the oil tank 1 and the B port of the first check valve 7. The rod chamber of the passive cylinder 02 is connected to the throttling module through the normally closed ball valve 26. Port A of the normally closed ball valve 26 is connected to port B of the normally open ball valve 25 and port T of the fourth relief valve 24. Port A of the normally open ball valve 25 is connected to port A of the third hydraulic control check valve 20 and port P of the fourth relief valve 24. Port K of the third hydraulic control check valve 20 is connected to port B of the normally closed ball valve 26. Port B of the normally closed ball valve 26 is connected to port A of the third speed control valve 14.

[0082] In use such Figure 4During the hydraulic system operation shown, when the ship lift is docked with the gate head and the sealing frame 03 is ready to be pushed out, the motor 2 starts, the left side of the solenoid reversing relief valve group 5 is energized, and a higher working pressure is established in the system; the second solenoid reversing valve 15 is energized, the first solenoid reversing valve 9 is de-energized, and the hydraulic oil flows into the P port of the second solenoid reversing valve 15 through the variable pump 3 and the second check valve 4, and flows out through the A port of the second solenoid reversing valve 15, flowing sequentially through the fourth speed control valve 17 and the second hydraulic control check valve 18 into the first active oil circuit. The first solenoid ball valve 30 is in the left open position, and the hydraulic oil flows sequentially through the fifth speed control valve 28, the sixth speed control valve 29, and the first solenoid ball valve. 30. The oil enters the rodless chamber of the active cylinder 01. The rodless chamber circuits of the four active cylinders 01 are circulated with oil. When the system pressure gradually rises to the opening pressure of the sequence valve 27, the hydraulic oil branch flows from the first active oil circuit into the first passive oil circuit. The second solenoid ball valve 21 is in the left open position and flows through the second solenoid ball valve 21 in sequence into the rodless chamber of the seven passive cylinders 02. The eleven cylinders drive the sealing frame 03 to move to the docking position and apply pressure. When the sealing frame 03 moves to the docking position, the limit switch of the cylinder is triggered, and the sealing frame 03 is pushed out to the position. At this time, the relevant valves of the hydraulic system of the ship lift sealing frame are closed, and the pressure holding stage is entered.

[0083] During the sealing process, the 11 hydraulic cylinders are pressure-maintained by coupling the disc spring box 06 and the hydraulic oil circuit. When the system pressure drops due to leakage or other reasons, the pressure replenishment oil circuit is activated to replenish the pressure. During this process, since the system is in the pressure-maintaining stage, the piston rod of the hydraulic cylinder is not pushed back a large distance under normal circumstances. When the pressure in the rodless chamber drops significantly, the amount of oil required for replenishment during the oil replenishment process is much smaller than the amount of oil when the sealing frame 03 is normally removed. At this time, the first solenoid directional valve 9, motor 2, and variable pump 3, which have a smaller flow rate than the second solenoid directional valve 15, can be opened. The hydraulic oil flows through the second check valve 4 via B. The oil flows into the P port of the first solenoid directional valve 9 and out through the A port of the first solenoid directional valve 9 to the first speed control valve 10 and the first hydraulic control check valve 13. The oil then enters the first active oil circuit through the first hydraulic control check valve 13 to replenish the rodless chamber of the active cylinder 01. When the system pressure gradually rises to the opening pressure of the sequence valve 27, the hydraulic oil branch flows from the first active oil circuit into the first passive oil circuit. The second solenoid ball valve 21 is in the left open position and flows through the second solenoid ball valve 21 in sequence into the rodless chamber of the 7 passive cylinders 02, thus replenishing the oil for the 11 cylinders.

[0084] In this specific embodiment, in addition to the disc spring box 06 having a certain pressure holding effect, the hydraulic system itself has a certain pressure holding function. It is equipped with double seals, has excellent pressure holding effect, and does not require frequent starting or setting up an accumulator for pressure holding, thus saving energy and cost.

[0085] When the ship lift and the gate head disconnect the sealing frame 03 and prepare to retract, firstly, the 11 hydraulic cylinders depressurize, the motor 2 starts, and the right side of the electromagnetic reversing overflow valve group 5 is energized, establishing a lower working pressure in the system. Under normal working conditions, hydraulic oil flows from port B of the second check valve 4 into port P of the second electromagnetic reversing valve 15, and then flows out from port B of the second electromagnetic reversing valve 15, sequentially passing through the third speed regulating valve 14 and entering the rod chamber of the active hydraulic cylinder 01, increasing the pressure in the rod chamber of the active hydraulic cylinder 01, thereby causing the piston rod of the active hydraulic cylinder 01 to drive the sealing frame 03 to retract. During this process, to avoid impact and collision during retraction, the hydraulic oil in the rodless chamber of the active cylinder 01 generally flows sequentially through the first solenoid ball valve 30, the sixth speed control valve 29, the fifth speed control valve 28, the first hydraulic check valve 13, and the first speed control valve 10 into the first solenoid directional valve 9, and then flows out through the T port of the first solenoid directional valve 9 to the oil tank 1. During this process, when the sealing frame 03 pushes the piston rod of the passive cylinder 02 and can make the piston rod of the passive cylinder 02 retract normally, the pressure in the rod chamber of the passive cylinder 02 decreases, and oil will be replenished to the rod chamber of the passive cylinder 02 through the first check valve 7 and the normally open ball valve 25 so that the piston rod of the passive cylinder 02 can retract smoothly. When the sealing frame 03 pushes the piston rod of the passive cylinder 02, but the guide slider 05 of the sealing frame 03 is stuck due to manufacturing or installation reasons, especially when the frictional resistance is too large near the U-shaped corner, or even when the sealing frame 03 cannot retract, the working state of the normally open ball valve 25 and the normally closed ball valve 26 can be adjusted. The normally open ball valve 25 is adjusted to be closed, and the normally closed ball valve 26 is adjusted to be open, so that the hydraulic oil can enter the rod chamber of the passive cylinder 02 through the B port of the second hydraulic control check valve 18 through the normally closed ball valve 26, so that the 11 cylinders work together to pull the sealing frame 03 back, so that the ship lift is disconnected from the lock head and the sealing frame 03 is disconnected.

[0086] In this application, the extension or retraction of the sealing frame 03 is synchronously controlled by two speed regulating valves of the control valve group of the active hydraulic cylinder 01, with the displacement sensor serving as a reference. Due to its short stroke, the synchronization requirements can be met. The system pressure required for the extension (pressure tightening) and retraction of the sealing frame 03 differs significantly. Setting different working pressures can reduce power consumption losses caused by oil pump overflow, achieving energy-saving effects.

[0087] In addition to the aforementioned hydraulic system for the sealing frame of a ship lift, the present invention also provides a control method for the hydraulic system for the sealing frame of a ship lift applied to any of the above-mentioned claims, the control method comprising:

[0088] Step S1: Control the start of the fuel supply power unit;

[0089] Step S2: Control the throttling and reversing module to supply oil to the rodless chamber of the active cylinder 01 so that the piston of the active cylinder 01 extends.

[0090] Step S3: When the pressure of the first active oil circuit is greater than the opening pressure of the sequence valve 27, oil is supplied to the rodless chamber of the passive cylinder 02.

[0091] Step S4: Determine whether the sealing frame 03 has been pushed out to the correct position. If yes, proceed to the next step. If no, control the throttling and reversing module to continuously supply oil to the rodless chamber of the active cylinder 01 and the rodless chamber of the passive cylinder 02.

[0092] Step S5: Control the oil supply power component and throttling reversing module to enter the pressure holding state, and maintain the pressure holding state for a preset time.

[0093] Step S6: Control the throttling and reversing module to supply oil to the rod chamber of the active cylinder 01 so that the piston of the active cylinder 01 extends.

[0094] Step S7: Determine whether the passive cylinder 02 retracts synchronously with the active cylinder 01. If yes, control the piston rod of the active cylinder 01 to continue retracting to the preset position; otherwise, proceed to the next step.

[0095] Step S8: Control the throttling and reversing module to supply oil to both the rod chamber of the passive cylinder 02 and the rod chamber of the active cylinder 01 until the passive cylinder 02 and the active cylinder 01 retract synchronously to the preset position.

[0096] The terms "first," "second," "third," "fourth," "fifth," and "sixth" in the first check valve 7, second check valve 4, third check valve 35, and fourth check valve 8, first solenoid ball valve 30 and second solenoid ball valve 21, first hydraulically controlled check valve 13 and second hydraulically controlled check valve 18, first solenoid directional valve 9 and second solenoid directional valve 15, first speed control valve 10, second speed control valve 11, third speed control valve 14, fourth speed control valve 17, fifth speed control valve 28 and sixth speed control valve 29, first relief valve 12, second relief valve 19 and third relief valve 34 mentioned in this application are only for distinguishing different positions and do not indicate any order.

[0097] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. Any combination of all embodiments provided by this invention is within the scope of protection of this invention and will not be elaborated upon here.

[0098] The hydraulic system and control method for the sealing frame of the ship lift provided by this invention have been described in detail above. Specific examples have been used to illustrate the principles and implementation methods of this invention. The descriptions of the embodiments above are only for the purpose of helping to understand the method and core ideas of this invention. It should be noted that those skilled in the art can make several improvements and modifications to this invention without departing from the principles of this invention, and these improvements and modifications also fall within the protection scope of the claims of this invention.

Claims

1. A hydraulic system for a ship lift sealing frame, characterized in that, include: Multiple active hydraulic cylinders (01) have piston rods connected to a sealing frame (03); Multiple passive hydraulic cylinders (02) have piston rods connected to the sealing frame (03); The oil supply power assembly has its oil inlet end connected to the oil tank (1) for drawing hydraulic oil from the oil tank (1); The throttling and reversing module has its inlet end connected to the outlet end of the oil supply power component, and is used to regulate the flow direction of hydraulic oil flowing into the active cylinder (01) and the passive cylinder (02); The throttling reversing module is connected to the rodless chamber of the active cylinder (01) through a first active oil circuit. The first active oil circuit is connected to the first passive oil circuit through a sequence valve (27). The first passive oil circuit is connected to the rodless chamber of the passive cylinder (02). When the throttling reversing module supplies oil to the first active oil circuit, and the pressure of the first active oil circuit is less than the opening pressure of the sequence valve (27), only the piston rod of the active oil cylinder (01) extends. When the throttling reversing module supplies oil to the first active oil circuit, and the pressure of the first active oil circuit is greater than the opening pressure of the sequence valve (27), the piston rod of the active oil cylinder (01) and the piston rod of the passive oil cylinder (02) both extend. The throttling and reversing module includes a first electromagnetic reversing valve (9) and a second electromagnetic reversing valve (15) arranged in parallel. The P port of the first electromagnetic reversing valve (9) and the P port of the second electromagnetic reversing valve (15) are both connected to the oil outlet of the oil supply power component. The T port of the first electromagnetic reversing valve (9) and the T port of the second electromagnetic reversing valve (15) are both connected to and return to the return oil circuit of the oil tank (1). The first electromagnetic directional valve (9) is connected in sequence to the first speed control valve (10) and the first hydraulic check valve (13) at port A; the first electromagnetic directional valve (9) is connected to the second speed control valve (11) at port B; the second electromagnetic directional valve (15) is connected to the third speed control valve (14) at port B; the second electromagnetic directional valve (15) is connected to the fourth speed control valve (17) and the second hydraulic check valve (18) at port A; the first hydraulic check valve (13) and the second hydraulic check valve (18) are both connected to the first active oil circuit; the third speed control valve (14) is connected to the second active oil circuit connected to the rod chamber of the active cylinder (01) and the second passive oil circuit connected to the rod chamber of the passive cylinder (02).

2. The hydraulic system for the sealing frame of the ship lift according to claim 1, characterized in that, A first overflow valve (12) is connected between the third speed regulating valve (14) and the second active oil circuit, and the other end of the first overflow valve (12) is connected to the oil tank (1). A second relief valve (19) is connected between the second hydraulic control check valve (18) and the first active oil circuit, and the other end of the second relief valve (19) is connected to the oil tank (1).

3. The hydraulic system for the sealing frame of the ship lift according to claim 1, characterized in that, The throttling and reversing module also includes a throttling valve (16), one end of which is connected to port A of the second electromagnetic reversing valve (15), and the other end is connected to the first active oil circuit and the first passive oil circuit.

4. The hydraulic system for the sealing frame of the ship lift according to claim 1, characterized in that, The throttling and reversing module also includes a separate oil supply circuit. When the active cylinder (01) drives the sealing frame (03) to retract and the sealing frame (03) compresses the passive cylinder (02), the separate oil supply circuit supplies oil to the rod chamber of the passive cylinder (02). One end of the separate oil supply circuit is connected to the oil tank (1), and the other end is connected to the rod chamber of the passive cylinder (02). A first check valve (7) is provided at the end of the separate oil supply circuit connected to the oil tank (1).

5. The hydraulic system for the sealing frame of the ship lift according to any one of claims 1-4, characterized in that, The oil supply power assembly includes a motor (2), a variable pump (3) connected to the motor (2) via a coupling, an electromagnetic reversing overflow valve group (5) connected to the variable pump (3), and a second check valve (4). The oil inlet of the variable pump (3) is connected to the oil tank (1), and the oil outlet is connected to the A port of the second check valve (4). The B port of the second check valve (4) is connected to the oil inlet of the throttling reversing module. The electromagnetic reversing overflow valve group (5) is used to adjust the working pressure of the hydraulic system of the ship lift sealing frame.

6. The hydraulic system for the sealing frame of the ship lift according to any one of claims 1-4, characterized in that, The first active oil circuit includes a fifth speed control valve (28), a sixth speed control valve (29), and a first electromagnetic ball valve (30) connected in sequence. The fifth speed control valve (28) is connected to the throttling reversing module, and the first electromagnetic ball valve (30) is connected to the rodless chamber of the active oil cylinder (01). The third check valve (35) is connected in parallel with the sequence valve (27). The B port of the third check valve (35) and the P port of the fifth speed control valve (28) are both connected to the P port of the sequence valve (27). The A port of the sequence valve (27) is connected to the A port of the third check valve (35). The K port of the sequence valve (27) is connected to the P port of the sixth speed control valve (29). The T port of the sequence valve (27) is connected to the return oil circuit connected to the oil tank (1).

7. The hydraulic system for the sealing frame of the ship lift according to claim 6, characterized in that, The rod chamber of the active cylinder (01) is connected to the throttling reversing module, and the rod chamber of the active cylinder (01) and the throttling reversing module are connected to the P port of the third overflow valve (34). The T port of the third overflow valve (34) is connected to the T port of the sequence valve (27) and the return oil circuit connected to the oil tank (1).

8. The hydraulic system for the sealing frame of the ship lift according to any one of claims 1-4, characterized in that, The first passive oil circuit includes a third hydraulic control check valve (20) and a second solenoid ball valve (21). The B port of the third hydraulic control check valve (20) is connected to the P port of the second solenoid ball valve (21). The A port of the second solenoid ball valve (21) is connected to the rodless chamber of the passive oil cylinder (02). The A port of the sequence valve (27) is connected to the P port of the second solenoid ball valve (21).

9. The hydraulic system for the sealing frame of the ship lift according to claim 8, characterized in that, The rod chamber of the passive cylinder (02) is connected to the throttling reversing module through a normally closed ball valve (26). The A port of the normally closed ball valve (26) is connected to the B port of the normally open ball valve (25) and the T port of the fourth relief valve (24). The A port of the normally open ball valve (25) is connected to the A port of the third hydraulic control check valve (20) and the P port of the fourth relief valve (24). The K port of the third hydraulic control check valve (20) is connected to the B port of the normally closed ball valve (26).

10. A control method applied to the hydraulic system of the ship lift sealing frame as described in any one of claims 1-9, characterized in that, The control method includes: Control the start-up of the fuel supply power unit; The control throttling module supplies oil to the rodless chamber of the active cylinder (01) so that the piston of the active cylinder (01) extends; When the pressure of the first active oil circuit is greater than the opening pressure of the sequence valve (27), oil is supplied to the rodless chamber of the passive oil cylinder (02); Determine whether the sealing frame (03) has been pushed out to the correct position. If yes, proceed to the next step. If no, control the throttling and reversing module to continuously supply oil to the rodless chamber of the active cylinder (01) and the rodless chamber of the passive cylinder (02). The oil supply power component and the throttling reversing module are controlled to enter the pressure holding state and remain in the pressure holding state for a preset time. The control throttling module supplies oil to the rod chamber of the active cylinder (01) so that the piston of the active cylinder (01) extends; Determine whether the passive cylinder (02) retracts synchronously with the active cylinder (01). If yes, control the piston rod of the active cylinder (01) to continue retracting to the preset position. If no, proceed to the next step. The control throttling and reversing module supplies oil to both the rod chamber of the passive cylinder (02) and the rod chamber of the active cylinder (01) until the passive cylinder (02) and the active cylinder (01) retract synchronously to the preset position.

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