Integrated large non-retractable fin stabilizer hydraulic system and control method thereof

Abstract

The application belongs to the field of ship stabilizer fins and hydraulic technology, and particularly relates to an integrated large non-retractable stabilizer fin hydraulic system and a control method thereof. The hydraulic system comprises a main pump, a motor, an auxiliary pump, a reset unlocking and servo valve group and an oil tank. A first shaft end of the motor drives a turning fin pump in the main pump to provide energy for a main circuit, and a second shaft end of the motor drives the auxiliary pump to provide energy for a servo, reset and unlocking circuit. The main pump integrates the turning fin pump, an oil supplement pump, a filter module, an oil supplement module, an overflow flushing module and a short circuit valve group. An output end of the turning fin pump and a turning fin oil cylinder of an actuator constitute a closed hydraulic circuit to realize forward and reverse turning fins. The oil supplement pump is driven by the motor, connected to the main circuit through the filter and the oil supplement module, and connected to a reset oil cylinder through a reset electromagnetic valve. The application realizes integrated lightweight design by integration and optimization, reduces hydraulic components and pipelines, controls oil temperature, improves system stability and reliability, and is suitable for the demand of large ships for high-performance stabilizer fin devices.

Description

Technical Field

[0001] This application belongs to the field of ship anti-roll fin and hydraulic technology, specifically, it relates to an integrated large-scale non-retractable anti-roll fin hydraulic system and its control method. Background Technology

[0002] During navigation or anchoring, sea waves can cause rolling motion, severely affecting the stability and comfort of the vessel. To reduce rolling, anti-roll fin systems, as widely used active anti-roll devices, have been extensively validated and applied in various ship types. Especially when encountering strong winds and waves during navigation, anti-roll fins can significantly reduce the hull's rolling angle, thereby improving navigational safety and crew comfort.

[0003] Anti-roll fins are mainly classified into retractable and non-retractable anti-roll fins based on whether their structure is retractable or not. Both types of anti-roll fin devices typically consist of components such as fins, actuators, hydraulic units, electrical control equipment, and fin seats (for non-retractable types) or fin boxes (for retractable types). Among these, the hydraulic unit, as the power and control core, plays a crucial role in the entire system; its technical performance, reliability, and ease of maintenance directly determine the engineering practicality and economy of the entire anti-roll device.

[0004] However, existing hydraulic systems for anti-roll fins still have many problems that urgently need improvement. First, the system structure is relatively complex, employing numerous discrete hydraulic components, resulting in a large number of connecting pipelines, cumbersome layout, high installation difficulty, and multiple potential leakage risks. Second, some hydraulic systems use closed-loop fin circuits but lack effective oil flushing mechanisms, which can easily cause oil temperature to rise, thereby affecting system stability and component lifespan. This leads to insufficient system reliability, high maintenance difficulty, and difficulty in meeting the long-term operational requirements of modern high-performance ships.

[0005] Furthermore, with the trend towards larger ships, higher requirements are placed on the structural strength and performance stability of roll damping devices. Simply scaling up existing small and medium-sized devices often results in excessively large and heavy units, compromised system performance, and significantly increased manufacturing and installation difficulties. Therefore, current technical architectures and solutions are no longer adequate for the high-efficiency, compact, and easily maintainable roll damping systems required by large ships, necessitating comprehensive technological innovation in system integration, structural optimization, and functional reliability. Summary of the Invention

[0006] To address the technical challenges of existing anti-roll fin hydraulic systems, such as the large number of hydraulic components, complex piping connections, and high oil temperature in closed-loop fin control circuits, this application provides an integrated large-scale non-retractable anti-roll fin hydraulic system and its control method. This system, through integrated and optimized design, reduces the number of hydraulic components and piping complexity, effectively controls system oil temperature, and improves operational stability. Furthermore, considering the trend towards larger equipment, the system fully addresses the coordination and matching between the hydraulic system's technical performance, structural dimensions, and weight with ship installation requirements, proposing an integrated and modular system configuration. This invention not only achieves integrated and lightweight design of the large anti-roll fin hydraulic system, reducing its footprint in the cabin, but also improves equipment reliability and ease of maintenance, making it suitable for the technical requirements of modern large ships for high-performance anti-roll devices.

[0007] On the one hand, this application provides an integrated large-scale non-retractable anti-roll fin hydraulic system, including a main pump, an electric motor, an auxiliary pump, a zero-reset unlocking and servo valve group, and an oil tank;

[0008] The motor is a dual-output shaft three-phase asynchronous motor with a first output shaft end and a second output shaft end. The first output shaft end is connected to the fin pump in the main pump and is used to provide power to the main circuit of the hydraulic system. The second output shaft end is connected to the auxiliary pump and is used to provide power to the servo, zeroing and unlocking circuits.

[0009] The main pump integrates a finned pump, a replenishing pump, a filter module, a replenishing oil module, an overflow flushing module, and a short-circuit valve group. The finned pump has two main oil circuits and has an output port A, an output port B, and a return port. Output ports A and B are respectively connected to one of the corresponding main oil circuits. The finned pump has a bidirectional pressure supply function, used to dynamically switch between the high-pressure side and the low-pressure side to achieve forward or reverse oil supply control of the anti-roll fins. The return port is connected to the oil tank, and output ports A and B are respectively connected to both ends of the finned hydraulic cylinder, forming a closed hydraulic circuit. The replenishing pump is arranged in series at the rear of the finned pump and is driven by an electric motor. The replenishing pump has an inlet and an outlet. The inlet is connected to the oil tank, and the outlet is connected to the closed hydraulic circuit via the filter module and the replenishing oil module.

[0010] The oil replenishment module includes a first check valve, a second check valve, a third check valve, an oil replenishment overflow valve, a first oil replenishment pipeline, and a second oil replenishment pipeline. The two ends of the first oil replenishment pipeline are connected to the two main oil circuits of the rotary fin pump, respectively. The first and second check valves are arranged on the first oil replenishment pipeline with their inlets facing each other and connected in series between the two main oil circuits, used to dynamically identify and connect the low-pressure side main oil circuit. The outlet end of the oil replenishment pump is fluidly connected to the connecting pipeline between the first and second check valves through the second oil replenishment pipeline. A return oil branch connected to the oil tank is provided in the first oil replenishment pipeline, located between the first and second check valves. A third check valve and an oil replenishment overflow valve are connected in series on the return oil branch. The third check valve controls the unidirectional flow of oil to the oil tank, and the oil replenishment overflow valve limits the oil replenishment pressure within a set pressure range.

[0011] The overflow flushing module includes a first finned overflow valve, a second finned overflow valve, and a shuttle valve. The first and second finned overflow valves are connected in parallel to control the maximum pressure of the main oil circuits on the output port A and output port B sides, respectively, and their outlets are connected to the other side of the main oil circuit. The shuttle valve has two inlets and one outlet. Its inlets are connected to the main oil circuits on the output port A side and the output port B side, respectively, and its outlet is connected to the oil tank via a replenishing overflow valve and a cooler, forming a cooling and return path for the flushing oil. The shuttle valve has a valve core structure that can be driven by the oil to automatically identify the side of the two main oil circuits that is in a low-pressure state when high-pressure oil is received and connect it to the low-pressure side, guiding the corresponding high-temperature, low-pressure oil to the replenishing overflow valve and then cooling it back to the oil tank.

[0012] The zero-reset unlocking and servo valve group includes a zero-reset solenoid valve, which is connected to the zero-reset cylinder and is used to control the reset action of the anti-roll fin.

[0013] In a preferred embodiment, a hand-cranked pump is further included. The hand-cranked pump has an oil inlet and an oil outlet. The oil inlet is connected to the oil tank, and the oil outlet is connected to the downstream of the reset solenoid valve. This is used to provide emergency oil supply to the reset circuit in the event of a power failure or malfunction of the hydraulic system.

[0014] In a preferred embodiment, the inlet of the first finned relief valve is connected to the oil circuit on the output port A side to control the maximum pressure of the main oil circuit on the output port A side, and its outlet is connected to the oil circuit on the output port B side; the inlet of the second finned relief valve is connected to the oil circuit on the output port B side to control the maximum pressure of the main oil circuit on the output port B side, and its outlet is connected to the oil circuit on the output port A side.

[0015] In a preferred implementation, the oil replenishment module further includes a fourth pressure testing connector, a fifth pressure testing connector, a fourth pressure gauge, a sixth pressure testing connector, and a pressure controller; the fourth and fifth pressure testing connectors are arranged in parallel and installed on the branch from the third check valve to the first and second check valves; the fourth pressure testing connector is connected to the fourth pressure gauge; and the fifth pressure testing connector is connected to the pressure controller through the sixth pressure testing connector.

[0016] In a preferred embodiment, the system further includes a second pressure testing connector, a third pressure testing connector, a second pressure gauge, and a third pressure gauge. The second and third pressure testing connectors are respectively connected to the main oil circuit on one side of the finned pump. The second pressure gauge is connected to the second pressure testing connector, and the third pressure gauge is connected to the third pressure testing connector. These components are used to monitor and display the pressure of the main oil circuits on both sides of the finned pump.

[0017] In a preferred implementation, the zero-reset unlocking mechanism further integrates a servo circuit, a zero-reset circuit, and an unlocking circuit with the servo valve group.

[0018] In a preferred implementation, the zero-locking and servo valve group further includes a sixth check valve, a servo loop filter, an overflow valve, and an unlocking solenoid valve. One side of the sixth check valve is connected to the output port of the auxiliary pump via a pipeline, and the downstream side is connected in series with the servo loop filter, the overflow valve, and the unlocking solenoid valve, ultimately forming multiple branch control loops in parallel with the zero-locking solenoid valve. The servo loop filter is connected to the servo valve, the unlocking solenoid valve is connected to the zero-locking cylinder, and the overflow valve is located in the servo control loop.

[0019] In a preferred implementation, the main pump further includes a displacement sensor and a servo valve. The servo valve is used to control the output flow rate according to the fin rotation command amplified by the servo amplifier from the electronic control system after the anti-roll fin device enters the fin rotation state. The displacement sensor is used to detect the position of the variable mechanism and feed it back to the servo amplifier.

[0020] In a preferred embodiment, the oil tank further integrates a first ball valve, a second ball valve, a level gauge, a thermometer, an air filter, a return oil filter, and a level control relay.

[0021] On the other hand, this application also provides a control method for an integrated large-scale non-retractable anti-roll fin hydraulic system as described in any one of the above claims, the control method comprising:

[0022] Step 1: When the main motor of the hydraulic system starts, the auxiliary pump, fin pump and oil replenishment pump work synchronously. At this time, the zero-reset solenoid valve is in the default de-energized state. The auxiliary pump provides hydraulic power for the zero-reset circuit. The oil flows into the zero-reset solenoid valve after passing through the sixth check valve and the servo circuit filter in sequence, and enters the zero-reset chamber of the first fin cylinder and the second fin cylinder, pushing the zero-reset piston to move and reset the anti-roll fin to the zero position. At the same time, the short-circuit solenoid valve is in the default de-energized state, controlling the two-way cartridge valve to be in the open state, connecting the two ends of the main oil circuit to achieve short-circuit unloading.

[0023] Step 2: After the zeroing action is completed, the control system switches the unlocking solenoid valve to the energized state. The hydraulic oil supplied by the auxiliary pump enters the zeroing cylinder, pushing the internal piston to overcome the force of the reset spring, causing the telescopic pin to retract and unlocking the locking mechanism. Subsequently, the zeroing solenoid valve is also switched to the energized state, the valve port of the short-circuit valve group is in the closed state, and the zeroing process ends.

[0024] Step 3: The hydraulic system enters the fin-rotating condition preparation state. The fin-rotating pump continues to run, keeping in sync with the auxiliary pump and the replenishing pump. The replenishing pump delivers oil to the low-pressure side of the main oil circuit through the second replenishing pipeline. During the replenishing process, the oil is first cleaned by the filter module, and then the low-pressure side of the main oil circuit is identified by the first check valve or the second check valve and the oil is introduced through the first replenishing pipeline.

[0025] Step 4: In the fin-rotating state, the anti-roll fin system monitors the hull roll rate signal in real time through a gyroscope and transmits the detection signal to the central processing unit. After analyzing the signal, the processor outputs control commands. The servo amplifier amplifies the commands and drives the servo valve to move, controlling the variable cylinder to adjust the tilt angle and direction of the swashplate inside the fin pump, changing the direction and magnitude of the flow rate output by the main pump, thereby driving the forward and reverse movements of the fin cylinder, driving the anti-roll fin to perform active oscillation, and realizing dynamic anti-roll control. During system operation, the overflow flushing module dynamically identifies the low-pressure side of the main oil circuit. When the pressure of the main oil circuit reaches the overflow valve threshold, some high-temperature hydraulic oil is guided through the corresponding fin overflow valve and shuttle valve to the replenishment overflow valve and then enters the cooler for cooling and returns to the oil.

[0026] Step 5: When the hydraulic system is de-energized, hydraulic power is provided by cranking the hand pump. The hand pump draws oil from the oil tank and outputs it under pressure. The zero-reset solenoid valve is still in the default de-energized state. The oil is introduced into the zero-reset chamber of the rotating fin cylinder through the zero-reset solenoid valve, pushing the zero-reset piston to the lowest position. During the reset process, the rotating fin piston is pushed at the same time to return the fin to the zero position. When the reset is completed, the telescopic pin in the zero-locking cylinder automatically springs into the fin shank pin hole under the action of the spring force to achieve mechanical locking, thus completing the reset and locking process.

[0027] The beneficial effects of this application are:

[0028] First, the integrated large-scale non-retractable anti-roll fin hydraulic system of this application highly integrates the main pump (including the fin pump and the replenishing pump), filter module, replenishing module, overflow flushing module, and short-circuit valve group into one unit, significantly reducing the number of discrete components and external pipeline connections, simplifying the system layout, reducing installation difficulty and leakage risk, and is particularly suitable for deployment in the engine room of large ships with limited space; it adopts dual-output shaft motors to drive the main pump and auxiliary pump respectively, realizing the physical separation of the power source of the main circuit (fin drive) and the control circuit (servo, zeroing, unlocking), improving the system response speed and action stability, and ensuring good control accuracy and anti-interference capability under various working conditions; the main circuit adopts a closed hydraulic system, and a dynamic flushing channel is constructed through the replenishing pump and a dedicated overflow flushing module to guide the high-temperature oil out of the system in a timely manner. The system provides and replenishes low-temperature new oil, solving the technical bottleneck of excessively high oil temperature affecting system stability and service life in traditional closed-loop systems. The three control functions—reset, unlock, and servo—are integrated into a unified valve module, with independent oil supply and pressure limiting protection from the auxiliary pump. This not only meets the needs of multi-mode fin rotation operation but also improves the overall consistency, modularity, and maintainability of the system. A hand-cranked pump is located in the reset circuit, allowing manual oil supply to the reset solenoid valve in case of power failure or system malfunction, ensuring that fin reset can be completed even under extreme conditions and enhancing the system's emergency response capabilities. This system is specifically designed for large, non-retractable anti-roll fins, solving the problems of bulky size and performance degradation that arise from scaling up traditional systems. While ensuring structural strength, it achieves a highly integrated, high-performance, and highly reliable marine anti-roll hydraulic control solution.

[0029] Secondly, in the preferred implementation, the oil replenishment module of this application automatically identifies and connects to the low-pressure side of the current circuit by setting a first check valve and a second check valve arranged in opposite directions between the main oil circuits of the rotary fin pump, thereby achieving dynamic and intelligent low-pressure oil replenishment. This structure enables the system to judge the pressure status of the main oil circuit in real time under different rotary fin working directions, ensuring that the oil replenishment channel is always connected to the low-pressure side, preventing high-pressure backflow, and improving energy utilization. The third check valve and the oil replenishment overflow valve set between the low-pressure side and the oil tank ensure that excess oil is controllably discharged and provide pressure limiting protection for the oil replenishment pressure, effectively preventing system overpressure or oil shock problems; the oil replenishment module is further equipped with a multi-point pressure measurement and control structure, by setting a fourth pressure measuring connector and a fifth pressure measuring connector in parallel on the return oil branch, which are respectively connected to a fourth pressure gauge and a pressure controller, realizing real-time monitoring and automatic control of the pressure of key nodes in the closed-loop oil replenishment path.

[0030] Third, in the preferred implementation, this application respectively installs a first finned overflow valve and a second finned overflow valve on both sides of the main oil circuit of the finned pump. This effectively limits the maximum pressure of the system in the return oil state, preventing oil temperature rise or actuator jamming due to excessive back pressure in the circuit, thereby improving the stability and safety of system operation. Simultaneously, the shuttle valve structure enables automatic identification and flushing switching between high and low pressure sides, ensuring continuous flushing of the low-pressure circuit, improving oil heat accumulation and contamination issues, and extending the service life of the oil and components. Furthermore, by integrating the second and third pressure measuring connectors and pressure gauges, real-time monitoring and visual display of the pressure in both main oil circuits are achieved, providing reliable data support for commissioning, maintenance, and troubleshooting.

[0031] Fourth, in the preferred implementation, this application integrates the sixth check valve, servo circuit filter, relief valve, reset solenoid valve, and unlocking solenoid valve into an integrated reset / unlocking and servo valve group. This not only achieves modular combination of multi-functional circuits, but also realizes orderly diversion and shared oil supply between different control functions through series-parallel oil circuit arrangement, effectively improving the logical clarity and control coordination of the hydraulic system. In addition, this structure allows the servo control oil to be purified by the filter before entering the servo valve and pressure limited by the relief valve, ensuring the cleanliness and pressure stability of the control oil.

[0032] Fifth, in the preferred implementation, the main pump of this application integrates a displacement sensor and a servo valve to construct a closed-loop control structure. After the anti-roll fin device enters the fin-rotating working state, the output flow of the main pump can be adjusted and precisely controlled in real time according to the fin-rotating command input by the electronic control system. The servo valve dynamically adjusts the pump's flow output based on the signal processed by the servo amplifier, and the displacement sensor detects the displacement of the variable mechanism in real time and forms position feedback, achieving high-precision fin-rotating control.

[0033] Sixth, in the preferred implementation, this application establishes fluid communication between the oil outlet of the replenishing pump and the connecting pipeline between the first check valve and the second check valve in the closed hydraulic circuit through the second replenishing pipeline, which can realize dynamic replenishing balance of the low-pressure chambers on both sides of the closed circuit.

[0034] Seventh, in the preferred implementation, the oil tank of this application adopts an integrated functional design, which integrates the first ball valve, the second ball valve, the level gauge, the thermometer, the air filter, the return oil filter, and the level control relay on the oil tank body. This not only simplifies the installation and piping structure of the oil tank accessories and improves the overall compactness and aesthetics of the system, but also realizes localized integrated management of multiple functions such as hydraulic oil suction, return, filtration, temperature and level monitoring, and air dust isolation.

[0035] Eighth, the control method of the integrated large non-retractable anti-roll fin hydraulic system of the present invention achieves precise zeroing of the fin cylinder through zeroing solenoid valve control, ensuring accurate system initialization. The unlocking mechanism driven by electro-hydraulic control ensures controllable release of the fin handle, improving system safety. Combined with gyroscope detection and servo adjustment, it achieves dynamic response and active roll reduction to the hull roll. In case of system abnormality or power failure, it has an automatic pressure relief and manual reset mechanism to ensure the system safely returns to zero position in emergency situations. Attached Figure Description

[0036] Figure 1 This is a schematic diagram of an integrated large-scale non-retractable anti-roll fin hydraulic system according to an embodiment of the present invention;

[0037] Figure 2 This is a schematic diagram of the overflow flushing module according to an embodiment of the present invention.

[0038] Among them, 1.1-First ball valve; 1.2-Second ball valve; 2-Level gauge; 3-Thermometer; 4-Air filter; 5-Return oil filter; 6-Cooler; 7-Level relay; 8-Main pump; 8.1-Finless fin pump; 8.2-Main oil pump; 9-Main oil filter; 10.1-First check valve; 10.2-Second check valve; 11-Third check valve; 12.1-First finless fin overflow valve; 12.2-Second finless fin overflow valve; 13-Shuttle valve; 14-Main oil overflow valve; 15-Displacement sensor; 16-Servo valve; 17.1-Fourth check valve; 17.2-Fifth check valve; 18-Two-way cartridge valve core; 19-Two-way cartridge valve cover; 20-Short 21-Solenoid valve; 22-Motor; 23-Auxiliary pump; 24-Hand-crank pump; 25-Sixth check valve; 26-Servo circuit filter; 27-Reset solenoid valve; 28-Unlock solenoid valve; 29.1-First pressure test connector; 29.2-Second pressure test connector; 29.3-Third pressure test connector; 29.4-Fourth pressure test connector; 29.5-Fifth pressure test connector; 30.1-First pressure gauge; 30.2-Second pressure gauge; 30.3-Third pressure gauge; 31-Fourth pressure gauge; 32-Sixth pressure test connector; 33-Pressure controller; 34-Oil tank; 35.1-First rotary fin cylinder; 35.2-Second rotary fin cylinder; 36-Zero-lock cylinder. Detailed Implementation

[0039] To enable those skilled in the art to better understand the technical solutions of this application, the following will provide a more detailed description of this application in conjunction with the accompanying drawings and embodiments.

[0040] The directional terms such as above, below, left, right, front, and back used in this application are based on the positional relationships shown in the attached drawings. Different attached drawings may result in different positional relationships, therefore they should not be interpreted as limitations on the scope of protection.

[0041] In this application, the terms "installation," "connection," "interlocking," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, an integral connection, a mechanical connection, an electrical connection, or a connection that allows communication between components. They can also refer to a direct connection or an indirect connection through an intermediate medium. They can refer to the internal connection of two components or the interaction between two components. For those skilled in the art, the specific meaning of the above terms in this application can be understood according to the specific circumstances.

[0042] Example

[0043] Refer to the instruction manual appendix Figure 1 This embodiment describes an integrated large-scale non-retractable anti-roll fin hydraulic system, which not only possesses the advantages of system-level integrated optimization and temperature control management, but also provides a stable and controllable driving force for the anti-roll fin actuator, thereby achieving active oscillation control of the anti-roll fin in strong wind and wave environments and effectively suppressing the ship's roll. The actuator is used to drive the oscillation motion of the anti-roll fin, and its structure includes a high-pressure circuit and a low-pressure circuit arranged between the output end of the main pump of the hydraulic system and the fin-rotating cylinder. The high-pressure circuit is responsible for delivering the high-pressure oil output from the main pump to the push chamber of the fin-rotating cylinder to generate driving force to drive the fin blades to deflect; the low-pressure circuit is responsible for receiving the return oil from the back pressure side of the fin-rotating cylinder and, in conjunction with the oil replenishment module, maintaining the system's oil balance and pressure stability.

[0044] by Figure 1 Taking the actuator shown as an example, the existing actuator includes a symmetrically arranged first fin cylinder 35.1 and second fin cylinder 35.2, a fin shaft, a fin handle, and a locking mechanism. Both the first fin cylinder 35.1 and the second fin cylinder 35.2 are linear reciprocating actuators, with their piston rods rigidly connected to both ends of the fin handle. The fin shaft passes through the central through-hole of the fin handle and is fixedly connected to the fin handle to realize the rotational movement of the fin blades along the fin shaft axis. The first fin cylinder 35.1 and the second fin cylinder 35.2 are respectively provided with hydraulic input interfaces and are connected to the integrated large-scale non-retractable anti-roll fin hydraulic system provided in this application to realize forward and reverse control of the anti-roll fin and zeroing operation. The locking mechanism includes a telescopic pin and a zeroing cylinder 36 that controls its telescopic movement. The zeroing cylinder 36 is a hydraulically driven component, and its inlet and outlet ports are connected to the hydraulic system of this application. The fin has a pin hole corresponding to the position of the telescopic pin. When the hydraulic system performs the zeroing operation, the zeroing cylinder drives the telescopic pin to extend and insert into the pin hole to form mechanical positioning and locking, so as to ensure that the anti-roll fin remains fixed in the zeroing state and prevents malfunction.

[0045] Specifically, the integrated large-scale non-retractable anti-roll fin hydraulic system of this application includes a main pump 8, an electric motor 21, an auxiliary pump 22, a zero-reset unlocking and servo valve group, a hand-cranked pump 23, and an oil tank 34. The electric motor 21 is a dual-shaft three-phase asynchronous motor with a first output shaft end and a second output shaft end. The main pump 8 is the core component of the entire hydraulic system, integrating multiple functional modules, namely a fin pump 8.1, a replenishing pump 8.2, a filter module, a replenishing oil module, an overflow flushing module, and a short-circuit valve group. The drive shaft of the fin pump 8.1 is connected to the first output shaft end of the electric motor 21 via a coupling, providing power to the main circuit of the hydraulic system, thereby driving the fin hydraulic cylinder. The replenishing pump 8.2 is integrated into the structure of the main pump 8, obtaining driving power through a coaxial transmission mechanism with the fin pump 8.1, and is driven by the electric motor 21, achieving synchronous driving of the fin pump 8.1 and the replenishing pump 8.2. The drive shaft of the auxiliary pump 22 is connected to the second output shaft of the motor 21 via a coupling, and is used to provide power for auxiliary circuits such as servo, zeroing, and unlocking.

[0046] Furthermore, the finned motor 8.1 has an output port A, an output port B, and an oil return port. The oil return port of the finned motor 8.1 is connected to the oil tank 34, and the finned motor 8.1 has two main oil circuits.

[0047] Output ports A and B serve as bidirectional output ports of the main pump 8, respectively, and are connected via pipelines to become ports A3 and A4 of the hydraulic unit. Ports A3 and A4 are connected to ports B3 and B4 of the actuator, respectively, forming a closed hydraulic circuit. Port B4 corresponds to the top cavity of the finned piston of the first finned cylinder 35.1 and the bottom cavity of the finned piston of the second finned cylinder 35.2. The high-pressure hydraulic oil input compresses the top of the piston of the first finned cylinder 35.1, causing the piston rod to extend, and simultaneously pushes the bottom of the piston of the second finned cylinder 35.2, causing its piston rod to retract. Port B3 corresponds to the bottom cavity of the finned piston of the first finned cylinder 35.1 and the top cavity of the finned piston of the second finned cylinder 35.2. The high-pressure hydraulic oil input pushes the bottom of the piston of the first finned cylinder 35.1, causing the piston rod to retract, and simultaneously compresses the top of the piston of the second finned cylinder 35.2, causing its piston rod to extend.

[0048] The rotary fin pump 8.1 employs a bidirectional variable displacement hydraulic pump, enabling forward / reverse oil supply switching. When the variable displacement mechanism inside the rotary fin pump 8.1 controls the forward movement of the swashplate inside the main pump 8, output port A is a high-pressure output. The oil circuit on the side of this port, located on the rotary fin pump 8.1, is the high-pressure side. The high-pressure side oil circuit enters port B3 of the actuator through port A3, then enters the piston bottom cavity of the first rotary fin cylinder 35.1 and the piston top cavity of the second rotary fin cylinder 35.2, pushing the rotary fin piston to move. The hydraulic oil in the piston top cavity of the first rotary fin cylinder 35.1 and the piston bottom cavity of the second rotary fin cylinder 35.2 flows through port B4 of the actuator, through port A4, and into output port B. At this time, the oil circuit on the side of output port B, located on the rotary fin pump 8.1, is the low-pressure side, and output port B is the return oil.

[0049] When the swashplate inside the main pump 8 moves in the reverse direction, and output port B is at high pressure, the oil circuit on the side of the fin pump 8.1 at this port is the high-pressure side, while the oil circuit on the opposite side of the fin pump 8.1 at output port A is the low-pressure side, and output port A is the return oil. This structure supports bidirectional extension and retraction of the fin hydraulic cylinder. The two main oil circuits of the fin pump 8.1 alternately undertake the oil inlet and return functions under different operating conditions of the system to realize the forward and reverse rotation control of the anti-rolling fin. The high-pressure side and low-pressure side of the fin pump 8.1 change dynamically with the direction of the fin.

[0050] To achieve dynamic pressure identification and function allocation in the closed-loop hydraulic system, the replenishing oil module, overflow flushing module, and short-circuit valve assembly are all arranged in parallel between the two main oil circuits to automatically identify and respond to the current high and low pressure status of the oil circuit. The replenishing oil module is located at the front end of the main oil circuit. The replenishing oil pump 8.2 has an inlet and an outlet. The inlet is connected to the oil tank 34, and the outlet is connected to the replenishing oil module via a filter module, so that the replenishing oil is cleaned and filtered by the filter module before entering the fin circuit, ensuring the cleanliness of the replenishing medium. The overflow flushing module is located in the middle and slightly rear of the main oil circuit to discharge the high-temperature oil on the low-pressure side of the fin circuit through overflow, achieving system cooling and oil renewal. The short-circuit valve assembly is configured between the replenishing oil module and the overflow flushing module to connect the two ends of the oil circuit in the event of a power outage or fault, completing emergency unloading and automatic fin reset.

[0051] The reset unlocking and servo valve assembly includes a reset solenoid valve 27 connected to the reset cylinder 36 in the actuator. This reset solenoid valve 27 controls the reset action during system reset. The hand-operated pump 23 has an inlet and an outlet. Its inlet is connected to the oil tank 34, and its outlet is connected downstream of the reset solenoid valve 27 via a pipeline. The hand-operated pump 23 serves as a backup hydraulic power unit in case of system power failure. It can be manually operated to draw oil from the oil tank 34 and output pressurized oil to supply the reset oil circuit, driving the finned actuator to complete the reset operation.

[0052] Through the aforementioned structure, the main pump drives a bidirectional hydraulic circuit, providing stable driving force for the anti-roll fins and supporting forward and reverse rotation control to actively oscillate and suppress hull roll under strong winds and waves. The system integrates modules for oil replenishment, filtration, flushing and cooling, and short-circuit unloading, simplifying the system structure, reducing the number of discrete components and pipelines, and lowering the difficulty of layout and installation. It possesses the ability to dynamically identify and allocate oil pressure. It adopts a closed-loop circuit and introduces an overflow flushing mechanism to improve oil temperature management capabilities, ensuring system stability and component lifespan. The dual-output shaft motor drives the main and auxiliary pumps, and is equipped with a hand-cranked pump and a zero-reset solenoid valve to support power failure reset and emergency operation, ensuring efficient, stable, and reliable system operation.

[0053] In the preferred embodiment of this application, the finned motor pump 8.1 is a swashplate piston pump with variable displacement and reversible flow capability. The displacement and direction are controlled by the swashplate tilt angle; changing the swashplate tilt angle changes the pump's displacement. The variable displacement of the finned motor pump 8.1 is controlled by a closed-loop control system consisting of a servo valve 16, a displacement sensor 15, and the variable displacement mechanism inside the swashplate piston pump. This control enables the swashplate control of the finned motor pump 8.1, thereby controlling the output flow rate and oil direction of the finned motor pump 8.1.

[0054] It should be noted that the variable displacement mechanism inside the rotary fin pump 8.1 includes a swashplate, plungers, a variable displacement piston, a variable displacement control valve, a return spring, and a pump housing. The swashplate is connected to and hinged to the housing. One end of the plunger is installed in the cylinder bore, and the other end contacts the swashplate, with the inclined surface of the swashplate sliding in contact with the plunger. The variable displacement piston is installed in the housing and pushes the swashplate to adjust its angle. The variable displacement control valve is connected to the variable displacement piston and adjusts the oil pressure in its two chambers. The return spring is located on the back of the variable displacement piston, allowing the swashplate to return to its initial angle. The drive shaft of the rotary fin pump 8.1 rotates at high speed under the action of the electric motor 21, and the cylinder, which is rigidly connected to it, rotates simultaneously. Multiple plungers are embedded in the annularly distributed plunger bores in the cylinder, with the tail end of the plunger sliding in contact with the inclined surface of the swashplate. Because the swashplate is inclined, the plungers continuously push away from or press back into the cylinder as they rotate, achieving reciprocating motion. The plunger stroke is proportional to the swashplate angle; the larger the angle, the longer the stroke and the greater the displacement per unit time. If the angle is zero (the swashplate is vertical), there is no plunger movement, and the displacement is zero. The two oil circuits of the rotary fin pump 8.1 have corresponding plunger chambers and cylinder passages. Under different swashplate tilt angles, one side forms a high-pressure oil supply, and the other side forms a low-pressure oil return.

[0055] In the implementation of this application, the oil replenishment module includes a first check valve 10.1, a second check valve 10.2, a third check valve 11, an oil replenishment relief valve 14, a first oil replenishment pipeline, and a second oil replenishment pipeline, forming a compact and functionally coordinated closed-loop hydraulic system oil replenishment pathway. The first oil replenishment pipeline is attached to the specification. Figure 1Points b1 to b2 are used to identify and directionally replenish oil on the low-pressure side of the system and to drain excess oil into the oil tank. The two ends of the first replenishment pipeline are connected to the two main oil circuits of the fin pump 8.1, respectively. The first check valve 10.1 and the second check valve 10.2 are arranged on the first replenishment pipeline with their inlets facing each other and connected in series between the two main oil circuits. They are used to dynamically identify the main oil circuit on the low-pressure side of the system and only conduct to the low-pressure side to achieve directional replenishment of oil on the low-pressure side.

[0056] A return oil branch is provided in the first replenishment oil line, located between the first check valve 10.1 and the second check valve 10.2. This return oil branch connects to the oil tank 34 and is used to drain excess oil during the replenishment process, ensuring system oil balance. A third check valve 11 and a replenishment overflow valve 14 are connected in series in this return oil branch to form a constant pressure return oil circuit. The third check valve 11 controls the unidirectional flow of oil to the oil tank 34, preventing backflow. The replenishment overflow valve 14 sets the overflow pressure of the replenishment channel to ensure the system pressure remains within the range of 1.6-2.5 MPa. The replenishment pump 8.2 is a gear pump or vane pump, configured in the closed circuit of the hydraulic system. The second replenishment oil line is attached to the instruction manual. Figure 1 Points b3 to b4 in the diagram form a fluid connection between the outlet of the replenishing pump 8.2 and the first replenishing pipeline, ensuring that the oil delivered by the replenishing pump enters the main system. The outlet of the replenishing pump 8.2 is connected via a second replenishing pipeline to the connecting pipeline between the first check valve 10.1 and the second check valve 10.2 in the first replenishing pipeline, completing the directional replenishment of oil to the low-pressure side of the closed circuit. The second replenishing pipeline is further connected to the return branch of this replenishing module. During system operation, this module automatically guides the oil delivered by the replenishing pump 8.2 to one of the two main oil circuits, the low-pressure side circuit, while simultaneously overflowing back to the oil tank 34 through the return branch, effectively maintaining the positive pressure state and thermal balance of the hydraulic system, and improving system stability and operational reliability.

[0057] A filtration module is installed on the second replenishment line to filter impurities and particles during the return or replenishment process, ensuring that the cleanliness of the hydraulic oil entering the closed loop meets the system's operational requirements. The filtration module employs a high-precision hydraulic oil filter element structure, with a preferred filtration accuracy of 10μm to 25μm, effectively removing solid particulate impurities from the system's replenishment line and improving the cleanliness level of the system's hydraulic oil. To achieve real-time monitoring and control of the oil pressure during the main pump's replenishment process and ensure stable operation of the hydraulic system, a dedicated replenishment pressure monitoring module is installed on the main pump 8. This module, through a multi-point pressure measuring device and a pressure controller, constitutes a complete monitoring and alarm system, enabling dynamic feedback and abnormal warnings of the replenishment status.

[0058] Specifically, the replenishment pressure monitoring module includes a fourth pressure testing connector 29.4, a fifth pressure testing connector 29.5, a fourth pressure gauge 31, a pressure testing connector 32, and a pressure controller 33. The fourth and fifth pressure testing connectors 29.4 and 29.5 are arranged in parallel and installed on the return oil branch between the third check valve 11 and the first and second check valves 10.1 and 10.2. This arrangement allows for multi-point monitoring of the replenishment pressure in the return oil path. The fourth pressure testing connector 29.4 is connected to the fourth pressure gauge 31, which displays the replenishment pressure value at the testing point, allowing operators to monitor the system's current replenishment status in real time. The fifth pressure testing connector 29.5 is connected to the pressure controller 33 via the sixth pressure testing connector 32. This path transmits the replenishment pressure signal to the pressure controller for automatic system monitoring. The pressure controller 33 is equipped with an alarm threshold. The alarm pressure value is generally set to 0.6-0.8 MPa. When the detected pressure is lower than this threshold, the system can issue an alarm signal to indicate abnormal oil replenishment pressure and prevent pump damage or system failure.

[0059] It should be noted that the sixth pressure test connector 32 acts as an "intermediate interface" or "transition node". Its series connection with the fifth pressure test connector 29.5 enables the pressure signal from the fifth pressure test connector 29.5 to be reliably transmitted to the pressure controller 33, avoiding the inconvenience caused by direct connection.

[0060] As per the instruction manual Figure 2 The overflow flushing module includes a first finned overflow valve 12.1, a second finned overflow valve 12.2, and a shuttle valve 13. The first finned overflow valve 12.1 and the second finned overflow valve 12.2 are arranged in parallel. The inlet of the first finned overflow valve 12.1 is connected to the oil circuit on the output port A side of the finned pump 8.1 to control the highest pressure of the main oil circuit on the output port A side, and its outlet is connected to the oil circuit on the output port B side of the finned pump 8.1. The inlet of the second finned overflow valve 12.2 is connected to the oil circuit on the output port B side of the finned pump 8.1 to control the highest pressure of the main oil circuit on the output port B side, and its outlet is connected to the oil circuit on the output port A side of the finned pump 8.1.

[0061] The shuttle valve 13 is a spring-return hydraulic shuttle valve with two inlets and one outlet. During the operation of the finned pump system, it can automatically identify and connect the low-pressure side of the two main oil circuits, allowing the oil on that side to flow out for flushing. The two inlets of the shuttle valve 13 are connected to the main oil circuit corresponding to output port A and output port B of the finned pump 8.1, respectively, via pipelines. The outlet is connected to the replenishing overflow valve 14.

[0062] The finned hydraulic system is in operation, with the main pump 8.1 driving the finned actuator in reciprocating motion. In the system, main oil circuits A and B alternately act as high-pressure and low-pressure sides. To achieve closed-loop temperature control and oil renewal, the overflow flushing module is activated. When one side of the main oil circuit is at high pressure, and the set pressure of the finned overflow valve has not been reached, the finned overflow valve remains closed. Under normal operating conditions, the set pressure of the finned overflow valve is higher than the working pressure, and overflow will not occur. Figure 2 Taking the example shown, when the main oil circuit on the output port A side is high pressure and the main oil circuit on the output port B side is low pressure, and the pressure of the main oil circuit on the output port A side is higher than the set pressure of the first rotary fin overflow valve 12.1, the high pressure oil enters the oil inlet of the first rotary fin overflow valve 12.1 through points a4 and a3. The first rotary fin overflow valve 12.1 is turned on, and part of the high pressure oil is introduced into the right oil circuit through points a2 and a1 to release the pressure. At the same time, the high pressure side oil enters the shuttle valve 13 through points a4 and a3, pushing the valve core to move towards the low pressure side, thereby identifying and turning on the low pressure side main oil circuit. That is, a1 and a2 are connected to the oil outlet of the shuttle valve 13, and the high temperature low pressure oil is discharged for flushing. The discharged oil flows into the cooler 6 for cooling after passing through the oil outlet of the shuttle valve 13 and the oil replenishment overflow valve 14 in sequence, and finally returns to the oil tank 34 to complete the thermal balance management. Flushing the low-pressure side of the fin-rotating circuit can effectively reduce the temperature of the oil in the fin-rotating circuit, solving the problem of high oil temperature in closed hydraulic systems without a flushing circuit and improving the reliability of the equipment.

[0063] During the operation of the hydraulic system, to ensure the operational stability and oil cleanliness of the finned pump, the pressure of its main oil circuit needs to be monitored and controlled in real time. Therefore, a dedicated pressure monitoring module is installed in the main pump system to improve the safety and maintainability of system operation. Specifically, the pressure monitoring module includes a second pressure test connector 29.2, a third pressure test connector 29.3, a second pressure gauge 30.2, and a third pressure gauge 30.3. The second pressure test connector 29.2 and the third pressure test connector 29.3 are connected to the main oil circuit on one side of the finned pump 8.1, the second pressure gauge 30.2 is connected to the second pressure test connector 29.2, and the third pressure gauge 30.3 is connected to the third pressure test connector 29.3, enabling the monitoring and display of the pressure in the main oil circuits on both sides of the finned pump 8.1.

[0064] In this application, the short-circuit valve assembly includes a fourth check valve 17.1, a fifth check valve 17.2, a two-way cartridge valve, and a short-circuit solenoid valve 20. The oil passages on the A and B sides of the output port of the rotary pump 8.1 are connected to the oil passages of the two-way cartridge valve via the fourth check valve 17.1 and the fifth check valve 17.2, respectively. The fourth check valve 17.1 and the fifth check valve 17.2 are used to prevent oil from flowing back from the two-way cartridge valve to port A or port B, ensuring the unidirectional flow of oil and serving to prevent backflow and facilitate the flow of positive pressure oil. The two-way cartridge valve includes a valve core 18 and a cover plate 19. A spring is installed inside the two-way cartridge valve to maintain a normally closed state when there is no signal. When the short-circuit solenoid valve 20 is de-energized and remains in position a, the control chamber of the two-way cartridge valve core 18 is depressurized, the two-way cartridge valve core 18 opens, and the two main oil circuits of the fin pump 8.1 are connected to the internal oil passages of the short-circuit valve group, realizing a short circuit in the fin pump circuit. When the short-circuit solenoid valve 20 is energized, it switches to position b, high pressure is established in the control chamber of the two-way cartridge valve core 18, and the two-way cartridge valve core 18 closes under hydraulic pressure, cutting off the passage between the two main oil circuits of the fin pump 8.1 and the internal oil passages of the short-circuit valve group. The oil circuits on side A and side B of the output port of the fin pump 8.1 are not connected, and the fin pump system can rotate normally.

[0065] In this application, the zero-reset unlocking and servo valve group integrates the functions of servo circuit, zero-reset circuit, and unlocking circuit, including a sixth check valve 24, a servo circuit filter 25, an overflow valve 26, a zero-reset solenoid valve 27, and an unlocking solenoid valve 28. The inlet of the sixth check valve 24 is connected to the outlet of the auxiliary pump 22 through a pipeline, and its outlet is connected to the zero-reset solenoid valve 27. The outlet of the zero-reset solenoid valve 27 is converted from the V port of the zero-reset unlocking and servo valve group to the A2 port of the hydraulic unit through a pipeline, and then connected to the B2 port on the actuator. In turn, it is connected to the zero-reset piston on the first rotary fin cylinder 35.1 and the second rotary fin cylinder 35.2 through the B2 port on the actuator to form a zero-reset circuit and realize the zero-reset function.

[0066] A servo loop filter 25, a relief valve 26, and an unlocking solenoid valve 28 are sequentially installed along the connection path between the sixth check valve 24 and the zero-reset solenoid valve 27. The unlocking solenoid valve 28 is connected from port VI of the zero-reset unlocking and servo valve assembly via a pipeline to port A1 of the hydraulic unit, which is then connected to port B1 on the actuator. This port B1 on the actuator connects to the zero-locking cylinder 36, forming an unlocking circuit to achieve the unlocking / locking function. The circuit of the unlocking solenoid valve 28 is connected to the oil tank 34 for oil return.

[0067] The main pump 8 also includes a displacement sensor 15 and a servo valve 16. One end of the servo loop filter 25 is connected to the outlet of the sixth check valve 24, and the other end is connected to the inlet of the servo valve 16. Oil is supplied to the servo valve 16 through the servo loop filter 25. The displacement sensor 15 is connected to the fin pump 8.1 and the servo valve 16 to form a servo loop. When the anti-roll fin device is working, after entering the fin rotation state, the electronic control system controls the output flow of the servo valve 16 after amplification of the fin rotation command by the servo amplifier. The hydraulic power output by the servo valve 16 drives the variable mechanism of the fin pump 8.1, changing the swashplate tilt angle of the fin pump 8.1, and correspondingly changing the output flow of the fin pump 8.1. The hydraulic power output by the fin pump 8.1 drives the actuator to move, thereby driving the fin to rotate. The position of the variable cylinder of the fin pump 8.1 is fed back to the servo amplifier via the displacement sensor 15, forming a small closed loop within the system. The fin rotation angle signal is fed back to the servo amplifier via the fin angle transmitter, forming a fin angle position closed loop, thereby realizing servo control of the fin rotation movement.

[0068] The overflow valve 26 is connected in series in the servo control circuit. One end of it is connected to the servo circuit filter 25, and the other end is connected to the path between the unlocking solenoid valve 28 and the oil tank 34. The overflow valve 26 is set with an upper limit of the output pressure of the auxiliary pump 22, which is generally 10 to 12.5 MPa, to prevent system overpressure.

[0069] One end of the first pressure test connector 29.1 is connected to the first pressure gauge 30.1, and the other end is connected to the oil circuit before the relief valve 26, for monitoring and displaying the pressure of the auxiliary pump 22.

[0070] During normal operation of the ship's roll reduction device, the hydraulic system completes the zeroing and unlocking of the actuators according to the following control sequence. When the motor starts, the system begins to pressurize, and the zeroing solenoid valve 27 is in the default position a (power off). At this time, the oil flows sequentially through the auxiliary pump 22, the sixth check valve 24, and the zeroing solenoid valve 27 into the zeroing chambers of the first fin cylinder 35.1 and the second fin cylinder 35.2. The oil pushes the zeroing piston to move, bringing the roll reduction fin to the zero position and ensuring the initial alignment of the system. The unlocking solenoid valve 28 is in position a at this time. Afterward, the unlocking solenoid valve 28 switches to position b (energized), and the oil enters the zeroing cylinder 36, pushing the piston inside the cylinder to overcome the return spring force, thereby opening the locking mechanism and releasing the mechanical restriction. At the same time, the zeroing solenoid valve 27 switches to position b (energized), closing its internal oil circuit. At this time, the oil in the zeroing chamber is discharged to the return oil circuit through the zeroing solenoid valve, and the zeroing action ends. After zeroing and unlocking are completed, the servo system takes over control, and servo oil is supplied from filter 25 to servo valve 16 to achieve precise position control of the fin system. The system then enters normal anti-roll working state.

[0071] To ensure long-term stable operation of the system and control oil temperature rise, the hydraulic system is equipped with a cooling and filtration circuit. In this application, the hydraulic system also includes a cooler 6 and a return oil filter 5. The cooler 6 is located in the return oil circuit and releases heat from the return oil through heat exchange with an external cooling medium, thus controlling the system temperature. The return oil filter 5 is located after the cooler and is used to filter particulate impurities in the return oil, protecting the pump, valves, and servo components. The cooler and filter form a series cleaning circuit, improving the stability and lifespan of the hydraulic system.

[0072] In this application, the oil tank 34 integrates a first ball valve 1.1, a second ball valve 1.2, a level gauge 2, a thermometer 3, an air filter 4, a return oil filter 5, and a level control relay. The first ball valve 1.1 is the suction port switch valve for the replenishing oil pump. The second ball valve 1.2 is the suction port switch valve for the auxiliary pump. The level gauge 2 is used to observe the oil level in the tank. The thermometer 3 is used to detect the oil temperature in the tank; when the set high temperature value is reached, an alarm is triggered, and the equipment stops operating to protect the equipment. The air filter 4 is used to filter impurities and dust from the air entering the tank. The level control relay 7 is used to monitor the oil level in the tank; when the oil level is too low, an alarm is triggered, and the equipment stops operating to protect the equipment.

[0073] The following is a detailed comparative analysis of the hydraulic system structure of the present invention and the existing technology structure, comprehensively analyzing from the perspectives of structural integration, functional modularity and temperature control capability, system reliability and maintainability, to illustrate the advantages of the present invention.

[0074]

[0075]

[0076] This application also provides a control method for an integrated large-scale non-retractable anti-roll fin hydraulic system, the control method including:

[0077] Step 1: After the main motor of the hydraulic system starts, the auxiliary pump, fin pump and replenishing pump work synchronously. At this time, the zero-reset solenoid valve is in the default de-energized state (function a position). The auxiliary pump provides hydraulic power to the zero-reset circuit. The oil flows into the zero-reset solenoid valve after passing through the sixth check valve and the servo circuit filter in sequence, and enters the zero-reset chamber of the first fin cylinder and the second fin cylinder, pushing the zero-reset piston to move and reset the anti-roll fin to the zero position. At the same time, the short-circuit solenoid valve is in the default de-energized state (function a position), controlling the two-way cartridge valve to be in the open state, connecting the two ends of the main oil circuit to achieve short-circuit unloading.

[0078] The short-circuit solenoid valve is in a default de-energized state, and the two ends of the main oil circuit are short-circuited and unloaded. This ensures that the main oil circuit is in an unloaded state during the hydraulic system's zeroing process, allowing the motor to start without load, reducing the starting current, and improving the safety and reliability of the zeroing process.

[0079] Step 2: After the zeroing action is completed, the control system switches the unlocking solenoid valve to the energized state (function b position). The hydraulic oil supplied by the auxiliary pump enters the zeroing cylinder, pushing the internal piston to overcome the force of the reset spring, causing the telescopic pin to retract and unlocking the locking mechanism. Subsequently, the zeroing solenoid valve is also switched to the energized state (function b position), the short-circuit solenoid valve is energized, the valve port of the short-circuit valve group is closed, and the zeroing process ends.

[0080] Step 3: The hydraulic system enters the fin-rotating condition preparation state. The fin-rotating pump continues to run, keeping synchronized with the auxiliary pump and the replenishing pump. The replenishing pump delivers oil to the low-pressure side of the main oil circuit through the second replenishing pipeline. During the replenishing process, the oil is first cleaned by the filter module, and then the low-pressure side of the main oil circuit is identified by the first or second check valve and the oil is introduced through the first replenishing pipeline.

[0081] Step 4: In the fin-rotating state, the anti-roll fin system monitors the hull roll rate signal in real time via a gyroscope and transmits the detected signal to the central processing unit. After analyzing the signal, the processor outputs control commands. The servo amplifier amplifies the commands and drives the servo valve to move, controlling the variable cylinder to adjust the tilt angle and direction of the swashplate inside the fin pump, changing the direction and magnitude of the main pump's output flow, thereby driving the forward and reverse movements of the fin cylinder, driving the anti-roll fin to perform active oscillation, and achieving dynamic anti-roll control. During system operation, the overflow flushing module dynamically identifies the low-pressure side of the main oil circuit. When the main oil circuit pressure reaches the overflow valve threshold, some high-temperature hydraulic oil is guided through the corresponding fin overflow valve and shuttle valve to the replenishment overflow valve and then enters the cooler for cooling and returns to the oil.

[0082] Step 5: When the hydraulic system is de-energized, hydraulic power is provided by cranking the hand pump. The hand pump draws oil from the oil tank and pressurizes it for output. The zero-reset solenoid valve is still in the default de-energized state (function a position). The oil is introduced into the zero-reset chamber of the rotating fin cylinder through the zero-reset solenoid valve, pushing the zero-reset piston to the lowest position. During the reset process, the rotating fin piston is pushed at the same time to return the fin to the zero position. When the reset is completed, the telescopic pin in the zero-locking cylinder automatically springs into the fin shank pin hole under the action of the spring force to achieve mechanical locking, thus completing the reset and locking process.

[0083] The present invention discloses an integrated large-scale non-retractable fin damping hydraulic system and control method, which realizes a highly integrated, high-performance, and highly reliable large-scale non-retractable fin damping hydraulic control system. It effectively simplifies the structural layout, improves system response and stability, and enhances control accuracy and safety, and is particularly suitable for space-constrained ship applications.

[0084] The above descriptions are merely embodiments of this application, and common knowledge regarding specific structures and characteristics in the solutions is not described in detail here. It will be apparent to those skilled in the art that this application is not limited to the details of the above exemplary embodiments, and that this application can be implemented in other specific forms without departing from the spirit or essential characteristics of this application. Therefore, the embodiments should be considered exemplary and non-limiting in all respects, and the scope of this application is defined by the appended claims rather than the foregoing description. Therefore, it is intended that all variations falling within the meaning and scope of equivalents of the claims be included within this application. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. An integrated large-scale non-retractable anti-roll fin hydraulic system, characterized in that, Includes main pump (8), motor (21), auxiliary pump (22), zero-reset unlocking and servo valve group and oil tank (34). The motor (21) is a dual-output shaft three-phase asynchronous motor with a first output shaft end and a second output shaft end. The first output shaft end is connected to the fin pump (8.1) in the main pump (8) to provide power to the main circuit of the hydraulic system. The second output shaft end is connected to the auxiliary pump (22) to provide power to the servo, reset and unlock circuits. The main pump (8) integrates a fin pump (8.1), a replenishing pump (8.2), a filter module, a replenishing module, an overflow flushing module, and a short-circuit valve group. The fin pump (8.1) has two main oil circuits and has an output port A, an output port B, and a return port. The output port A and the output port B are respectively connected to one of the corresponding main oil circuits. The fin pump (8.1) has a bidirectional pressure supply function, which is used to dynamically switch the high-pressure side and the low-pressure side to realize the forward or reverse oil supply control of the anti-roll fin. The return port is connected to the oil tank (34). The output port A and the output port B are respectively connected to the two ends of the fin hydraulic cylinder to form a closed hydraulic circuit. The replenishing pump (8.2) is arranged in series at the rear of the fin pump (8.1) and is driven by a motor (21). The replenishing pump (8.2) has an inlet and an outlet. The inlet is connected to the oil tank (34), and the outlet is connected to the closed hydraulic circuit through the filter module and the replenishing module. The oil replenishment module includes a first check valve (10.1), a second check valve (10.2), a third check valve (11), an oil replenishment overflow valve (14), a first oil replenishment pipeline, and a second oil replenishment pipeline, wherein the two ends of the first oil replenishment pipeline are respectively connected to the finned motor pump ( The two main oil circuits of 8.1 are connected. The first check valve (10.1) and the second check valve (10.2) are set on the first replenishment oil line with their inlets facing each other and are connected in series between the two main oil circuits. They are used to dynamically identify and conduct the low-pressure side main oil circuit. The outlet end of the replenishment oil pump (8.2) is fluidly connected to the connecting pipeline between the first check valve (10.1) and the second check valve (10.2) through the second replenishment oil line. In the first replenishment oil line, and located at the first check valve (8.1) 10.1) A return oil branch connected to the oil tank (34) is provided between the second check valve (10.2) and the second check valve (10.2). A third check valve (11) and a replenishment relief valve (14) are connected in series on the return oil branch. The third check valve (11) is used to control the oil to flow to the oil tank in one direction, and the replenishment relief valve (14) is used to limit the replenishment pressure within the set pressure range. The overflow flushing module includes a first finned overflow valve (12.1), a second finned overflow valve (12.2), and a shuttle valve (13). The first finned overflow valve (12.1) and the second finned overflow valve (12.2) are connected in parallel to control the maximum pressure of the main oil circuits on the output port A and output port B sides, respectively, and their outlets are connected to the other side of the main oil circuit. The shuttle valve (13) has two inlets and one outlet. Its inlets are connected to the main oil circuits on the output port A side and the output port B side, respectively, and its outlet is connected to the oil tank (34) via the replenishing overflow valve (14) and the cooler, forming a cooling and return path for the flushing oil. The shuttle valve (13) has a valve core structure that can be operated under the drive of the oil, which is used to automatically identify the side of the two main oil circuits that is in a low-pressure state when receiving high-pressure oil and connect it to it, guiding the corresponding high-temperature low-pressure oil to the replenishing overflow valve (14) and then cooling and returning it to the oil tank (34). The zero-reset unlocking and servo valve group includes a zero-reset solenoid valve (27), which is connected to the zero-reset cylinder and is used to control the reset action of the anti-roll fin.

2. The integrated large-scale non-retractable anti-roll fin hydraulic system according to claim 1, characterized in that, It also includes a hand pump (23), which has an oil inlet and an oil outlet. Its oil inlet is connected to the oil tank (34), and its oil outlet is connected to the downstream of the reset solenoid valve (27), which is used to provide emergency oil supply to the reset circuit in the event of a power failure or malfunction of the hydraulic system.

3. The integrated large-scale non-retractable anti-roll fin hydraulic system according to claim 1, characterized in that, The inlet of the first rotary fin relief valve (12.1) is connected to the oil circuit on the A side of the output port, and is used to control the highest pressure of the main oil circuit on the A side of the output port. Its outlet is connected to the oil circuit on the B side of the output port. The inlet of the second rotary fin relief valve (12.2) is connected to the oil circuit on the B side of the output port, and is used to control the highest pressure of the main oil circuit on the B side of the output port. Its outlet is connected to the oil circuit on the A side of the output port.

4. The integrated large-scale non-retractable anti-roll fin hydraulic system according to claim 1, characterized in that, The oil replenishment module also includes a fourth pressure test connector (29.4), a fifth pressure test connector (29.5), a fourth pressure gauge (31), a sixth pressure test connector (32), and a pressure controller (33). The fourth pressure test connector (29.4) and the fifth pressure test connector (29.5) are arranged in parallel and installed on the branch from the third check valve (11) to the first check valve (10.1) and the second check valve (10.2). The fourth pressure test connector (29.4) is connected to the fourth pressure gauge (31), and the fifth pressure test connector (29.5) is connected to the pressure controller (33) through the sixth pressure test connector (32).

5. The integrated large-scale non-retractable anti-roll fin hydraulic system according to claim 4, characterized in that, It also includes a second pressure test connector (29.2), a third pressure test connector (29.3), a second pressure gauge (30.2), and a third pressure gauge (30.3). The second pressure test connector (29.2) and the third pressure test connector (29.3) are respectively connected to the main oil circuit on one side of the fin pump (8.1). The second pressure gauge (30.2) is connected to the second pressure test connector (29.2), and the third pressure gauge (30.3) is connected to the third pressure test connector (29.3). They are used to monitor and display the pressure of the main oil circuits on both sides of the fin pump (8.1).

6. The integrated large-scale non-retractable anti-roll fin hydraulic system according to claim 1, characterized in that, The zero-reset and unlocking system integrates a servo circuit, a zero-reset circuit, and an unlocking circuit with the servo valve group.

7. The integrated large-scale non-retractable anti-roll fin hydraulic system according to claim 6, characterized in that, The zero-lock and servo valve group also includes a sixth check valve (24), a servo loop filter (25), an overflow valve (26), and an unlocking solenoid valve (28). The sixth check valve (24) is connected to the output port of the auxiliary pump (22) through a pipeline on one side. The downstream of the sixth check valve is connected in series with the servo loop filter (25), the overflow valve (26), and the unlocking solenoid valve (28), and finally connected in parallel with the zero-lock solenoid valve (27) to form multiple branch control loops. The servo loop filter (25) is connected to the servo valve (16), the unlocking solenoid valve (28) is connected to the zero-lock cylinder (35), and the overflow valve (26) is located in the servo control loop.

8. The integrated large-scale non-retractable anti-roll fin hydraulic system according to claim 1, characterized in that, The main pump (8) also includes a displacement sensor (15) and a servo valve (16). The servo valve (16) is used to control the output flow rate of the fin-squeezing device after it enters the fin-squeezing state, according to the fin-squeezing command amplified by the servo amplifier in the electronic control system. The fin pump (8.1) adopts a swashplate piston pump. The variable of the fin pump (8.1) is controlled by the servo valve (16), the displacement sensor (15) and the variable mechanism inside the swashplate piston pump to form a closed-loop control system. The displacement sensor (15) is used to detect the position of the variable mechanism and feed it back to the servo amplifier.

9. The integrated large-scale non-retractable anti-roll fin hydraulic system according to claim 1, characterized in that, The oil tank (34) integrates a first ball valve (1.1), a second ball valve (1.2), a level gauge (2), a thermometer (3), an air filter (4), a return oil filter (5), and a level control relay (7).

10. A control method for an integrated large-scale non-retractable anti-roll fin hydraulic system as described in any one of claims 1-9, characterized in that, The control method includes: Step 1: When the main motor of the hydraulic system starts, the auxiliary pump, fin pump and oil replenishment pump work synchronously. At this time, the zero-reset solenoid valve is in the default de-energized state. The auxiliary pump provides hydraulic power for the zero-reset circuit. The oil flows into the zero-reset solenoid valve after passing through the sixth check valve and the servo circuit filter in sequence, and enters the zero-reset chamber of the first fin cylinder and the second fin cylinder, pushing the zero-reset piston to move and reset the anti-roll fin to the zero position. At the same time, the short-circuit solenoid valve is in the default de-energized state, controlling the two-way cartridge valve to be in the open state, connecting the two ends of the main oil circuit to achieve short-circuit unloading. Step 2: After the zeroing action is completed, the control system switches the unlocking solenoid valve to the energized state. The hydraulic oil supplied by the auxiliary pump enters the zeroing cylinder, pushing the internal piston to overcome the force of the reset spring, causing the telescopic pin to retract and unlocking the locking mechanism. Subsequently, the zeroing solenoid valve is also switched to the energized state, the short-circuit solenoid valve is energized, the valve port of the short-circuit valve group is closed, and the zeroing process ends. Step 3: The hydraulic system enters the fin-rotating condition preparation state. The fin-rotating pump continues to run, keeping in sync with the auxiliary pump and the replenishing pump. The replenishing pump delivers oil to the low-pressure side of the main oil circuit through the second replenishing pipeline. During the replenishing process, the oil is first cleaned by the filter module, and then the low-pressure side of the main oil circuit is identified by the first check valve or the second check valve and the oil is introduced through the first replenishing pipeline. Step 4: In the fin-rotating state, the anti-roll fin system monitors the hull roll rate signal in real time through a gyroscope and transmits the detection signal to the central processing unit. After analyzing the signal, the processor outputs control commands. The servo amplifier amplifies the commands and drives the servo valve to move, controlling the variable cylinder to adjust the tilt angle and direction of the swashplate inside the fin pump, changing the direction and magnitude of the flow rate output by the main pump, thereby driving the forward and reverse movements of the fin cylinder, driving the anti-roll fin to perform active oscillation, and realizing dynamic anti-roll control. During system operation, the overflow flushing module dynamically identifies the low-pressure side of the main oil circuit. When the pressure of the main oil circuit reaches the overflow valve threshold, some high-temperature hydraulic oil is guided through the corresponding fin overflow valve and shuttle valve to the replenishment overflow valve and then enters the cooler for cooling and returns to the oil. Step 5: When the hydraulic system is de-energized, hydraulic power is provided by cranking the hand pump. The hand pump draws oil from the oil tank and outputs it under pressure. The zero-reset solenoid valve is still in the default de-energized state. The oil is introduced into the zero-reset chamber of the rotating fin cylinder through the zero-reset solenoid valve, pushing the zero-reset piston to the lowest position. During the reset process, the rotating fin piston is pushed at the same time to return the fin to the zero position. When the reset is completed, the telescopic pin in the zero-locking cylinder automatically springs into the fin shank pin hole under the action of the spring force to achieve mechanical locking, thus completing the reset and locking process.

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