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

Abstract

The invention belongs to the technical field of ship fin stabilizers and hydraulics, and particularly relates to an integrated large non-retractable fin stabilizer hydraulic system and a control method thereof.The hydraulic system comprises a main pump, a motor, an auxiliary pump, a zero resetting unlocking and servo valve set and an oil tank, the first output shaft end of the motor drives a fin rotating pump in the main pump and supplies energy to a main loop, and the second output shaft end of the motor drives a second output shaft of the motor; the second output shaft end drives the auxiliary pump to supply energy to the servo, zero resetting and unlocking loop, the main pump integrates a fin rotating pump, an oil supplementing pump, a filtering module, an oil supplementing module, an overflow flushing module and a short circuit valve set, the output end of the fin rotating pump and a fin rotating oil cylinder of an executing mechanism form a closed type hydraulic loop to achieve forward and reverse fin rotating, and the oil supplementing pump is driven by a motor. And the zero resetting electromagnetic valve is connected to a main loop through a filtering and oil supplementing module and is communicated with the zero resetting oil cylinder. Through integrated optimization, hydraulic elements and pipelines are reduced, the oil temperature is controlled, the stability and reliability of the system are improved, integrated lightweight design is achieved, and the fin stabilizer device meets the requirements of large ships for high-performance fin stabilizers.

Description

Technical Field

[0001] The present application belongs to the field of ship fin stabilizers and hydraulic technology, and specifically relates to an integrated large-scale non-retractable fin stabilizer hydraulic system and a control method thereof. Background Art

[0002] While a ship is sailing or moored, waves at sea can induce rolling motion, severely impacting its stability and comfort. To reduce rolling, fin stabilizers, a widely used active anti-roll device, have been extensively verified and applied on various ship types. Especially during strong waves, fin stabilizers can significantly reduce the ship's roll angle, thereby improving navigation safety and crew comfort.

[0003] Fin stabilizers are primarily categorized as retractable or non-retractable, depending on whether they are retractable or not. Both types of fin stabilizers typically consist of fin blades, actuators, hydraulic units, electronic control equipment, and fin mounts (for non-retractable) or fin boxes (for retractable). 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 economic viability of the entire fin stabilizer system.

[0004] However, existing fin stabilizer hydraulic systems still face numerous challenges that require urgent improvement. First, the system's complex structure and the use of numerous discrete hydraulic components result in a large number of connecting pipes, cumbersome layout, difficult installation, and multiple potential leaks. Second, some hydraulic systems utilize closed fin-rotating circuits but lack effective oil flushing mechanisms, which can easily cause oil temperatures to rise, affecting system stability and component life. This results in insufficient system reliability and significant maintenance difficulties, making it difficult to meet the long-term operational requirements of modern high-performance vessels.

[0005] Furthermore, the trend toward larger ships places greater demands on the structural strength and performance stability of roll stabilization systems. Simply scaling up existing small and medium-sized systems often results in excessive size and weight, making system performance difficult to guarantee, while significantly increasing the complexity of manufacturing and installation. Consequently, current technical architectures and solutions are no longer adequate for the efficient, compact, and easily maintainable roll stabilization systems required by large vessels. Comprehensive technological innovation in system integration, structural optimization, and functional reliability is urgently needed. Summary of the Invention

[0006] In order to solve the technical problems of the existing fin stabilizer hydraulic system, such as the large number of hydraulic components, complex system pipeline connections, and high oil temperature in the closed fin rotation circuit, the present application provides an integrated large-scale non-retractable fin stabilizer hydraulic system and its control method. Through integrated optimization design, the system reduces the number of hydraulic components and the complexity of the pipelines, effectively controls the system oil temperature, and improves operational stability. In addition, in response to the trend of large-scale equipment, the system fully considers the coordination and matching between the technical performance, structural dimensions and weight of the hydraulic system and the ship installation requirements, and proposes an integrated and modular system configuration scheme. The present invention not only realizes the integrated and lightweight design of the large-scale fin stabilizer hydraulic system, reduces the space occupied in the cabin, but also improves the reliability and maintenance convenience of the equipment, and is suitable for the technical requirements of modern large ships for high-performance anti-roll devices.

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

[0008] The motor is a double-shaft three-phase asynchronous motor having a first shaft end and a second shaft end. The first shaft end is connected to the fin pump in the main pump to provide power for the main circuit of the hydraulic system. The second shaft end is connected to the auxiliary pump to provide power for the servo, reset and unlock circuits.

[0009] The main pump integrates a fin pump, an oil feed pump, a filter module, an oil feed module, an overflow flushing module and a short-circuit valve group. The fin pump is provided with two main oil circuits, and has an output port A, an output port B and an oil return port. The output port A and the output port B are respectively connected to a corresponding main oil circuit. The fin pump has a two-way pressure supply function, which is used to dynamically switch the high-pressure side and the low-pressure side to realize forward or reverse oil supply control of the stabilizer fin; the oil return port is connected to the oil tank, and 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 oil feed pump is arranged in series at the rear of the fin pump and is driven by an electric motor. The oil feed pump is provided with an oil inlet and an oil outlet. The oil inlet is connected to the oil tank, and the oil outlet is connected to the closed hydraulic circuit through the filter module and the oil feed module;

[0010] The oil replenishment module includes a first one-way valve, a second one-way valve, a third one-way valve oil replenishment overflow valve, 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 two main oil circuits of the fin pump, the first one-way valve and the second one-way valve are arranged on the first oil replenishment pipeline with their oil inlets facing each other, and are connected in series between the two main oil circuits, for dynamically identifying and conducting the low-pressure side main oil circuit; the outlet end of the oil replenishment pump is fluidically connected to the connecting pipeline between the first one-way valve and the second one-way valve through the second oil replenishment pipeline; an oil return branch connected to the oil tank is provided in the first oil replenishment pipeline and between the first one-way valve and the second one-way valve, and a third one-way valve and an oil replenishment overflow valve are sequentially arranged in series on the oil return branch, the third one-way valve is used to control the one-way flow of oil to the oil tank, and the oil replenishment overflow valve is used to limit the oil replenishment pressure within a set pressure range;

[0011] The overflow flushing module includes a first fin overflow valve, a second fin overflow valve and a shuttle valve; the first fin overflow valve and the second fin overflow valve are arranged in parallel, respectively used to control the maximum pressure of the main oil circuit on the output port A and output port B sides, and their outlets are respectively connected to the main oil circuit on the other side; the shuttle valve has two oil inlets and one oil outlet, and its oil inlet is respectively connected to the main oil circuit on the output port A side and the main oil circuit on the output port B side, and the oil outlet is connected to the oil tank through the oil replenishment overflow valve and the cooler, forming a cooling and oil return path for the flushing oil; the shuttle valve has a valve core structure that can be actuated by oil drive, and is used to automatically identify the side of the two main oil circuits in a low-pressure state when receiving high-pressure oil and connect it to it, and guide the corresponding high-temperature and low-pressure oil to the oil replenishment overflow valve and then return it to the oil tank after cooling;

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

[0013] In a preferred implementation, it further includes a hand pump, which is provided with an oil inlet and an oil outlet, wherein the oil inlet is connected to the oil tank, and the oil outlet is connected to the downstream of the reset solenoid valve, for realizing emergency oil supply of the reset circuit when the hydraulic system is out of power or fails.

[0014] In a preferred implementation, further, the inlet of the first fin-turning relief valve is connected to the oil circuit on the output port A side, for controlling 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 fin-turning relief valve is connected to the oil circuit on the output port B side, for controlling 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 replenishing module further includes a fourth pressure measuring joint, a fifth pressure measuring joint, a fourth pressure gauge, a sixth pressure measuring joint and a pressure controller; the fourth pressure measuring joint and the fifth pressure measuring joint are arranged in a parallel structure and are installed on a branch line from the third one-way valve to between the first one-way valve and the second one-way valve, the fourth pressure measuring joint is connected to the fourth pressure gauge, and the fifth pressure measuring joint is connected to the pressure controller via the sixth pressure measuring joint.

[0016] In a preferred implementation, it further includes a second pressure measuring joint, a third pressure measuring joint, a second pressure gauge and a third pressure gauge, wherein the second pressure measuring joint and the third pressure measuring joint are respectively connected to the main oil circuit on one side of the fin pump, the second pressure gauge is connected to the second pressure measuring joint, and the third pressure gauge is connected to the third pressure measuring joint, for monitoring and displaying the pressure of the main oil circuit on both sides of the fin pump.

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

[0018] In a preferred implementation, further, the reset, unlock and servo valve group also includes a sixth one-way valve, a servo loop filter, a relief valve and an unlocking solenoid valve; one side of the sixth one-way valve is connected to the output port of the auxiliary pump through a pipeline, and its downstream is connected in series with the servo loop filter, the relief valve and the unlocking solenoid valve in sequence, and finally connected in parallel with the reset solenoid valve to form multiple branch control loops; the servo loop filter is connected to the servo valve, the unlocking solenoid valve is connected to the zeroing cylinder, and the relief valve is arranged in the servo control loop.

[0019] In a preferred implementation, the main pump further includes a displacement sensor and a servo valve, wherein the servo valve is used to control its output flow according to the fin rotation instruction amplified by the servo amplifier of the electronic control system after the fin stabilizer 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 implementation, further, the oil tank is integrated with a first ball valve, a second ball valve, a liquid level gauge, a thermometer, an air filter, a return oil filter and a liquid level control relay.

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

[0022] Step 1: After the main motor of the hydraulic system is started, the auxiliary pump, the fin pump and the charge pump work synchronously. At this time, the zeroing solenoid valve is in the default power-off state. The auxiliary pump provides hydraulic power for the zeroing circuit. The oil flows into the zeroing solenoid valve after passing through the sixth one-way valve and the servo circuit filter, and enters the zeroing chamber of the first fin cylinder and the second fin cylinder, pushing the zeroing piston to move and reset the fin stabilizer to zero position. At the same time, the short-circuit solenoid valve is in the default power-off 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 completing the zero reset action, the control system switches the unlocking solenoid valve to the energized state. The hydraulic oil provided by the auxiliary pump enters the zero lock cylinder, pushing the internal piston to overcome the return spring force, causing the telescopic pin to retract and unlocking the locking mechanism. Subsequently, the zero reset solenoid valve is also switched to the energized state, and the valve port of the short-circuit valve group is closed. The zero reset process is completed.

[0024] Step 3: The hydraulic system enters the fin rotation working condition preparation state. The fin rotation pump continues to operate, keeping synchronization with the auxiliary pump and the oil supply pump. The oil supply pump delivers oil to the low-pressure side of the main oil circuit through the second oil supply line. During the oil supply process, the oil is first cleaned by the filter module, and then the first one-way valve or the second one-way valve is used to identify the low-pressure side of the main oil circuit and introduce the oil through the first oil supply line.

[0025] Step 4: In the fin-turning state, the fin stabilizer system monitors the ship's roll angular velocity signal in real time through the gyroscope and transmits the detection signal to the central processing unit. The processor analyzes the signal and outputs a control instruction. The servo amplifier amplifies the instruction and drives the servo valve to operate, controlling the variable cylinder to adjust the inclination and direction of the swash plate in the fin pump, changing the direction and size of the flow output of the main pump, and realizing the forward and reverse drive of the fin-turning cylinder, driving the fin stabilizer to perform active swing and realize 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 directed through the corresponding fin-turning overflow valve and shuttle valve to the oil replenishment overflow valve and then enters the cooler for cooling and oil return.

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

[0027] The beneficial effects of this application are:

[0028] First, the integrated large-scale non-retractable fin stabilizer hydraulic system of the present application highly integrates the main pump (including fin pump and oil replenishment pump), filter module, oil replenishment module, overflow flushing module and short-circuit valve group into one, 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 large ship engine rooms with limited space; a dual-shaft motor is used to drive the main pump and the auxiliary pump respectively, realizing physical separation of the power source of the main circuit (fin drive) and the control circuit (servo, reset, unlocking), improving the system response speed and action stability, and ensuring good control accuracy and anti-interference ability under various working conditions; the main circuit adopts a closed hydraulic system, and a dynamic flushing channel is constructed through the oil replenishment pump and a dedicated overflow flushing module to timely guide the high-temperature oil to discharge The system can discharge and replenish low-temperature new oil, solving the technical bottleneck of excessive oil temperature in the operation of traditional closed systems, which affects the stability and service life of the system; the three control functions of zeroing, unlocking and servo are integrated into a unified valve group module, and cooperate with the independent oil supply and pressure limiting protection of the auxiliary pump to meet the needs of multi-mode fin rotation operation and improve the overall consistency, modularity and maintainability of the system; the hand pump is set in the zeroing circuit, and oil can be manually supplied to the zeroing solenoid valve in the event of power failure or system failure, ensuring that the fin zeroing action can be completed under extreme working conditions, thereby enhancing the system's emergency support capability; the system is specially designed for large non-retractable anti-roll fins, solving the problems of redundant volume and performance degradation caused by proportional enlargement of traditional systems, and realizing a highly integrated, high-performance and highly reliable ship anti-roll hydraulic control solution while ensuring structural strength.

[0029] Second, in the preferred implementation, the oil replenishment module of the present application can automatically identify and connect to the low-pressure side of the current circuit by setting a first one-way valve and a second one-way valve arranged oppositely between the main oil circuit of the fin pump, thereby realizing dynamic and intelligent low-pressure oil replenishment. This structure enables the system to judge the pressure state of the main oil circuit in real time under different 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 one-way valve and the oil replenishment overflow valve arranged between the low-pressure side and the oil tank ensure that the excess oil can be controlled to drain back and the oil replenishment pressure is limited to protect the system, effectively preventing system overpressure or oil shock problems; a multi-point pressure measurement and control structure is further provided in the oil replenishment module, which is connected to the fourth pressure gauge and the pressure controller respectively through the fourth pressure measuring joint and the fifth pressure measuring joint arranged in parallel on the return oil branch, thereby 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, the present application sets a first fin relief valve and a second fin relief valve on the main oil circuits on both sides of the fin pump, respectively, to effectively limit the maximum pressure of the system in the oil return state, prevent the oil temperature from rising or the actuator from getting stuck due to excessive back pressure in the circuit, thereby improving the stability and safety of the system operation. At the same time, with the help of the shuttle valve structure, automatic identification and flushing on-off switching of the high and low pressure sides are achieved, ensuring continuous flushing of the low-pressure circuit, improving the problem of oil heat accumulation and contamination, and extending the service life of the oil and components. In addition, by integrating the second and third pressure measuring joints and pressure gauges, real-time monitoring and visual display of the pressure of the main oil circuits on both sides are achieved, providing reliable data support for debugging, maintenance and troubleshooting.

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

[0032] Fifth, in a preferred implementation, the main pump of this application is integrated with a displacement sensor and servo valve, creating a closed-loop control structure. Once the fin stabilizer enters the fin rotation mode, the main pump's output flow rate can be adjusted and precisely controlled in real time based on fin rotation commands input from the electronic control system. The servo valve dynamically adjusts the pump's flow rate based on signals processed by the servo amplifier, while the displacement sensor detects the displacement of the variable mechanism in real time and generates position feedback, enabling highly precise fin rotation control.

[0033] Sixth, in a preferred implementation, the present application establishes fluid communication between the oil outlet of the oil replenishment pump and the connecting pipeline between the first one-way valve and the second one-way valve in the closed hydraulic circuit via the second oil replenishment pipeline, thereby achieving dynamic oil replenishment balance for the low-pressure chambers on both sides of the closed circuit.

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

[0035] Eighth, the control method of the integrated large-scale non-retractable fin stabilizer hydraulic system of the present invention realizes the precise zeroing of the fin cylinder through the control of the zeroing solenoid valve, ensuring accurate system initialization. It adopts an electronically controlled hydraulically driven unlocking mechanism to ensure the controllable release of the fin handle, improving system safety. In combination with gyroscope detection and servo adjustment, it realizes dynamic response to hull roll and active roll reduction. In the event of system abnormality or power outage, it has automatic pressure relief and manual reset mechanisms to ensure the safe return of the system to zero position in an emergency. BRIEF DESCRIPTION OF THE DRAWINGS

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

[0037] Figure 2 Schematic diagram of an 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-liquid level gauge; 3-thermometer; 4-air filter; 5-return oil filter; 6-cooler; 7-liquid level relay, 8-main pump; 8.1-rotating fin pump; 8.2-supply oil pump; 9-supply oil filter; 10.1-first one-way valve; 10.2-second one-way valve; 11-third one-way valve; 12.1-first rotating fin relief valve; 12.2-second rotating fin relief valve; 13-shuttle valve; 14-supply oil relief valve; 15-displacement sensor; 16-servo valve; 17.1-fourth one-way valve; 17.2-fifth one-way valve; 18-two-way cartridge valve core; 19-two-way cartridge valve cover; 20-short Circuit solenoid valve; 21-electric motor; 22-auxiliary pump; 23-hand pump; 24-sixth one-way valve; 25-servo circuit filter; 26-relief valve; 27-zeroing solenoid valve; 28-unlocking solenoid valve; 29.1-first pressure measuring joint; 29.2-second pressure measuring joint; 29.3-third pressure measuring joint; 29.4-fourth pressure measuring joint; 29.5-fifth pressure measuring joint; 30.1-first pressure gauge; 30.2-second pressure gauge; 30.3-third pressure gauge; 31-fourth pressure gauge; 32-sixth pressure measuring joint; 33-pressure controller; 34-oil tank; 35.1-first fin cylinder; 35.2-second fin cylinder; 36-zero locking cylinder. DETAILED DESCRIPTION

[0039] In order to enable those skilled in the art to better understand the technical solution of the present application, the present application will be further described in detail below with reference to the accompanying drawings and embodiments.

[0040] The terms "up", "down", "left", "right", "front", and "back" in this application are based on the positional relationships shown in the accompanying drawings. The corresponding positional relationships may vary depending on the drawings, and should not be construed as limiting the scope of protection.

[0041] In this application, the terms "installed," "connected," "connected," "connected," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, integral connection, mechanical connection, electrical connection, or mutual communication. They can also be directly connected or indirectly connected through an intermediate medium. They can also refer to internal communication between two components or interaction between two components. For those skilled in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0042] Example

[0043] Refer to the instruction manual Figure 1 , the embodiment describes an integrated large-scale non-retractable fin stabilizer hydraulic system, which not only has the advantages of system-level integrated optimization and temperature control management, but also provides a stable and controllable driving force for the actuator of the fin stabilizer, thereby realizing active swing control of the fin stabilizer in a strong wind and wave environment, and achieving the purpose of effectively suppressing the roll of the hull. The actuator is used to drive the swinging motion of the fin stabilizer, 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-turning cylinder. Among them, the high-pressure circuit is responsible for delivering the high-pressure oil output by the main pump to the push chamber of the fin-turning cylinder, generating a 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-turning cylinder, and cooperating with the oil replenishment module to maintain the system 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-turning cylinder 35.1 and a second fin-turning cylinder 35.2, a fin shaft, a fin handle, and a locking mechanism. The first fin-turning cylinder 35.1 and the second fin-turning cylinder 35.2 are both linear reciprocating actuators, and their piston rods are rigidly connected to the two ends of the fin handle respectively. 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 blade in the axial direction of the fin shaft. The first fin-turning cylinder 35.1 and the second fin-turning 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 by the present application to realize the forward and reverse control and zeroing operation of the anti-roll fin. The locking mechanism includes a telescopic pin and a zero-locking cylinder 36 that controls its telescopic action. The zero-locking cylinder 36 is a hydraulic drive component, and its oil inlet and outlet are connected to the hydraulic system of the present application. A pin hole corresponding to the position of the telescopic pin is provided on the fin handle. When the hydraulic system of the application performs the zeroing operation, the zero locking cylinder drives the telescopic pin to extend and insert it into the pin hole to form mechanical positioning and locking to ensure that the fin stabilizer remains fixed in the zeroing state to prevent malfunction.

[0045] Specifically, the integrated large-scale non-retractable fin anti-roll hydraulic system of the present application includes a main pump 8, an electric motor 21, an auxiliary pump 22, a reset unlocking and servo valve group, a hand pump 23 and an oil tank 34. The electric motor 21 adopts a double-output 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. Its body integrates multiple functional modules, namely, a fin pump 8.1, an oil replenishment pump 8.2, a filter module, an oil replenishment module, an overflow flushing module and a short-circuit valve group. The driving shaft of the fin pump 8.1 is connected to the first output shaft end of the electric motor 21 through a coupling, which is used to provide power for the main circuit of the hydraulic system and then drive the fin hydraulic cylinder. The oil replenishment pump 8.2 is integrated into the structure of the main pump 8, obtains driving power through a coaxial transmission mechanism with the fin pump 8.1, and is driven by the electric motor 21 to achieve synchronous driving of the fin pump 8.1 and the oil replenishment pump 8.2. The drive shaft of the auxiliary pump 22 is connected to the second output shaft end of the motor 21 through a coupling, and is used to provide power for auxiliary circuits such as servo, reset, and unlocking.

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

[0047] Output port A and output port B serve as the bidirectional output ports of the main pump 8, respectively, and are connected through pipelines to ports A3 and A4 of the hydraulic unit. Ports A3 and A4 are connected to ports B3 and B4 of the actuator structure, respectively, to form a closed hydraulic circuit. Among them, port B4 corresponds to the top cavity of the fin-turning piston of the first fin-turning cylinder 35.1 and the bottom cavity of the fin-turning piston of the second fin-turning cylinder 35.2, and is used to input high-pressure hydraulic oil to compress the top of the piston of the first fin-turning cylinder 35.1 to drive the piston rod to extend, and simultaneously push the bottom of the piston of the second fin-turning cylinder 35.2 to drive its piston rod to retract. Port B3 corresponds to the bottom cavity of the fin-turning piston of the first fin-turning cylinder 35.1 and the top cavity of the fin-turning piston of the second fin-turning cylinder 35.2, and is used to input high-pressure hydraulic oil to push the bottom of the piston of the first fin-turning cylinder 35.1 to drive the piston rod to retract, and simultaneously compress the top of the piston of the second fin-turning cylinder 35.2 to drive its piston rod to extend.

[0048] Fin pump 8.1 uses a bidirectional variable hydraulic pump, capable of switching between forward and reverse oil supply. When the variable mechanism within fin pump 8.1 controls the forward motion of the swash plate within main pump 8, output port A is high-pressure. The oil circuit on the side of this port on the fin pump 8.1 is the high-pressure side. This high-pressure oil circuit enters port B3 of the actuator via port A3, then enters the piston bottom cavity of the first fin cylinder 35.1 and the piston top cavity of the second fin cylinder 35.2, driving the fin pistons. The hydraulic oil in the piston top cavity of the first fin cylinder 35.1 and the piston bottom cavity of the second fin cylinder 35.2 flows through port B4 of the actuator, then through port A4, and into output port B. At this point, the oil circuit on the side of output port B on the fin pump 8.1 is low-pressure, and output port B is the return oil source.

[0049] When the swash plate in main pump 8 moves in the reverse direction and output port B outputs high pressure, the oil circuit connected to this port, located on the side of fin pump 8.1, becomes the high-pressure side. The opposite output port, output port A, located on the side of fin pump 8.1, becomes the low-pressure side, with output port A being the return oil source. This structure supports bidirectional extension and retraction of the fin hydraulic cylinder. The two main oil circuits of fin pump 8.1 alternate between supplying and returning oil in different system operating states, achieving forward and reverse control of the fin stabilizer. The high-pressure and low-pressure sides of fin pump 8.1 change dynamically with the direction of the fins.

[0050] In order to realize the dynamic pressure identification and function distribution of the closed hydraulic system, the oil replenishment module, the overflow flushing module and the short-circuit valve group are arranged in parallel between the two main oil circuits mentioned above to realize automatic identification and response to the high and low pressure status of the current oil circuit. The oil replenishment module is arranged in the front section of the main oil circuit. The oil replenishment pump 8.2 is provided with an oil inlet and an oil outlet, wherein the oil inlet is connected to the oil tank 34, and the oil outlet is connected to the oil replenishment module via a filter module, so that the replenishment oil is first cleaned and filtered by the filter module before entering the fin turning circuit to ensure the cleanliness of the oil replenishment medium. The overflow flushing module is arranged at the rear position of the midstream section of the main oil circuit, and is used to discharge the high-temperature oil on the low-pressure side of the fin turning circuit out of the circuit by overflow, so as to realize system cooling and oil renewal. The short-circuit valve group is configured between the oil replenishment module and the overflow flushing module, and is used to connect the two ends of the oil circuit when the system is powered off or in a fault state, to complete emergency unloading and automatic resetting of the fin surface.

[0051] The zero reset unlocking and servo valve assembly includes a zero reset solenoid valve 27 connected to the zero reset cylinder 36 in the actuator. This zero reset solenoid valve 27 controls the zero reset during a system reset. A hand pump 23 has an oil inlet and an oil outlet. Its inlet is connected to the oil tank 34, and its outlet is connected via a pipeline to the downstream side of the zero reset solenoid valve 27. Serving as a backup hydraulic power unit in the event of a system power outage, the hand pump 23 can be manually operated to draw oil from the oil tank 34 and deliver pressurized oil to the zero reset oil circuit, driving the fin actuator to complete the zero reset operation.

[0052] Through the above structure, the main pump of this application drives a bidirectional hydraulic circuit, providing a stable driving force for the anti-roll fins, and supporting forward and reverse control to achieve active swinging under strong winds and waves to suppress the hull's roll. The system integrates modules such as oil replenishment, filtration, flushing and cooling, and short-circuit unloading, which simplifies the system structure, reduces the number of discrete components and pipelines, reduces the difficulty of layout and installation, and has the ability to dynamically identify oil pressure and allocate functions. It adopts a closed circuit and introduces an overflow flushing mechanism to improve the oil temperature management capability, ensure system stability and component life, and adopts a dual-shaft motor to drive the main and auxiliary pumps. It is equipped with a hand pump and a zeroing solenoid valve to support power-off reset and emergency operation, ensuring efficient, stable and reliable operation of the system.

[0053] In a preferred embodiment of this application, fin pump 8.1 utilizes a swash plate piston pump with variable displacement and reversible flow direction. The displacement and direction are controlled by the swash plate angle; changing the swash plate angle alters the pump's displacement. The variable speed of fin pump 8.1 is controlled via a closed-loop control system comprised of a servo valve 16, a displacement sensor 15, and the variable speed mechanism within the swash plate piston pump. This controls the swash plate of fin pump 8.1, thereby controlling the output flow rate and direction of the oil.

[0054] It should be noted that the variable displacement mechanism within the rotating fin pump 8.1 includes a swash plate, a plunger, a variable displacement piston, a variable displacement control valve, a return spring, and a pump housing. The swash plate is hingedly connected to the housing. One end of the plunger is mounted within a bore in the cylinder body, while the other end contacts the swash plate. The inclined surface of the swash plate slides in contact with the plunger. The variable displacement piston is mounted within the housing, pushing the swash plate to adjust its angle. The variable displacement control valve is connected to the variable displacement piston, regulating the oil pressure in its two chambers. A return spring, located on the back of the variable displacement piston, returns the swash plate to its initial angle. The drive shaft of the rotating fin pump 8.1 rotates at high speed under the power of the motor 21, simultaneously rotating the cylinder body to which it is rigidly connected. Multiple plungers are embedded in an annular arrangement of plunger holes within the cylinder body. The plunger tails slide in contact with the inclined surface of the swash plate. Because the swash plate is tilted, the plungers are constantly pushed away from or pressed back into the cylinder body during rotation, achieving reciprocating motion. The plunger stroke is proportional to the swash plate's inclination angle. The larger the inclination angle, the longer the stroke and the greater the displacement per unit time. If the inclination angle is zero (the swash plate is vertical), there is no plunger motion, and the displacement is zero. The two oil circuits of the fin pump 8.1 have corresponding plunger cavities and cylinder channels. Under different swash plate inclination directions, one side forms high-pressure oil supply and the other side forms low-pressure oil return.

[0055] In the implementation of this application, the oil replenishment module includes a first one-way valve 10.1, a second one-way valve 10.2, a third one-way valve 11, an oil replenishment relief valve 14, a first oil replenishment pipeline and a second oil replenishment pipeline, forming a closed hydraulic system oil replenishment passage with a compact structure and coordinated functions. The first oil replenishment pipeline is the attached manual. Figure 1Points b1 to b2 in the diagram are used to identify the low-pressure side of the system, provide targeted oil replenishment, and discharge excess oil into the tank. The two ends of the first oil replenishment line are respectively connected to the two main oil circuits of the fin pump 8.1. A first one-way valve 10.1 and a second one-way valve 10.2 are arranged on the first oil replenishment line with their oil 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 conduct only the low-pressure side to achieve targeted oil replenishment on the low-pressure side.

[0056] An oil return branch is provided in the first oil replenishment pipeline and between the first one-way valve 10.1 and the second one-way valve 10.2. The oil return branch is connected to the oil tank 34 and is used to discharge excess oil during the oil replenishment process to ensure the oil balance of the system. The oil return branch is sequentially connected with the third one-way valve 11 and the oil replenishment overflow valve 14 to construct a constant pressure oil return circuit. The third one-way valve 11 controls the one-way flow of oil to the oil tank 34 to prevent the oil from flowing back. The oil replenishment overflow valve 14 sets the overflow pressure of the oil replenishment channel to ensure that the system pressure remains within the range of 1.6-2.5MPa. The oil replenishment pump 8.2 is a gear pump or a vane pump, which is configured in the closed circuit of the hydraulic system. The second oil replenishment pipeline is attached to the instruction manual. Figure 1 Points b3 to b4 in the diagram form the fluid connection path between the outlet of the replenishment pump 8.2 and the first replenishment line, which is used to ensure that the oil delivered by the replenishment pump enters the main system. The outlet of the replenishment pump 8.2 is fluidically connected to the connecting line between the first check valve 10.1 and the second check valve 10.2 in the first replenishment line through the second replenishment line, completing the directional replenishment of the low-pressure side of the closed loop. The second replenishment line is further connected to the return oil branch of the replenishment module. When the system is running, the module automatically directs the oil delivered by the replenishment pump 8.2 to the low-pressure side circuit of one of the two main oil circuits, and at the same time overflows back to the oil tank 34 through the return oil 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 oil replenishment line to filter out impurity particles during the return or replenishment process, ensuring that the cleanliness of the hydraulic oil entering the closed circuit meets the system's operating requirements. The filtration module uses a high-precision hydraulic oil filter element structure, with a filter element filtration accuracy of preferably 10μm to 25μm. This filter element can effectively remove solid particle impurities from the system's oil replenishment line and improve the cleanliness level of the system's hydraulic oil. To achieve real-time monitoring and control of the oil pressure during the main pump replenishment process and ensure the stable operation of the hydraulic system, a dedicated oil replenishment pressure monitoring module is installed on the main pump 8. This module, through a multi-point pressure measuring device and a pressure controller, forms a complete monitoring and alarm system, capable of dynamic feedback on the oil replenishment status and abnormal warning.

[0058] Specifically, the oil replenishment pressure monitoring module includes a fourth pressure measuring joint 29.4, a fifth pressure measuring joint 29.5, a fourth pressure gauge 31, a pressure measuring joint 32, and a pressure controller 33. Among them, the fourth pressure measuring joint 29.4 and the fifth pressure measuring joint 29.5 are arranged in parallel and are installed on the return oil branch from the third one-way valve 11 to the first one-way valve 10.1 and the second one-way valve 10.2. This setting can perform multi-point monitoring of the oil replenishment pressure in the return oil path. The fourth pressure measuring joint 29.4 is connected to the fourth pressure gauge 31, and the fourth pressure gauge 31 is used to intuitively display the oil replenishment pressure value of the pressure measuring point so that the operator can grasp the current oil replenishment status of the system in real time. The fifth pressure measuring joint 29.5 is connected to the pressure controller 33 through the sixth pressure measuring joint 32. This path is used to transmit the oil replenishment pressure signal to the pressure controller to realize automatic monitoring of the system. The pressure controller 33 is provided with an alarm threshold, which is generally set at 0.6-0.8 MPa. When the detected pressure is lower than the threshold, the system may issue an alarm signal to indicate that the oil replenishment pressure is abnormal, thereby preventing pump damage or system failure.

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

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

[0061] Shuttle valve 13 is a spring-return, hydraulically controlled shuttle valve with two oil inlets and one outlet. During fin-spinning system operation, it automatically identifies the low-pressure side of the two main oil circuits and connects them, allowing oil from that side to flow out for flushing. The two inlets of shuttle valve 13 are connected via pipelines to the main oil circuits corresponding to output port A and output port B of fin-spinning pump 8.1, respectively. The outlet is connected to the oil-supply relief valve 14.

[0062] The fin hydraulic system is in working condition, and the main pump 8.1 drives the fin actuator to perform reciprocating motion. In the system, the main oil circuit A and the main oil circuit B alternately become the high-pressure side and the low-pressure side. In order to achieve temperature control and oil renewal of the closed circuit, the overflow flushing module starts working. When the main oil circuit on one side is at high pressure and does not reach the set pressure of the fin overflow valve, the fin overflow valve does not conduct and remains closed. Under normal working conditions, the set pressure of the fin 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, 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 fin relief valve 12.1, the high-pressure oil enters the oil inlet of the first fin relief valve 12.1 through points a4 and a3, the first fin relief valve 12.1 is turned on, and part of the high-pressure oil is introduced into the right oil circuit from points a2 and a1 to achieve pressure release. At the same time, the high-pressure side oil enters the shuttle valve 13 from points a4 and a3, pushing the valve core to move to the low-pressure side, thereby identifying and turning on the low-pressure side main oil circuit, that is, a1 and a2 are turned on with 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 through the oil outlet of the shuttle valve 13 and the oil replenishment relief valve 14 in turn to cool down, and finally returns to the oil tank 34 to complete the heat balance management. By flushing the low-pressure side of the fin-turning circuit, the temperature of the oil in the fin-turning circuit can be effectively reduced, solving the problem of high oil temperature in closed hydraulic systems without a flushing circuit and improving equipment reliability.

[0063] During the operation of the hydraulic system, in order to ensure the operating stability and oil cleanliness of the fin pump, the pressure of its main oil circuit needs to be monitored and controlled in real time. To this end, a special pressure monitoring module is set in the main pump system to improve the safety and maintainability of the system operation. Specifically, the pressure monitoring module includes a second pressure measuring joint 29.2, a third pressure measuring joint 29.3, a second pressure gauge 30.2 and a third pressure gauge 30.3. The second pressure measuring joint 29.2 and the third pressure measuring joint 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 measuring joint 29.2, and the third pressure gauge 30.3 is connected to the third pressure measuring joint 29.3, so as to realize the monitoring and display of the pressure of the main oil circuits on both sides of the fin pump 8.1.

[0064] In this application, the short-circuit valve assembly includes a fourth one-way valve 17.1, a fifth one-way valve 17.2, a two-way cartridge valve, and a short-circuit solenoid valve 20. The oil circuits on the A and B sides of the output ports of the rotary fin pump 8.1 are connected to the oil passages of the two-way cartridge valve via the fourth one-way valve 17.1 and the fifth one-way valve 17.2, respectively. The fourth one-way valve 17.1 and the fifth one-way valve 17.2 are used to prevent oil from flowing back from the two-way cartridge valve to port A or port B, respectively, ensuring the unidirectionality of the oil flow, preventing backflow, and conducting positive pressure oil. The two-way cartridge valve includes a two-way cartridge valve spool 18 and a two-way cartridge valve cover plate 19. A spring is provided inside the two-way cartridge valve to maintain a normally closed state when no signal is present. When the short-circuit solenoid valve 20 is de-energized and held in position a, the pressure in the control chamber of the two-way cartridge valve core 18 is relieved, opening the valve core 18 and connecting the two main oil circuits of the fin pump 8.1 with the internal oil passages of the short-circuit valve group, short-circuiting the fin rotation circuit. When the short-circuit solenoid valve 20 is energized, it switches to position b, building up high pressure in the control chamber of the two-way cartridge valve core 18. The two-way cartridge valve core 18 closes under the action of 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 passages on the A side and B side of the output port of the fin pump 8.1 are disconnected, allowing the fin rotation system to operate normally.

[0065] In this application, the zero reset, unlocking, and servo valve assembly integrates the functions of the servo circuit, zero reset, and unlocking circuit, and includes a sixth one-way valve 24, a servo circuit filter 25, a relief valve 26, a zero reset solenoid valve 27, and an unlocking solenoid valve 28. The inlet of the sixth one-way valve 24 is connected to the outlet of the auxiliary pump 22 via 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 assembly via a pipeline to the A2 port of the hydraulic unit, and then connected to the B2 port on the actuator. Furthermore, through the B2 port on the actuator, it is connected to the zero reset pistons on the first and second fin rotating cylinders 35.1 and 35.2 to form a zero reset circuit, realizing the zero reset function.

[0066] The connection path between the sixth check valve 24 and the reset solenoid valve 27 is sequentially provided with a servo circuit filter 25, a relief valve 26, and an unlocking solenoid valve 28. The unlocking solenoid valve 28 is connected via a pipeline from port VI of the reset, unlock, and servo valve assembly to port A1 of the hydraulic unit. This port is then connected to port B1 on the actuator. This port is then connected 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, forming a servo loop. When the fin stabilizer device is in operation and the fins are rotated, the electronic control system controls the output flow of the servo valve 16 based on the fin rotation command, which is amplified 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 angle of the fin pump 8.1 and, accordingly, the output flow of the fin pump 8.1. The hydraulic power output by the fin pump 8.1 drives the actuator, thereby rotating the fins. 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 angle signal is fed back to the servo amplifier via the fin angle transmitter, forming a closed loop for the fin angle position, thereby achieving servo control of the fin movement.

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

[0069] One end of the first pressure measuring joint 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 stabilization system, the hydraulic system completes the zeroing and unlocking of the actuators according to the following control sequence. When the motor starts and the system begins pressurizing, the zeroing solenoid valve 27 is in its default position a (off). Oil then flows sequentially through the auxiliary pump 22, the sixth one-way valve 24, and the zeroing solenoid valve 27, entering the zeroing chambers of the first and second fin cylinders 35.1 and 35.2. The oil pushes the zeroing piston, shifting the stabilizer to zero position and ensuring initial system alignment. The unlocking solenoid valve 28 is now in position a. Subsequently, the unlocking solenoid valve 28 switches to position b (energized), and oil enters the locking cylinder 36, pushing the piston inside the cylinder to overcome the return spring force, unlocking the locking mechanism and releasing the mechanical restraint. Simultaneously, the zeroing solenoid valve 27 switches to position b (energized), closing its internal oil circuit. The oil in the zeroing chamber now drains through the zeroing solenoid valve to the return line, completing the zeroing operation. After the reset and unlocking are completed, the servo system takes over the control, and the servo oil is supplied to the servo valve 16 through the filter 25 to achieve precise position control of the fin system, and the system enters the 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 arranged in the return oil circuit and releases the heat of the return oil through heat exchange with an external cooling medium to control the system temperature. The return oil filter 5 is arranged after the cooler and is used to filter particulate impurities in the return oil to protect the pump, valves and servo components. The cooler and filter form a series cleaning circuit, which improves the stability and life of the hydraulic system.

[0072] In this application, the fuel tank 34 is integrated with a first ball valve 1.1, a second ball valve 1.2, a liquid level gauge 2, a thermometer 3, an air filter 4, an oil return filter 5, and a liquid level control relay. The first ball valve 1.1 is the oil suction port switching valve of the replenishing pump. The second ball valve 1.2 is the oil suction port switching valve of the auxiliary pump. The liquid level gauge 2 is used to observe the oil level in the fuel tank. The thermometer 3 is used to detect the oil temperature in the fuel tank. When the set high temperature value is reached, the alarm is triggered and the equipment is stopped to protect the equipment. The air filter 4 is used to filter impurities and dust in the air entering the fuel tank. The liquid level control relay 7 is used to monitor the oil level in the fuel tank. When the oil level is too low, the alarm is triggered and the equipment is stopped to protect the equipment.

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

[0074]

[0075]

[0076] The present application also provides a control method for an integrated large-scale non-retractable fin stabilizer hydraulic system, the control method comprising:

[0077] Step 1: After the main motor of the hydraulic system is started, the auxiliary pump, fin pump and oil charge pump work synchronously. At this time, the zeroing solenoid valve is in the default power-off state (function a position), and the auxiliary pump provides hydraulic power for the zeroing circuit. The oil flows into the zeroing solenoid valve after passing through the sixth one-way valve and the servo circuit filter, and enters the zeroing chamber of the first fin cylinder and the second fin cylinder, pushing the zeroing piston to move, so that the fin stabilizer is reset to zero position. At the same time, the short-circuit solenoid valve is in the default power-off 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 realize short-circuit unloading.

[0078] The short-circuit solenoid valve is in the power-off state by default, and short-circuit unloading is achieved at both ends of the main oil circuit, ensuring that the main oil circuit is in the unloaded state during the hydraulic system zeroing process, so that the motor starts without load, reducing the starting current and improving the safety and reliability of the zeroing process.

[0079] Step 2: After completing the zeroing action, the control system switches the unlocking solenoid valve to the energized state (function b position), and the hydraulic oil provided by the auxiliary pump enters the zero locking cylinder, pushing the internal piston to overcome the return spring force, so that the telescopic pin retracts, and the locking mechanism is unlocked. 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 is completed.

[0080] Step 3: The hydraulic system enters the fin rotation working condition preparation state, the fin rotation pump continues to run, and keeps synchronization with the auxiliary pump and the oil supply pump. The oil supply pump transports the oil to the low-pressure side of the main oil circuit through the second oil supply line. During the oil supply 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 one-way valve or the second one-way valve and the oil is introduced through the first oil supply line.

[0081] Step 4: In the fin-turning state, the fin stabilizer system monitors the hull roll angular velocity signal in real time through the gyroscope and transmits the detection signal to the central processing unit. The processor analyzes the signal and outputs a control instruction. The servo amplifier amplifies the instruction and drives the servo valve to operate, controlling the variable cylinder to adjust the inclination and direction of the swash plate in the fin pump, changing the flow direction and size of the main pump output, realizing the drive of the fin cylinder in the forward and reverse directions, driving the fin stabilizer to perform active swing, and realizing dynamic anti-roll control. During the operation of the system, 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, part of the high-temperature hydraulic oil is directed through the corresponding fin overflow valve and shuttle valve to the oil replenishment overflow valve and then enters the cooler for cooling and oil return.

[0082] Step 5: When the hydraulic system is in the power-off state, hydraulic power is provided by shaking the hand pump. The hand pump draws oil from the oil tank and outputs it under pressure. The zeroing solenoid valve is still in the default power-off state (function a position). The oil is introduced into the zeroing chamber of the fin cylinder through the zeroing solenoid valve, pushing the zeroing piston to the lowest position. During the resetting process, the fin piston is pushed at the same time to return the fin blade to the zero position. When the resetting is completed, the telescopic pin in the zero locking cylinder automatically springs into the pin hole of the fin handle under the action of the spring force, realizing mechanical locking and completing the resetting and locking process.

[0083] The present invention provides an integrated large-scale non-retractable fin stabilizer hydraulic system and control method, realizing a highly integrated, high-performance, and highly reliable large-scale non-retractable fin stabilizer hydraulic control system. This effectively simplifies the structural layout, improves system response and stability, and enhances control accuracy and safety, making it particularly suitable for space-constrained ship applications.

[0084] The above is only an embodiment of the present application, and common sense such as the specific structure and characteristics of the scheme are not described in detail here. For those skilled in the art, it is obvious that the present application is not limited to the details of the above-mentioned exemplary embodiments, and the present application can be implemented in other specific forms without departing from the spirit or basic characteristics of the present application. Therefore, from any point of view, the embodiments should be regarded as exemplary and non-restrictive, and the scope of the present application is defined by the attached claims rather than the above description, and it is intended that all changes that fall within the meaning and scope of the equivalent elements of the claims are included in the present application. Any figure mark in the claims should not be regarded as limiting the claims involved.

Claims

1. An integrated large-scale non-retractable fin stabilizer hydraulic system, characterized in that: It includes a main pump (8), an electric motor (21), an auxiliary pump (22), a reset unlocking and servo valve group and an oil tank (34); The motor (21) is a double-shaft three-phase asynchronous motor having a first shaft end and a second shaft end, wherein the first shaft end is connected to a fin pump (8.1) in a main pump (8) for providing power to a main circuit of a hydraulic system, and the second shaft end is connected to an auxiliary pump (22) for providing power to a servo, reset and unlock circuit. The main pump (8) is integrated with a fin pump (8.1), an oil replenishment pump (8.2), a filter module, an oil replenishment module, an overflow flushing module and a short-circuit valve group. The fin pump (8.1) is provided with two main oil circuits and has an output port A, an output port B and an oil return port. The output port A and the output port B are respectively connected to a corresponding main oil circuit. The fin pump (8.1) has a two-way pressure supply function for dynamically switching the high-pressure side and the low-pressure side to achieve forward or reverse oil supply control of the fin stabilizer; the oil return port is connected to the oil tank (34), and 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 oil replenishment pump (8.2) is arranged in series at the rear of the fin pump (8.1) and is driven by an electric motor (21). The oil replenishment pump (8.2) is provided with an oil inlet and an oil outlet. The oil inlet is connected to the oil tank (34), and the oil outlet is connected to the closed hydraulic circuit through the filter module and the oil replenishment module. The oil replenishment module comprises a first one-way valve (10.1), a second one-way valve (10.2), a third one-way 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 two main oil circuits of the fin pump (8.1); the first one-way valve (10.1) and the second one-way valve (10.2) are arranged on the first oil replenishment pipeline with their oil inlets facing each other and are connected in series between the two main oil circuits for dynamically identifying and conducting the low-pressure side main oil circuit; the outlet of the oil replenishment pump (8.2) The end is in fluid communication with the connecting pipeline between the first one-way valve (10.1) and the second one-way valve (10.2) through the second oil supply pipeline; an oil return branch line connected to the oil tank (34) is provided in the first oil supply pipeline and between the first one-way valve (10.1) and the second one-way valve (10.2); a third one-way valve (11) and an oil supply relief valve (14) are sequentially arranged in series on the oil return branch line; the third one-way valve (11) is used to control the one-way flow of oil to the oil tank; and the oil supply relief valve (14) is used to limit the oil supply pressure within a set pressure range; The overflow flushing module comprises a first fin-turning overflow valve (12.1), a second fin-turning overflow valve (12.2) and a shuttle valve (13); the first fin-turning overflow valve (12.1) and the second fin-turning overflow valve (12.2) are arranged in parallel, respectively used to control the maximum pressure of the main oil circuits on the output port A and the output port B sides, and their outlets are respectively connected to the main oil circuit on the other side; the shuttle valve (13) has two oil inlets and one oil outlet, the oil inlets are respectively connected to the main oil circuit on the output port A side and the main oil circuit on the output port B side, and the oil outlet is connected to the oil tank (34) via the oil replenishment overflow valve (14) and the cooler, forming a cooling and oil return path for the flushing oil; the shuttle valve (13) has a valve core structure that can be actuated by oil, and is used to automatically identify the side of the two main oil circuits in a low-pressure state when receiving high-pressure oil and conduct it, and guide the corresponding high-temperature low-pressure oil to the oil replenishment overflow valve (14) and then return it to the oil tank (34) after cooling; The reset unlocking and servo valve group comprises a reset solenoid valve (27), which is connected to a reset oil cylinder and is used to control the reset action of the fin stabilizer.

2. The integrated large-scale non-retractable fin stabilizer hydraulic system according to claim 1, characterized in that: The hand pump (23) is also included. The hand pump (23) is provided with an oil inlet and an oil outlet. The oil inlet is connected to the oil tank (34), and the oil outlet is connected to the downstream of the reset solenoid valve (27). The hand pump is used to realize emergency oil supply of the reset circuit when the hydraulic system is out of power or fails.

3. The integrated large-scale non-retractable fin stabilizer hydraulic system according to claim 1, characterized in that: The inlet of the first fin-turning relief valve (12.1) is connected to the oil circuit on the output port A side, and is used 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 fin-turning relief valve (12.2) is connected to the oil circuit on the output port B side, and is used 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.

4. The integrated large-scale non-retractable fin stabilizer hydraulic system according to claim 1, characterized in that: The oil replenishing module further comprises a fourth pressure measuring joint (29.4), a fifth pressure measuring joint (29.5), a fourth pressure gauge (31), a sixth pressure measuring joint (32) and a pressure controller (33); the fourth pressure measuring joint (29.4) and the fifth pressure measuring joint (29.5) are arranged in parallel and are installed on a branch line from the third one-way valve (11) to the first one-way valve (10.1) and the second one-way valve (10.2); the fourth pressure measuring joint (29.4) is connected to the fourth pressure gauge (31), and the fifth pressure measuring joint (29.5) is connected to the pressure controller (33) via the sixth pressure measuring joint (32).

5. The integrated large-scale non-retractable fin stabilizer hydraulic system according to claim 4, characterized in that: The apparatus further comprises a second pressure measuring joint (29.2), a third pressure measuring joint (29.3), a second pressure gauge (30.2) and a third pressure gauge (30.3), wherein the second pressure measuring joint (29.2) and the third pressure measuring joint (29.3) are respectively connected to the main oil circuit on one side of the rotating fin pump (8.1), the second pressure gauge (30.2) is connected to the second pressure measuring joint (29.2), and the third pressure gauge (30.3) is connected to the third pressure measuring joint (29.3), for monitoring and displaying the pressure of the main oil circuits on both sides of the rotating fin pump (8.1).

6. The integrated large-scale non-retractable fin stabilizer hydraulic system according to claim 1, characterized in that: The zero reset, unlock and servo valve group integrates a servo circuit, a zero reset circuit and an unlock circuit.

7. The integrated large-scale non-retractable fin stabilizer hydraulic system according to claim 6, characterized in that: The reset-to-zero unlocking and servo valve group further comprises a sixth one-way valve (24), a servo loop filter (25), a relief valve (26) and an unlocking solenoid valve (28); one side of the sixth one-way valve (24) is connected to the output port of the auxiliary pump (22) through a pipeline, and its downstream is sequentially connected in series with the servo loop filter (25), the relief valve (26) and the unlocking solenoid valve (28), and finally connected in parallel with the reset-to-zero 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 zeroing oil cylinder (35), and the relief valve (26) is arranged in the servo control loop.

8. The integrated large-scale non-retractable fin stabilizer hydraulic system according to claim 1, characterized in that: The main pump (8) further comprises a displacement sensor (15) and a servo valve (16). The servo valve (16) is used to control its output flow rate according to a fin rotation instruction amplified by a servo amplifier of an electronic control system after the fin stabilizer device enters a fin rotation state; 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 fin stabilizer hydraulic system according to claim 1, characterized in that: The oil tank (34) is integrated with a first ball valve (1.1), a second ball valve (1.2), a liquid level gauge (2), a thermometer (3), an air filter (4), an oil return filter (5), and a liquid level control relay (7).

10. A control method for an integrated large-scale non-retractable fin stabilizer hydraulic system according to any one of claims 1 to 9, characterized in that: The control method includes: Step 1: After the main motor of the hydraulic system is started, the auxiliary pump, the fin pump and the charge pump work synchronously. At this time, the zeroing solenoid valve is in the default power-off state. The auxiliary pump provides hydraulic power for the zeroing circuit. The oil flows into the zeroing solenoid valve after passing through the sixth one-way valve and the servo circuit filter, and enters the zeroing chamber of the first fin cylinder and the second fin cylinder, pushing the zeroing piston to move and reset the fin stabilizer to zero position. At the same time, the short-circuit solenoid valve is in the default power-off 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 completing the zero reset action, the control system switches the unlocking solenoid valve to the energized state. The hydraulic oil provided by the auxiliary pump enters the zero lock cylinder, pushing the internal piston to overcome the return spring force, causing the telescopic pin to retract and unlocking the locking mechanism. Subsequently, the zero reset solenoid valve is also switched to the energized state, the short-circuit solenoid valve is energized, and the valve port of the short-circuit valve group is closed. The zero reset process is completed. Step 3: The hydraulic system enters the fin rotation working condition preparation state. The fin rotation pump continues to operate, keeping synchronization with the auxiliary pump and the oil supply pump. The oil supply pump delivers oil to the low-pressure side of the main oil circuit through the second oil supply line. During the oil supply process, the oil is first cleaned by the filter module, and then the first one-way valve or the second one-way valve is used to identify the low-pressure side of the main oil circuit and introduce the oil through the first oil supply line. Step 4: In the fin-turning state, the fin stabilizer system monitors the ship's roll angular velocity signal in real time through the gyroscope and transmits the detection signal to the central processing unit. The processor analyzes the signal and outputs a control instruction. The servo amplifier amplifies the instruction and drives the servo valve to operate, controlling the variable cylinder to adjust the inclination and direction of the swash plate in the fin pump, changing the direction and size of the flow output of the main pump, and realizing the forward and reverse drive of the fin-turning cylinder, driving the fin stabilizer to perform active swing and realize 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 directed through the corresponding fin-turning overflow valve and shuttle valve to the oil replenishment overflow valve and then enters the cooler for cooling and oil return. Step 5: When the hydraulic system is in the power-off state, hydraulic power is provided by shaking the hand pump. The hand pump draws oil from the oil tank and outputs it under pressure. The zeroing solenoid valve is still in the default power-off state. The oil is introduced into the zeroing chamber of the fin cylinder through the zeroing solenoid valve, pushing the zeroing piston to the lowest position. During the resetting process, the fin piston is pushed at the same time to return the fin blade to the zero position. When the resetting is completed, the telescopic pin in the zero locking cylinder automatically springs into the pin hole of the fin handle under the action of the spring force, realizing mechanical locking and completing the resetting and locking process.

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