A proportional multi-way valve applied to a wharf gangway

Abstract

The utility model discloses a kind of proportional multi-way valves applied to wharf gangway, hydraulic pump station motor provides power source and is equipped with proportional multi-way valve, proportional multi-way valve is as control element control the movement of swing motor, telescopic cylinder and amplitude cylinder, when boarding condition, through hydraulic pump station motor start amplitude cylinder, reversing valve three control amplitude cylinder and it is lifted to set height;Reversing valve one controls swing motor and it is rotated to the top of ship;Reversing valve two controls telescopic cylinder and it is extended to specified position;Micro-motion amplitude cylinder is carried on deck on gangway;Under compensation condition, hydraulic pump station motor stops working, telescopic cylinder and amplitude cylinder are freely floating, the utility model can ensure that gangway is stably operated under different load and dynamic change, and maintenance cost is reduced.

Description

Technical Field

[0001] This utility model belongs to the technical field of proportional multi-way valves, and relates to a proportional multi-way valve applied to dock gangways. Background Technology

[0002] As a boarding device, wave-compensated gangways must meet the requirement of safe and rapid passage of personnel between ships and docks or other structures. Taking into account the dynamic characteristics of ocean waves, wave-compensated gangways can remain stable under various sea conditions. Even in severe sea conditions, they ensure the safety and comfort of personnel, reducing the risks during boarding.

[0003] Currently, the gangway requires continuous power from the hydraulic station after being deployed on the ship's deck. This results in significant energy loss in the hydraulic transmission, leading to relatively low transmission efficiency. Furthermore, when the hydraulic pump's speed is too low, the natural suction capacity weakens, resulting in insufficient torque at low frequencies. This affects the stability and reliability of the gangway during operation, increasing the failure rate and leading to higher maintenance costs. Utility Model Content

[0004] To address the aforementioned problems in the existing technology, this application provides a proportional multi-way valve applicable to dock gangways.

[0005] The technical solution of this utility model is as follows:

[0006] A proportional multi-way valve for use on dock gangways includes a hydraulic pump station motor installed on a fixed displacement pump. The hydraulic pump station motor provides the power source and is equipped with the proportional multi-way valve. The proportional multi-way valve acts as a control element to control the movement of a slewing motor, a telescopic cylinder, and a luffing cylinder. During loading, the hydraulic pump station motor starts the luffing cylinder, and a third directional valve controls the luffing cylinder to lift it to a set height; a first directional valve controls the slewing motor to rotate it back above the ship; a second directional valve controls the telescopic cylinder to extend it to a designated position; and a micro-motion luffing cylinder loads the gangway onto the deck. In compensation mode, the hydraulic pump station motor stops working and begins compensation work. The A and B chambers of the slewing motor are connected, and the telescopic cylinder and the luffing cylinder float freely.

[0007] As a preferred embodiment of this utility model: the proportional multi-way valve includes a connecting block and a tail connector. The connecting block integrates a damping element, a three-way pressure compensator, a safety valve, a filter, and a three-way pressure reducing valve. The connecting block provides stable pilot control oil to the three-way pressure reducing valve through the pilot pressure generated by the damping element.

[0008] In a preferred embodiment of this utility model, directional valve one, directional valve two, and directional valve three are each provided with a proportional directional valve block, a main directional valve, a secondary pressure reducing valve, a two-way pressure compensator, and a shuttle valve.

[0009] In a preferred embodiment of this utility model, the three-way pressure compensator works in conjunction with the shuttle valve network to make the outlet pressure of the metering pump 10-15 bar higher than the maximum load pressure of the reversing valve 1, reversing valve 2, and reversing valve 3.

[0010] In a preferred embodiment of this utility model: the rotary motor is connected to a two-position two-way solenoid valve 1, the telescopic cylinder includes a piston chamber 1 and a piston rod chamber 1, the telescopic cylinder is connected to a two-position two-way solenoid valve 2, the luffing cylinder includes a piston chamber 2 and a piston rod chamber 2, and the luffing cylinder is connected to a two-position two-way solenoid valve 3.

[0011] As a preferred embodiment of this utility model: the proportional multi-way valve is connected to T port one and T port two.

[0012] The beneficial effects of this utility model are:

[0013] This utility model discloses a proportional multi-way valve for use on dock gangways. The proportional multi-way valve enables precise control, adapts to complex working conditions, and ensures stable operation of the gangway under different loads and dynamic changes. In severe sea conditions, after the gangway is anchored on the ship's deck, the hydraulic station can be de-energized, and the gangway follows the ship with the current. Even if the ship is docked for a long time, it will not affect the following movement of the gangway. When applied to port dock gangways, it can ensure the compensation effect, is safe and reliable, realizes diversified operation, and has the advantages of compact structure, multi-functional valve, energy saving and environmental protection. It simplifies the system structure, saves installation space, and reduces maintenance costs. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the structure of a proportional multi-way valve applied to a dock gangway according to the present invention;

[0015] Figure 2 This is a schematic diagram of the assembly of a proportional multi-way valve.

[0016] In the diagram: 1-Hydraulic pump station motor, 2-Proportional multi-way valve, 3-Two-position two-way solenoid valve I, 4-Rotary motor, 5-Directional valve I, 6-Directional valve II, 7-Directional valve III, 8-Telescopic cylinder, 9-Piston chamber I, 10-Piston rod chamber I, 11-Two-position two-way solenoid valve II, 12-Amplitude cylinder, 13-Piston chamber II, 14-Piston rod chamber II, 15-Two-position two-way solenoid valve III, 16-T-port I, 17-T-port II, 201-Connecting block, 202-Damping element, 203-Three-way pressure compensator, 204-Safety valve, 205-Filter, 206-Three-way pressure reducing valve, 207-Proportional directional valve block, 208-Main directional valve, 209-Secondary pressure reducing valve, 210-Two-way pressure compensator, 211-Shuttle valve, 212-Tail coupling. Detailed Implementation

[0017] The present invention will now be described in detail with reference to the accompanying drawings and embodiments. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0018] like Figure 1-2 As shown, a proportional multi-way valve applied to a dock gangway includes a hydraulic pump station motor 1 installed on a fixed displacement pump. The hydraulic pump station motor 1 provides the power source and is equipped with a proportional multi-way valve 2. The proportional multi-way valve 2 acts as a control element to control the movement of a rotary motor 4, a telescopic cylinder 8, and a luffing cylinder 12. During loading, the hydraulic pump station motor 1 starts the luffing cylinder 12, and the reversing valve 3 7 controls the luffing cylinder 12 to lift it to a set height; the reversing valve 1 5 controls the rotary motor 4 to rotate it to the top of the ship; the reversing valve 2 6 controls the telescopic cylinder 8 to extend it to a designated position; the micro-motion luffing cylinder 12 loads the gangway onto the deck; under compensation conditions, the hydraulic pump station motor 1 stops working and begins compensation work, the A and B chambers of the rotary motor 4 are connected, and the telescopic cylinder 8 and the luffing cylinder 12 float freely.

[0019] The proportional multi-way valve 2 includes a connecting block 201 and a tail connector 212. The tail connector 212 is not only a sealing plate, but also has an oil inlet and outlet function, allowing the pilot control return oil to flow back to the oil tank from the T port. The connecting block 201 integrates a damping element 202, a three-way pressure compensator 203, a safety valve 204, a filter 205, and a three-way pressure reducing valve 206. The pilot pressure generated by the damping element 202 provides a stable pilot control oil to the three-way pressure reducing valve 206. The directional valves 1, 2, and 3 are all equipped with a proportional directional valve block 207, a main directional valve 208, a secondary pressure reducing valve 209, a two-way pressure compensator 210, and a shuttle valve 211. The three-way pressure compensator 203 and the shuttle valve 211 work together to make the outlet pressure of the fixed displacement pump 10-15 bar higher than the maximum load pressure of the directional valves 1, 2, and 3.

[0020] The rotary motor 4 is connected to a two-position two-way solenoid valve 3; the telescopic cylinder 8 includes a piston chamber 9 and a piston rod chamber 10; the telescopic cylinder 8 is connected to a two-position two-way solenoid valve 11; the luffing cylinder 12 includes a piston chamber 13 and a piston rod chamber 14; the luffing cylinder 12 is connected to a two-position two-way solenoid valve 15; the proportional multi-way valve 2 is connected to a T-port 16 and a T-port 17.

[0021] Excess flow from the fixed displacement pump overflows back to the oil tank at the current pressure via the three-way pressure compensator 203. When all directional valves 208 are in the neutral position, the three-way pressure compensator 203 unloads the pump at a pressure of 10-15 bar, putting the system in a low-pressure standby state and achieving energy saving. The two-way pressure compensator 210 inside the directional valve ensures that multiple actuators operate independently at different pressures and speeds, and that the control flow is unaffected by the load. The secondary pressure reducing valve 209 limits the maximum operating pressure of the directional valve load port A or B by limiting the pressure at the LS test port.

[0022] The connecting block 201 not only functions as an inlet and outlet oil valve, but also generates a stable pilot pressure through the damping element 202, providing stable pilot control oil for the three-way pressure reducing valve 206. The safety valve 204 is used to limit the maximum working pressure at the inlet of the multi-way valve. The excess clean oil from the fixed displacement pump, after overflowing through the filter 205 and filtering out impurities generated in the system, is unloaded into the oil tank at the pressure set by the three-way pressure compensator 203 and the safety valve 204.

[0023] The proportional directional valve block 207 is a functional block that enables the actuator to perform directional switching and proportional speed regulation. The main directional valve 208, via the shuttle valve 211, switches the direction of action of the actuator. The two-way pressure compensator 210 reduces the oil pressure in the oil inlet of the connecting block 201, maintaining a constant pressure difference between the inlet and outlet of the main valve core of the main directional valve 208. Together with the main valve core of the main directional valve 208, it forms a speed regulating valve. This ensures that the output flow rate at ports A and B of the main directional valve 208 is only proportional to the opening size of the main valve core, thus forming a proportional flow directional valve. The secondary pressure reducing valve 209 further limits the pressure at ports A and B of the main directional valve 208, making the system more energy-efficient.

[0024] The output pressure of the three-way pressure reducing valve 206 is approximately 40 bar. If the rotary reducer is selected for external brake release, port Z is connected to port C of the rotary reducer to provide an external control pressure of >30 bar for brake release. If the pressure of the three-way pressure reducing valve 206 is less than the brake pressure of the reducer, the brake valve of the rotary reducer cannot be opened. This pressure setting is crucial. If no external control oil connection is required, i.e., port Z is blocked, the output pressure of the three-way pressure reducing valve 206 can be adjusted to 20 bar.

[0025] After the gangway is attached to the ship's deck, the hydraulic pump station motor 1 can be stopped depending on the length of the working time. At this time, the two-position two-way solenoid valve 1, the two-position two-way solenoid valve 2 11, and the two-position two-way solenoid valve 3 15 are simultaneously de-energized, so that the A and B chambers of the rotary motor 4 are connected, the piston chamber 1 9 and the piston rod chamber 10 of the telescopic cylinder 8 are connected, and the piston chamber 2 13 and the piston rod chamber 2 14 of the luffing cylinder 12 are connected, generating a floating function. At this time, the rotary motor 4 swings left and right with the waves, and the telescopic cylinder 8 and the luffing cylinder 12 float freely.

[0026] T-port 2.17 is used for oil return from the proportional multi-way valve, while T-port 1.16 can be used for oil replenishment to the working device.

[0027] If the luffing cylinder 12 is in the extended state while floating, the oil in the piston rod chamber 14 of the luffing cylinder 12 is more than the oil in the piston chamber 13. At this time, oil needs to be replenished. One path of the oil in the piston rod chamber 14 is connected to the piston chamber through the two-position two-way solenoid valve 15, and the other path is returned to the T port 17 of the multi-way valve through the reversing valve 7 of the multi-way valve. A hose of the T port 16 is connected to the reversing valve 7 of the multi-way valve that controls the telescopic cylinder, forming a closed loop to replenish oil to the piston rod chamber 14 of the luffing cylinder 12.

[0028] If the luffing cylinder 12 is in a retracted state while floating, the oil in the piston rod chamber 14 of the luffing cylinder 12 is less than the oil in the piston chamber 13. At this time, unloading is required. The oil in the piston chamber is connected to the piston chamber 13 through the two-position two-way solenoid valve 15. The excess oil is returned to the T port 17 of the multi-way valve through the directional valve 7 of the multi-way valve in the middle position for unloading.

[0029] After the passengers have boarded, the ship needs to leave the dock. The hydraulic pump station motor 1 is restarted. The gangway can be operated by the control handle or remote control to place it on the open ground of the dock or suspend it in the air. After the operation is completed, the pump station is turned off.

[0030] In summary, during the loading operation, starting the hydraulic pump station motor 1 first activates the luffing cylinder 12, causing it to rise to a certain height. Then, the slewing motor 4 rotates 90 degrees to the top of the ship, extending the telescopic cylinder 8 to the designated position. Subsequently, the micro-motion luffing cylinder 12 loads the gangway onto the deck. In the compensation mode, the hydraulic pump station motor 1 stops working and begins compensation operations.

[0031] Although the embodiments of this utility model have been disclosed above, they are not limited to the applications listed in the specification and embodiments. They can be applied to various fields suitable for this utility model. For those skilled in the art, and for those of ordinary skill in the art, various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of this utility model. Therefore, without departing from the general concept defined by the claims and their equivalents, this utility model is not limited to the specific details.

Claims

1. A proportional multi-way valve for use on a dock gangway, characterized in that: The system includes a hydraulic pump station motor (1) installed on a fixed displacement pump. The hydraulic pump station motor (1) provides a power source and is equipped with a proportional multi-way valve (2). The proportional multi-way valve (2) acts as a control element to control the movement of the rotary motor (4), the telescopic cylinder (8), and the luffing cylinder (12). During the loading operation, the hydraulic pump station motor (1) starts the luffing cylinder (12), and the reversing valve three (7) controls the luffing cylinder (12) to lift it to a set height. The reversing valve one (5) controls the rotary motor (4) to rotate it to the top of the ship. The reversing valve two (6) controls the telescopic cylinder (8) to extend it to a designated position. The luffing cylinder (12) is slightly moved to load the gangway onto the deck. In the compensation condition, the hydraulic pump station motor (1) stops working and begins compensation work. The A and B chambers of the rotary motor (4) are connected, and the telescopic cylinder (8) and the luffing cylinder (12) float freely.

2. The proportional multi-way valve for use on a quay side ramp according to claim 1, characterized in that: The proportional multi-way valve (2) includes a connecting block (201) and a tail connector (212). The connecting block (201) integrates a damping element (202), a three-way pressure compensator (203), a safety valve (204), a filter (205), and a three-way pressure reducing valve (206). The connecting block (201) provides stable pilot control oil to the three-way pressure reducing valve (206) through the pilot pressure generated by the damping element (202).

3. The proportional multi-way valve for use on a dock gangway according to claim 2, characterized in that: The first reversing valve (5), the second reversing valve (6), and the third reversing valve (7) are all equipped with a proportional reversing valve block (207), a main reversing valve (208), a secondary pressure reducing valve (209), a two-way pressure compensator (210), and a shuttle valve (211).

4. The proportional multi-way valve for use on a dock gangway according to claim 3, characterized in that: The three-way pressure compensator (203) works in conjunction with the shuttle valve (211) network to make the outlet pressure of the metering pump 10-15 bar higher than the maximum load pressure of the reversing valve 1 (5), reversing valve 2 (6), and reversing valve 3 (7).

5. The proportional multi-way valve applied to a dock gangway according to claim 1, characterized in that: The rotary motor (4) is connected to a two-position two-way solenoid valve (3), the telescopic cylinder (8) includes a piston chamber (9) and a piston rod chamber (10), the telescopic cylinder (8) is connected to a two-position two-way solenoid valve (11), the luffing cylinder (12) includes a piston chamber (13) and a piston rod chamber (14), and the luffing cylinder (12) is connected to a two-position two-way solenoid valve (15).

6. The proportional multi-way valve applied to a dock gangway according to any one of claims 1-5, characterized in that: The proportional multi-way valve (2) is connected to T port one (16) and T port two (17).

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