A hydraulic system for anti-collision beams of a ship lift

Abstract

The present invention discloses a hydraulic system for a ship lift's anti-collision beam, comprising a fuel tank and a motor. The fuel tank includes a return oil circuit and a supply oil circuit. The return oil circuit and the supply oil circuit are connected in series via a pipeline, which is equipped with a safety valve and separates the pipeline into a supply line and a return oil line. A variable pump and a first check valve are connected in series in the supply line, the variable pump being positioned near the fuel tank and driven by the motor. A first ball valve is provided at the output end of the check valve, with a pressure compensator connected between the output end of the first ball valve and the oil inlet of the proportional reversing valve. A second check valve is connected to the return oil line, with a cartridge valve group connected in parallel between the input end of the second check valve and the oil circuit connecting the first ball valve and the pressure compensator. This invention replaces the hydraulic circuit that drives the oil cylinder piston rod to push the anti-collision beam downward with a differential circuit, significantly improving the anti-collision beam lowering time, enhancing the navigation efficiency of the ship lift, and reducing system configuration and cost.

Description

Technical Field

[0001] The invention relates to the technical field of ship lift engineering, and in particular to a ship lift anti-collision beam hydraulic system. Background Art

[0002] Common ship lift anti-collision devices are typically installed near the upstream and downstream folding gates of the ship carriage. Some ship lift lockheads also have them to prevent stalled vessels from colliding with the folding gates. These devices typically consist of a box-section anti-collision beam, fixed pulleys, movable pulleys, wire ropes, drive cylinders, and a hydraulic system. Two hydraulic cylinders, symmetrically located within the left and right longitudinal beams of the ship carriage, drive the beam up and down within the guide groove via a pulley block and wire rope. Due to the limited clearance between the guide groove and the anti-collision beam, strict synchronization of the drive cylinders is required.

[0003] In current ship lift engineering cases, the hydraulic system of the anti-collision device generally uses a proportional speed control valve + speed control valve in parallel for synchronous correction, or a speed control valve + bypass reversing valve for leakage and oil release correction. The synchronization effect is less than ideal. On the one hand, the anti-collision beam moves up and down in the guide rail groove, causing jamming and friction. The loads of the two drive cylinders are changing and fluctuating greatly. The bypass oil release method may cause hydraulic shock and reduce synchronization performance. Generally speaking, the operating speed of these engineering cases is relatively slow, and the extension time of the anti-collision beam drive cylinder is generally longer than the retraction time. The working stroke of the drive cylinder is generally large, and the operating time is longer than that of other mechanisms. To shorten the operating time, the current anti-collision device hydraulic system is generally equipped with a larger motor pump source, which is more expensive or prolongs the operating time, reducing navigation efficiency. Summary of the Invention

[0004] The purpose of the present invention is to provide a hydraulic system for an anti-collision device with reasonable structural design, high operating speed, low cost and good synchronization.

[0005] In order to achieve the above-mentioned object, the present invention provides the following technical solution: a ship lift anti-collision beam hydraulic system, comprising an oil tank and a motor, wherein the oil tank comprises an oil return line and an oil supply line, wherein:

[0006] The oil return line and the oil supply line are connected in series through a pipeline, and a safety valve is provided on the pipeline, and the safety valve divides the pipeline into a supply pipeline and an oil return pipeline;

[0007] A variable pump and a first one-way valve are sequentially connected in series on the supply pipeline, the variable pump is arranged close to the oil tank and is driven by the motor;

[0008] The output end of the one-way valve is provided with a first ball valve, and a pressure compensator is fixedly connected between the output end of the first ball valve and the oil inlet of the proportional reversing valve;

[0009] The oil return line is connected to a second one-way valve, and an oil line connected between the input end of the second one-way valve and the first ball valve and the pressure compensator is connected in parallel to a cartridge valve group;

[0010] The oil circuit between the first ball valve and the pressure compensator is connected in parallel with the oil circuit of the cartridge valve group input port) with a third one-way valve, and the oil circuit at the output end of the pressure compensator and the oil circuit at the input end of the cartridge valve group are proportional reversing valves.

[0011] Preferably, an electromagnetic reversing overflow valve group is fixedly connected between the variable pump and the oil tank.

[0012] Preferably, the pressure compensator is respectively arranged before the proportional reversing valve and before the rod chamber of the driving cylinder merges with the pump source pressure oil.

[0013] Preferably, a second ball valve is connected to the first output end pipeline of the proportional reversing valve, and a first pressure measuring joint, a first pressure relay and a relief valve are connected in parallel on the oil line, and the overflow port of the relief valve is connected to the input end of the second one-way valve.

[0014] Preferably, the input end oil circuit of the second one-way valve is connected to the overflow port of the second overflow valve, and the second output end oil circuit of the proportional reversing valve is connected in parallel with a third ball valve, a second pressure relay, a second pressure measuring joint and the second overflow valve.

[0015] Preferably, the third ball valve and the second ball valve are connected to a driving cylinder, and the driving cylinder is provided with a balancing valve group, and the driving cylinder is provided with two proximity switches and a displacement sensor.

[0016] A method for controlling the hydraulic pressure of a ship lift anti-collision beam is applied to the hydraulic system of the ship lift anti-collision beam described in the above-mentioned solution, and further includes components such as an anti-collision beam, a pulley assembly, and a steel wire rope. The hydraulic system performs hydraulic oil supply and oil return during the vertical movement of the anti-collision beam and is movably assembled into the following two motion states:

[0017] When the anti-collision beam rises:

[0018] 1) When the piston rod on the driving oil cylinder retracts, the motor starts, and the electromagnetic relief valve group is energized to establish a lower system working pressure;

[0019] 2) The pressure oil enters the rod chamber of the driving cylinder through the variable pump, the first one-way valve, the first ball valve, the pressure compensator, the proportional reversing valve, the second ball valve and the balancing valve group. At this time, the hydraulic oil in the rodless chamber returns to the oil tank through the balancing valve group, the third ball valve, the proportional reversing valve, the cartridge valve group and the second one-way valve;

[0020] When the anti-collision beam descends:

[0021] 3) When the piston rod on the driving oil cylinder extends, the motor starts, and the electromagnetic relief valve group is energized to establish a lower system working pressure;

[0022] 4) The plug-in valve group is energized to close the oil circuit, and the pump source pressure oil enters the rodless chamber of the driving cylinder through the first one-way valve, the first ball valve, the pressure compensator, the proportional reversing valve, the second ball valve and the balancing valve group. The hydraulic oil in the rod chamber of the driving cylinder also passes the balancing valve group, the second ball valve, the proportional reversing valve, the third one-way valve, the pressure compensator, the proportional reversing valve, the third ball valve and the balancing valve group into the rodless chamber of the driving cylinder. Then the circuit of the hydraulic system constitutes a differential circuit to accelerate the extension speed of the piston rod of the driving cylinder.

[0023] Preferably, there are two driving cylinders, both of which are used to drive the anti-collision beam to rise and fall.

[0024] In the above technical solution, the present invention provides a ship lift anti-collision beam hydraulic system, which has the following beneficial effects: the hydraulic circuit that drives the cylinder piston rod to push the anti-collision beam down is changed to a differential circuit, which greatly improves the lowering time of the anti-collision beam, improves the navigation efficiency of the ship lift, and reduces the system configuration and cost; and ensures the synchronization of the two cylinders under larger flow rates or faster operating speeds. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments described in the present invention. For ordinary technicians in this field, other drawings can also be obtained based on these drawings.

[0026] Figure 1 This is a schematic structural diagram of the hydraulic system of the anti-collision device provided in an embodiment of the present invention.

[0027] Description of reference numerals:

[0028] 1. Fuel tank; 2. Motor; 3. Variable pump; 4. First one-way valve; 5. Solenoid reversing relief valve group; 6. Safety valve; 7. First ball valve; 8. Second one-way valve; 9. Insert valve group; 10. Third one-way valve; 11. Pressure compensator; 12. Proportional reversing valve; 13. First relief valve; 14. Second relief valve; 15. First pressure measuring joint; 16. First pressure relay; 17. Second ball valve; 18. Third ball valve; 19. Second pressure relay; 20. Second pressure measuring joint; 21. Balancing valve group; 22. Proximity switch; 23. Drive cylinder; 24. Displacement sensor. DETAILED DESCRIPTION

[0029] In order to enable those skilled in the art to better understand the technical solution of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings.

[0030] Example 1

[0031] like Figure 1 As shown, a hydraulic system for a ship lift anti-collision beam includes an oil tank 1 and a motor 2. The oil tank 1 includes an oil return line and an oil supply line, wherein:

[0032] The oil return line and the supply line are connected in series through a pipeline, and a safety valve 6 is provided on the pipeline, and the pipeline is divided into a supply pipeline and an oil return pipeline by the safety valve 6;

[0033] The supply pipeline is connected in series with a variable pump 3 and a first one-way valve 4. The variable pump 3 is arranged close to the oil tank 1 and is driven by the motor 2.

[0034] The output end of the one-way valve 4 is provided with a first ball valve 7, and a pressure compensator 11 is fixedly connected between the output end of the first ball valve 7 and the oil inlet of the proportional reversing valve (12);

[0035] The oil return line is connected to a second one-way valve 8, and the oil line between the input end of the second one-way valve 8 and the first ball valve 7 and the pressure compensator 11 is connected in parallel to a cartridge valve group 9;

[0036] The oil circuit between the first ball valve 7 and the pressure compensator 11 is connected in parallel with the pipeline at the input end of the cartridge valve group 9 to connect with a third one-way valve 10, and the oil circuit at the output end of the pressure compensator 11 is connected to the oil circuit at the input end of the cartridge valve group 9 to connect with the proportional reversing valve 12;

[0037] The oil circuit at the first output end of the proportional reversing valve 12 is connected to a second ball valve 17 , and the oil circuit is connected in parallel to a first pressure measuring joint 15 , a first pressure relay 16 and a relief valve 13 , and the overflow port of the relief valve 13 is connected to the input end of the second one-way valve 8 .

[0038] The input end oil circuit of the second one-way valve 8 is fixedly connected to the overflow port of the second overflow valve 14, and the second output end oil circuit of the proportional reversing valve 12 is connected in parallel to the third ball valve 18, the second pressure relay 19, the second pressure measuring joint 20 and the second overflow valve 14.

[0039] The output ends of the third ball valve 18 and the second ball valve 17 are fixedly connected to a driving cylinder 23 , and a balancing valve group 21 is provided on the driving cylinder 23 . The driving cylinder 23 is provided with two proximity switches 22 and a displacement sensor 24 .

[0040] Specifically, there are two drive cylinders 23, both used to drive the anti-collision beam up and down. The two anti-collision beam drive cylinders 23, displacement sensor 24, proportional reversing valve 12, and upper computer PLC constitute a master-slave dual-cylinder position closed-loop synchronous control system. The displacement of one drive cylinder 23 is used as a reference, and the other drive cylinder 23 follows. Whether it's a differential circuit (where the pump source pressure oil merges with the return oil from the rod chamber) or a normal circuit (where the rod chamber retracts), the pressure compensator can maintain a constant pressure differential across the proportional reversing valve. The flow rate change of the proportional reversing valve is only related to the electrical signal output by the PLC and is immune to the effects of load changes, thus better ensuring the strict synchronization of the dual-cylinder operation.

[0041] Furthermore, in the above embodiment, an electromagnetic reversing relief valve group 5 is fixedly connected between the variable displacement pump 3 and the oil tank 1 .

[0042] Furthermore, in the above embodiment, the pressure compensator 11 is respectively arranged before the proportional reversing valve 12 and before the rod chamber of the driving cylinder 23 merges with the pump source pressure oil.

[0043] In the above technical solution, the hydraulic circuit for driving the piston rod of the oil cylinder 23 to push the anti-collision beam down is changed to a differential circuit, which greatly improves the lowering time of the anti-collision beam, improves the navigation efficiency of the ship lift, reduces the system configuration and cost; and ensures the synchronization of the two cylinders under large flow or fast operating speed.

[0044] Example 2

[0045] A method for controlling the hydraulic pressure of a ship lift anti-collision beam is applied to the hydraulic system of the ship lift anti-collision beam provided in Example 2, and further includes components such as an anti-collision beam, a pulley assembly, and a wire rope. The hydraulic system performs hydraulic oil supply and oil return during the vertical movement of the anti-collision beam and is movably assembled into the following two motion states:

[0046] When the anti-collision beam rises:

[0047] 1) When the piston rod on the driving cylinder 23 retracts, the motor 2 starts, and the electromagnetic relief valve group 5 is energized to establish a lower system working pressure;

[0048] 2) The pressure oil enters the rod chamber of the driving cylinder 23 through the variable pump 3, the first check valve 4, the first ball valve 7, the pressure compensator 9, the proportional reversing valve 10, the fourth check valve 14, the second ball valve 17 and the balancing valve group 21. At this time, the hydraulic oil in the rodless chamber passes through the balancing valve group 21, the third ball valve 18, the proportional reversing valve 10, and the second check valve 8 and then returns to the oil tank 1;

[0049] When the anti-collision beam is lowered:

[0050] 3) When the piston rod on the driving cylinder 23 extends, the motor 2 starts, and the electromagnetic relief valve group 5 is energized to establish a lower system working pressure;

[0051] 4) The pump source pressure oil enters the rodless cavity of the driving cylinder 23 through the first one-way valve 4, the first ball valve 7, the pressure compensator 9, the proportional reversing valve 10, the third ball valve 18 and the balancing valve group 21. The hydraulic oil in the rod cavity of the driving cylinder 23 also flows through the balancing valve group 21, the second ball valve 17, the balancing valve 12, the third one-way valve 11, the pressure compensator 9, the proportional reversing valve 10, the third ball valve 18 and the balancing valve group 21 into the rodless cavity of the driving cylinder 23. Then the circuit of the hydraulic system constitutes a differential circuit to accelerate the extension speed of the piston rod of the driving cylinder 23.

[0052] The above description is merely illustrative of certain exemplary embodiments of the present invention. It goes without saying that those skilled in the art will be able to modify the described embodiments in various ways without departing from the spirit and scope of the present invention. Therefore, the above drawings and description are illustrative in nature and should not be construed as limiting the scope of protection of the claims.

Claims

1. A ship lift anti-collision beam hydraulic system, characterized in that: It comprises an oil tank (1) and a motor (2), wherein the oil tank (1) comprises an oil return path and an oil supply path, wherein: The oil return line and the supply line are connected in series via a pipeline, and a safety valve (6) is provided on the pipeline, and the safety valve (6) divides the pipeline into a supply line and an oil return line; A variable pump (3) and a first one-way valve (4) are sequentially connected in series on the supply pipeline; the variable pump (3) is arranged close to the oil tank (1) and is driven by the motor (2); The output end of the one-way valve (4) is provided with a first ball valve (7), and a pressure compensator (11) is connected between the output end of the first ball valve (7) and the oil inlet of the proportional reversing valve (12); The oil return line is connected to a second one-way valve (8), and the oil line connecting the input end of the second one-way valve (8) and the first ball valve (7) and the pressure compensator (11) is connected in parallel to a cartridge valve group (9); The oil circuit between the first ball valve (7) and the pressure compensator (11) and the oil circuit at the input end of the cartridge valve group (9) are connected in parallel to a third one-way valve (10), and the oil circuit at the output end of the pressure compensator (11) and the oil circuit at the input end of the cartridge valve group (9) are connected to a proportional reversing valve (12); The oil circuit at the first output end of the proportional reversing valve (12) is connected to a second ball valve (17); A third ball valve (18), a second pressure relay (19), a second pressure measuring joint (20) and a second relief valve (14) are connected in parallel on the oil circuit at the second output end of the proportional reversing valve (12); The third ball valve (18) and the second ball valve (17) are connected to the driving oil cylinder (23), and the driving oil cylinder (23) has a rod cavity provided with a balancing valve group (21); When the anti-collision beam rises: The pressure oil enters the rod chamber of the driving oil cylinder (23) through the variable pump (3), the first one-way valve (4), the first ball valve (7), the pressure compensator (11), the proportional reversing valve (12), the second ball valve (17) and the balancing valve group (21). At this time, the hydraulic oil in the rodless chamber returns to the oil tank (1) through the balancing valve group (21), the third ball valve (18), the proportional reversing valve (12), the cartridge valve group (9) and the second one-way valve (8). When the anti-collision beam descends: The plug-in valve group (9) is energized to close the oil circuit, and the pump source pressure oil passes through the first one-way valve (4), the first ball valve (7), the pressure compensator (11), the proportional reversing valve (12), the third ball valve (18) and the balancing valve group (21) and enters the rodless chamber of the driving oil cylinder (23). The hydraulic oil in the rod chamber of the driving oil cylinder (23) also passes through the balancing valve group (21), the second ball valve (17), the proportional reversing valve (12), the third one-way valve (10), the pressure compensator (11), the proportional reversing valve (12), the third ball valve (18) and the balancing valve group (21) and enters the rodless chamber of the driving oil cylinder (23). Then, the circuit of the hydraulic system constitutes a differential circuit to accelerate the extension speed of the piston rod of the driving oil cylinder (23).

2. The ship lift anti-collision beam hydraulic system according to claim 1, characterized in that: An electromagnetic overflow valve group (5) is also fixedly connected between the variable pump (3) and the oil tank (1).

3. The ship lift anti-collision beam hydraulic system according to claim 1, characterized in that: The pressure compensator (11) is respectively arranged before the proportional reversing valve (12) and before the rod chamber of the driving oil cylinder (23) merges with the pump source pressure oil.

4. The ship lift anti-collision beam hydraulic system according to claim 1, characterized in that: The first output end oil circuit is connected in parallel with a first pressure measuring joint (15), a first pressure relay (16) and an overflow valve (13), and the overflow port of the overflow valve (13) is connected to the input end of the second one-way valve (8).

5. The ship lift anti-collision beam hydraulic system according to claim 4, characterized in that: The oil circuit at the input end of the second one-way valve (8) is connected to the overflow port of the second overflow valve (14).

6. The ship lift anti-collision beam hydraulic system according to claim 5, characterized in that: The driving oil cylinder (23) is provided with two proximity switches (22) and a displacement sensor (24).

7. A hydraulic control method for a ship lift anti-collision beam, characterized in that: The hydraulic system for the ship lift anti-collision beam as described in claim 2 further comprises an anti-collision beam, a pulley assembly, and a steel rope, wherein the hydraulic system performs hydraulic oil supply and oil return during the vertical movement of the anti-collision beam and is movably assembled into the following two motion states; When the anti-collision beam rises: 1) When the piston rod on the driving oil cylinder (23) is retracted, the motor (2) is started, and the electromagnetic relief valve group (5) is energized to establish a lower system working pressure; 2) The pressure oil enters the rod chamber of the driving oil cylinder (23) through the variable pump (3), the first one-way valve (4), the first ball valve (7), the pressure compensator (11), the proportional reversing valve (12), the second ball valve (17) and the balancing valve group (21). At this time, the hydraulic oil in the rodless chamber passes through the balancing valve group (21), the third ball valve (18), the proportional reversing valve (12), the cartridge valve group (9) and the second one-way valve (8) and then returns to the oil tank (1); When the anti-collision beam descends: 3) When the piston rod on the driving oil cylinder (23) extends, the motor (2) starts, and the electromagnetic relief valve group (5) is energized to establish a lower system working pressure; 4) The plug-in valve group (9) is energized to close the oil circuit, and the pump source pressure oil passes through the first one-way valve (4), the first ball valve (7), the pressure compensator (11), the proportional reversing valve (12), the third ball valve (18) and the balancing valve group (21) and enters the rodless chamber of the driving oil cylinder (23). The hydraulic oil in the rod chamber of the driving oil cylinder (23) also enters the balancing valve group (21), the second ball valve (17), the proportional reversing valve (12), the third one-way valve (10), the pressure compensator (11), the proportional reversing valve (12), the third ball valve (18) and the balancing valve group (21) into the rodless chamber of the driving oil cylinder (23). Then, the circuit of the hydraulic system constitutes a differential circuit to accelerate the extension speed of the piston rod of the driving oil cylinder (23).

8. The method for hydraulically controlling the anti-collision beam of a ship lift according to claim 7, characterized in that: There are two driving cylinders (23), both of which are used to drive the anti-collision beam to rise and fall.

9. An electronic device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein: When the processor executes the program, the steps of the hydraulic control method for the ship lift anti-collision beam according to any one of claims 7 to 8 are implemented.

10. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the steps of the hydraulic control method for the ship lift anti-collision beam according to any one of claims 7 to 8 are implemented.

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