A large-scale torque loading hydraulic system and method for a passive integrated fin stabilizer
By integrating a hydraulic system with passive and active torque loading functions, the problem of torque loading for large anti-roll fins under different speed conditions was solved, enabling efficient and accurate test verification and reducing costs and energy consumption.
Patent Information
- Application Number
- CN202510981703.5
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-07-16
- Publication Date
- 2026-06-09
Smart Images
Figure CN122170120A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of ship anti-roll fins and hydraulic technology, specifically to a large-scale anti-roll fin active-passive integrated torque loading hydraulic system and method. Background Technology
[0002] Anti-roll fins, as the main device for reducing ship roll, have been widely used in actual ships and can effectively reduce the ship's roll angle when encountering large winds and waves.
[0003] When a stabilizer fin moves in water, it generates lift, drag, and torque loads. The stabilizer fin primarily relies on the lift generated to create a balancing torque on the ship, counteracting the rolling torque to achieve its roll reduction function. The drag generated on the fin is the resistance that the ship must overcome during navigation. The torque acting on the fin is the torque that the stabilizer fin device must overcome during its fin rotation.
[0004] A roll-damping fin mainly consists of a fin, actuator, hydraulic unit, electrical control equipment, fin mount or fin box, etc. The lift, drag, and torque loads generated on the fin are transmitted to the roll-damping fin actuator. When developing new roll-damping fin products, loading tests must be conducted on the actuator. The loads (including lift, drag, and torque loads) that the roll-damping fin experiences during actual ship operation are applied to the roll-damping fin research prototype through simulated loading to verify whether the designed prototype can meet the requirements of actual ship operating conditions in terms of basic functions, load-bearing capacity, and reliability.
[0005] In recent years, with the increasing demand for roll reduction in large ships, anti-roll fins have become larger, with a single fin area exceeding 15 square meters. Furthermore, in addition to the roll reduction requirements under normal speed conditions, ships also have a strong need for roll reduction under zero-speed and low-speed conditions. Therefore, it is necessary to develop full-speed anti-roll fins to meet the roll reduction requirements under both zero-speed and low-speed and normal speed conditions.
[0006] When developing large conventional-speed and large-scale full-speed roll damping fins, the laboratory needs to simulate real-ship loads and apply torque to the fins. However, conventional torque-loading hydraulic systems for roll damping fins can only achieve passive torque loading, failing to accurately obtain the required torque and thus making it impossible to evaluate the fin's response under specific torque. To apply a specific torque to the roll damping fin, active torque loading is required, necessitating the development of a new active torque-loading hydraulic system, increasing testing costs. Furthermore, the passive torque-loading system for large roll damping fins often has a large flow rate, exceeding 1500 L / min, resulting in significant energy consumption. To adapt to the development of large ships, there is an urgent need to develop a hydraulic system capable of meeting the torque loading requirements of large conventional-speed and large-scale full-speed roll damping fins. Summary of the Invention
[0007] To address the shortcomings of the existing technologies, this invention provides a large-scale anti-roll fin integrated active and passive torque loading hydraulic system and method. It can achieve both passive and active torque loading of the anti-roll fin through a single hydraulic unit, reducing testing costs. In addition, it can also meet the torque loading requirements under high flow conditions when passively loading large-scale anti-roll fins.
[0008] To achieve the above objectives, the present invention provides the following technical solution:
[0009] A large-scale anti-roll fin integrated active and passive torque loading hydraulic system, the torque loading hydraulic system comprising a hydraulic unit and two torque loading cylinders;
[0010] The hydraulic unit includes an electric motor, a hydraulic pump, a hydraulic circuit, and an oil tank; the electric motor is connected to the hydraulic pump, the electric motor drives the hydraulic pump to draw oil from the oil tank, and supplies oil to the torque loading cylinder through the hydraulic circuit;
[0011] The hydraulic circuit includes a first manual directional valve, a check valve, a cover-type cartridge relief valve, a cover-type cartridge check valve assembly, a first relief valve, a second manual directional valve, a stacked hydraulically controlled check valve, and a second relief valve; wherein the cover-type cartridge check valve assembly includes a 1# cover-type cartridge check valve, a 2# cover-type cartridge check valve, a 3# cover-type cartridge check valve, and a 4# cover-type cartridge check valve;
[0012] The outlet of the hydraulic pump is connected to the inlet pipe of the first manual directional valve; the first manual directional valve has a functional A position and a functional B position;
[0013] The output port corresponding to position A of the first manual directional valve is connected via the check valve to the inlet pipes of the parallel-connected #1 and #2 cover-type cartridge check valves; the outlets of the #1 and #2 cover-type cartridge check valves are connected to the first and second oil circuits respectively via pipes; the input port of the cover-type cartridge relief valve is connected to the outlet pipes of the parallel-connected #3 and #4 cover-type cartridge check valves, and the inlets of the #3 and #4 cover-type cartridge check valves are respectively connected to the second oil circuit and the first oil circuit via pipes; the output port of the cover-type cartridge relief valve is connected to the input pipe of the first relief valve and intersects with the output side pipe of the check valve; the output port of the first relief valve is connected to the oil tank pipe.
[0014] The input port of the second manual directional valve and the input port of the second relief valve are connected in parallel and connected to the output port pipeline corresponding to the B position of the first manual directional valve; the two output ports of the second manual directional valve are respectively connected to the first oil circuit and the second oil circuit pipeline through the superimposed hydraulic control check valve.
[0015] The return port of the first manual directional valve, the return port of the second manual directional valve, and the output port of the second relief valve are connected in parallel and then connected to the oil tank pipeline.
[0016] The rod chamber of torque loading cylinder #1 and the rodless chamber of torque loading cylinder #2 are connected in parallel and then connected to the first oil circuit; the rodless chamber of torque loading cylinder #1 and the rod chamber of torque loading cylinder #2 are connected in parallel and then connected to the second oil circuit; the torque loading cylinders #1 and #2 drive the loading fin handle of the anti-roll fin to rotate through the extension and retraction of the piston rods.
[0017] Furthermore, the hydraulic circuit also includes a first pressure sensor, a #1 second pressure sensor, and a #2 second pressure sensor;
[0018] The first pressure sensor is installed at the front end of the parallel connection point of the No. 1 cover-type cartridge check valve and the No. 2 cover-type cartridge check valve to monitor the replenishment pressure and feed the replenishment pressure back to the electronic control unit.
[0019] The #1 second pressure sensor and the #2 second pressure sensor are respectively installed on the first oil circuit and the second oil circuit, and are used to monitor the oil pressure in the first oil circuit and the second oil circuit, and to feed the oil pressure back to the electronic control unit.
[0020] Furthermore, the hydraulic circuit also includes a first pressure testing connector group, a first pressure gauge group, a second pressure testing connector, and a second pressure gauge; the first pressure testing connector group includes a first pressure testing connector #1, a first pressure testing connector #2, a first pressure testing connector #3, a first pressure testing connector #4, and a first pressure testing connector #5; the first pressure gauge group includes a first pressure gauge #1, a first pressure gauge #2, a first pressure gauge #3, a first pressure gauge #4, and a first pressure gauge #5.
[0021] The first pressure gauge (1#) is installed on the outlet side of the hydraulic pump via the first pressure testing connector (1#) to monitor the pump outlet pressure. The first pressure gauge (2#) is installed on the front end pipeline of the cover-type cartridge relief valve via the first pressure testing connector (2#) to monitor the passive loading pressure. The first pressure gauge (3#) is installed on the first oil circuit via the first pressure testing connector (3#) to monitor the oil pressure in the first oil circuit. The first pressure gauge (4#) is installed on the second oil circuit via the first pressure testing connector (4#) to monitor the oil pressure in the second oil circuit. The first pressure gauge (5#) is installed on the pipeline at the parallel connection of the second manual directional valve and the second relief valve via the first pressure testing connector (5#) to monitor the active torque loading pressure. The second pressure gauge is installed on the pipeline at the front end of the parallel connection point of the first cover-type cartridge check valve and the second cover-type cartridge check valve via the second pressure testing connector (2#) to monitor the replenishment pressure.
[0022] Furthermore, the hydraulic circuit also includes a first filter; the check valve is connected to the parallel pipelines of the No. 1 cover-type cartridge check valve and the No. 2 cover-type cartridge check valve through the first filter.
[0023] Furthermore, the hydraulic circuit also includes a second filter; the output ports of the first relief valve and the second relief valve are connected in parallel and then connected to the oil tank pipeline through the second filter.
[0024] Furthermore, the hydraulic unit also includes a first cooler and a second cooler;
[0025] The cover-type cartridge overflow valve is connected to the inlet pipe of the first overflow valve via the first cooler; the outlet of the second overflow valve is connected to the oil tank via the second cooler.
[0026] Furthermore, the hydraulic unit also includes a level controller and a level gauge; the level controller and the level gauge are respectively installed on the oil tank; the level controller is used to monitor the oil level in the oil tank and trigger an alarm when the oil level is too low; the level gauge is used to monitor and display the oil level in the oil tank.
[0027] Furthermore, the hydraulic unit also includes an air filter and a thermometer; the air filter and the thermometer are respectively installed on the oil tank; the air filter is used to filter impurities and dust in the air entering the oil tank; the thermometer is used to monitor the oil temperature in the oil tank, and triggers an alarm when the oil temperature reaches a set temperature value.
[0028] This invention also discloses a torque loading test method for a sway damper actuator. The torque loading test method is implemented using the large-scale sway damper active-passive integrated torque loading hydraulic system described in any of the above-mentioned methods. The torque loading test method includes the following steps:
[0029] S1. The piston rods of the two torque loading cylinders are connected to the two ends of the loading fin handle of the anti-roll fin by connecting pins, and the loading fin handle is fixedly connected to the fin shaft of the anti-roll fin.
[0030] S2. Start the electric motor and hydraulic pump, and fill the oil circuit of the entire torque-loaded hydraulic system with oil through the first manual directional valve.
[0031] S3, the first manual directional valve selects the function A position, and the entire torque loading hydraulic system enters the passive torque loading mode; the fin shaft of the anti-roll fin actuator drives the loading fin handle to rotate at a predetermined speed, and the loading fin handle drives the hydraulic unit to passively load the fin shaft through the extension and retraction movement of the piston rod of the torque loading cylinder, and the passive loading pressure is adjusted through the cover plate type cartridge relief valve.
[0032] S4. The first manual directional valve selects the function in position B, and the entire torque loading hydraulic system enters the active torque loading mode; the active loading pressure is set through the second relief valve, and the set pressure of the cover-type cartridge relief valve is greater than the set pressure of the second relief valve.
[0033] S4.1 The oil output from the first manual directional valve is delivered to the second manual directional valve;
[0034] S4.2 When the second manual directional valve is selected for function A, the oil output from the second manual directional valve passes through the superimposed hydraulic control check valve and is actively supplied through the first oil circuit, which is the rod chamber of torque loading cylinder #1 and the rodless chamber of torque loading cylinder #2. The torque loading cylinder drives the loading fin to rotate counterclockwise, actively loading the fin shaft with counterclockwise torque. The oil in the rodless chamber of torque loading cylinder #1 and the rod chamber of torque loading cylinder #2 flows to the second manual directional valve through the second oil circuit and returns through the second manual directional valve.
[0035] S4.3 When the second manual directional valve is selected for function B, the oil output from the second manual directional valve passes through the superimposed hydraulic control check valve and then actively supplies oil to the rodless chamber of torque loading cylinder #1 and the rod chamber of torque loading cylinder #2 through the second oil circuit. The torque loading cylinder drives the loading fin to rotate clockwise, actively loading clockwise torque onto the fin shaft. The oil in the rod chamber of torque loading cylinder #1 and the rodless chamber of torque loading cylinder #2 flows to the second manual directional valve through the first oil circuit and returns through the second manual directional valve.
[0036] S4.4 The oil returned from the first manual directional valve and the second manual directional valve, as well as the excess oil overflowing through the second relief valve, are cooled by the second cooler and filtered by the second filter before returning to the oil tank.
[0037] S4.5 Calculate the active loading torque. Active loading torque = active loading pressure × (area of rod chamber of torque loading cylinder + area of rodless chamber of torque loading cylinder) × radius of loading fin.
[0038] Further, in step S3, the hydraulic unit applies passive torque to the anti-roll fins, including the following steps:
[0039] S3.1 The fin shaft of the anti-roll fin actuator rotates at a predetermined speed, and the fin shaft drives the loading fin handle to rotate. The piston rods of the #1 torque loading cylinder and the #2 torque loading cylinder move in extension and retraction under the drive of the loading fin handle.
[0040] When the fin shaft drives the loading fin handle to rotate clockwise, the oil in the rod chamber of the #1 torque loading cylinder and the rodless chamber of the #2 torque loading cylinder enters the first oil circuit of the hydraulic unit, and is then transported to the cover plate type cartridge relief valve through the #4 cover plate type cartridge check valve.
[0041] When the fin shaft rotates counterclockwise, the oil in the rodless chamber of the #1 torque loading cylinder and the rod chamber of the #2 torque loading cylinder enters the second oil circuit of the hydraulic unit, and is then transported to the cover plate type cartridge relief valve through the #3 cover plate type cartridge check valve.
[0042] When the oil pressure at the front end of the cover-type cartridge relief valve, i.e. the passive loading pressure, does not exceed the set pressure of the cover-type cartridge relief valve, the oil stops flowing and enters a pressure-stagnant state, causing the fin shaft to be passively loaded; when the oil pressure at the front end of the cover-type cartridge relief valve reaches the set pressure of the cover-type cartridge relief valve, the cover-type cartridge relief valve begins to overflow.
[0043] S3.2 When the cover-type cartridge relief valve starts to overflow; the overflowing oil is cooled by the first cooler and then merges with the oil that flows through the first manual reversing valve, the check valve and the first filter in sequence, and flows together to the front end of the parallel connection point of the 1# cover-type cartridge check valve and the 2# cover-type cartridge check valve.
[0044] When the fin shaft rotates clockwise, the first oil circuit contains high-pressure oil and the second oil circuit contains low-pressure oil. The collected oil is replenished to the low-pressure side of the second oil circuit through the No. 2 cover plate type cartridge check valve. The oil then flows through the second oil circuit to the rodless chamber of the No. 1 torque loading cylinder and the rod chamber of the No. 2 torque loading cylinder to apply passive torque to the fin shaft.
[0045] When the fin shaft rotates counterclockwise, the first oil circuit contains low-pressure oil and the second oil circuit contains high-pressure oil. The oil is replenished to the first oil circuit on the low-pressure side through the No. 1 cover plate type cartridge check valve. The oil flows from the first oil circuit to the rod chamber of the No. 1 torque loading cylinder and the rodless chamber of the No. 2 torque loading cylinder to passively load the fin shaft with torque.
[0046] S3.3 Calculate the passive loading torque;
[0047] Passive loading torque = passive loading pressure × (area of rod chamber of torque loading cylinder + area of rodless chamber of torque loading cylinder) × radius of loading fin.
[0048] The beneficial effects of this invention are:
[0049] The large-scale anti-roll fin integrated active and passive torque loading hydraulic system and method provided by this invention integrates passive torque loading and active torque loading into a single hydraulic system. This allows for active and passive torque loading tests on the anti-roll fin during the land-based test bench phase using a single loading hydraulic system. This facilitates the verification of the basic functions and reliability of the anti-roll fin and avoids test deviations caused by different loading hydraulic systems, improving the reliability and efficiency of verification. It also increases the utilization efficiency of hydraulic components and the hydraulic system, and reduces the development cost of the loading hydraulic system.
[0050] The hydraulic unit of the present invention increases the oil flow rate by adopting a cover-type cartridge check valve and a cover-type cartridge relief valve, which meets the high flow rate conditions that occur during the passive torque loading test of large conventional speed anti-roll fins and large full speed anti-roll fins, and can realize the loading of large conventional speed anti-roll fins and large full speed anti-roll fins. Attached Figure Description
[0051] Figure 1 This is a schematic diagram of the large-scale anti-roll fin integrated active and passive torque loading hydraulic system of the present invention;
[0052] Figure 2 This is a schematic diagram of the anti-roll fin torque loading mechanism of the present invention;
[0053] Figure 3 This is a schematic diagram of the passive torque loading hydraulic mechanism of the present invention;
[0054] Figure 4 This is a schematic diagram of the active torque loading hydraulic mechanism of the present invention.
[0055] The components are as follows: 1-Electric motor, 2-Hydraulic pump, 3-First manual directional valve, 4-Check valve, 5-First filter, 6-Cover-type cartridge relief valve, 7-Cover-type cartridge check valve assembly, 7.1-1# Cover-type cartridge check valve, 7.2-2# Cover-type cartridge check valve, 7.3-3# Cover-type cartridge check valve, 7.4-4# Cover-type cartridge check valve, 8-First cooler, 9-First relief valve, 10-Second filter, 11-Second manual directional valve, 12-Stacked hydraulic check valve, 13-Second relief valve, 14-Second cooler, 15-First pressure test connector assembly, 15.1-1# First pressure test connector, 15.2-2# First pressure test connector, 15.3-3# First... Pressure testing connector, 15.4-4# first pressure testing connector, 15.5-5# first pressure testing connector, 16-first pressure gauge group, 16.1-1# first pressure gauge, 16.2-2# first pressure gauge, 16.3-3# first pressure gauge, 16.4-4# first pressure gauge, 16.5-5# first pressure gauge, 17-first pressure sensor, 18-second pressure testing connector, 19-second pressure gauge, 20-second pressure sensor group, 20.1-1# second pressure sensor, 20.2-2# second pressure sensor, 21-level controller, 22-level gauge, 23-air filter, 24-thermometer, 25-torque loading cylinder, 26-loading fin handle, 27-fin shaft. Detailed Implementation
[0056] The specific embodiments of the present invention will be further described in detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and are not intended to limit the scope of the invention.
[0057] The terms used in this application, such as top, bottom, left, right, inside, outside, front end, rear end, head, and tail, are based on the orientations or positional relationships shown in the accompanying drawings. Different drawings may result in different positional relationships, therefore they should not be construed as limiting the scope of protection.
[0058] In this invention, 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. Furthermore, they can refer to the internal connection of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of these terms in this invention based on the specific circumstances.
[0059] This embodiment describes a large-scale anti-roll fin integrated active and passive torque loading hydraulic system and method, which integrates a passive torque loading hydraulic system and an active torque loading hydraulic system into one hydraulic system. It can use one hydraulic system to conduct active and passive loading tests on the anti-roll fin, avoiding the use of different hydraulic systems for torque loading and improving the accuracy of the anti-roll fin torque test.
[0060] like Figure 1 As shown, the torque-loading hydraulic system includes a hydraulic press unit that integrates a passive torque-loading hydraulic mechanism and an active torque-loading hydraulic mechanism, and two torque-loading cylinders 25. The hydraulic press unit is connected to the loading fin 26 via the two torque-loading cylinders 25. The hydraulic press unit has four connection ports, of which ports X1 and X2 are used to connect to the torque-loading cylinders 25. The oil passage connected to port X1 is designated as the first oil passage, and the oil passage connected to port X2 is designated as the second oil passage. Ports X3 and X4 are used to connect to the first cooler 8 in the hydraulic press unit.
[0061] The hydraulic unit in this embodiment includes an electric motor 1, a hydraulic pump 2, a hydraulic oil circuit, a first cooler 8, a second cooler 14, a level controller 21, a level gauge 22, an air filter 23, a thermometer 24, and an oil tank.
[0062] Electric motor 1 is connected to hydraulic pump 2, forming the power source for the torque loading hydraulic system. The inlet of hydraulic pump 2 is connected to an oil tank. Driven by electric motor 1, hydraulic pump 2 pumps oil from the tank and supplies oil to torque loading cylinder 25 via the hydraulic circuit. Preferably, the oil used in the torque loading test in this embodiment is hydraulic oil, and electric motor 1 is a low-power motor, such as a 5.5kW motor. A first pressure test connector 15.1 and a first pressure gauge 16.1 are installed at the outlet of hydraulic pump 2 to monitor the pump outlet pressure of hydraulic pump 2, and on-site observation is achieved through the display of the first pressure gauge 16.1.
[0063] The hydraulic circuit includes a first manual directional valve 3, a check valve 4, a first filter 5, a cover-type cartridge relief valve 6, a cover-type cartridge check valve group 7, a first relief valve 9, a second filter 10, a second manual directional valve 11, a stacked hydraulic control check valve 12, a second relief valve 13, a first pressure test connector group 15, a first pressure gauge group 16, a first pressure sensor 17, a second pressure test connector 18, a second pressure gauge 19, and a second pressure sensor group 20.
[0064] The outlet of hydraulic pump 2 is connected to the inlet pipe of the first manual directional valve 3. The first manual directional valve 3 is used to switch between the active torque loading hydraulic mechanism and the passive torque loading hydraulic mechanism. The first manual directional valve 3 has a function A position and a function B position. When the first manual directional valve 3 is switched to function A position, the torque loading hydraulic system is in passive torque loading mode, and the first manual directional valve 3 is connected to the passive torque loading oil circuit. When the first manual directional valve 3 is switched to function B position, the torque loading hydraulic system is in active torque loading mode, and the first manual directional valve 3 is connected to the active torque loading oil circuit. Specifically:
[0065] The output port corresponding to position A of the first manual directional valve 3 is connected to the input port of the first filter 5 via a check valve 4. The first filter 5 is used to prevent impurities from entering the passive torque loading hydraulic circuit. The inlets of the #1 cover-type cartridge check valve 7.1 and the #2 cover-type cartridge check valve 7.2 are connected in parallel to point J1 via pipelines, and the output port of the first filter 5 is connected to the pipeline at point J1. The outlets of the #1 cover-type cartridge check valve 7.1 and the #2 cover-type cartridge check valve 7.2 are respectively connected to the first and second oil circuits, namely ports X1 and X2.
[0066] A first pressure sensor 17, a second pressure test connector 18, and a second pressure gauge 19 are installed on the oil line at point J2, which is upstream of point J1. The first pressure sensor 17 is used to monitor the replenishing oil pressure of the passive torque loading hydraulic mechanism and feed the replenishing oil pressure back to the electronic control unit. The second pressure gauge 19 monitors and displays the replenishing oil pressure of the passive torque loading hydraulic mechanism through the second pressure test connector 18, which facilitates on-site observation of the replenishing oil pressure.
[0067] The inlets of the #3 and #4 cover-type cartridge check valves 7.3 and 7.4 are respectively connected via pipelines to the second and first oil circuits, located at ports X2 and X1 of the torque loading cylinder 25. The outlets of both valves 7.3 and 7.4 are connected in parallel via pipelines to point J3, which is connected to the inlet pipeline of the cover-type cartridge relief valve 6. The connection point between the #3 and #4 cover-type cartridge check valves 7.3 and the second oil circuit is designated as point J4, and the connection point between the #4 and #5 cover-type cartridge check valves 7.4 and the first oil circuit is designated as point J5. A #2 pressure test connector 15.2 and a #2 first pressure gauge 16.2 are installed on the pipeline upstream of the cover-type cartridge relief valve 6 to monitor the passive loading pressure. The passive loading pressure is regulated by the cover-type cartridge relief valve 6.
[0068] In this embodiment, the 1#, 2#, 3#, and 4# cover-type cartridge check valves (7.1, 7.2, 7.3, and 7.4) mainly consist of a valve core insert and a directional control cover plate. Their function is to achieve unidirectional delivery, meaning the oil can only be delivered in one direction, and the flow is stopped in the opposite direction. Cover-type cartridge check valves are suitable for high-flow-rate applications; for example, a cover-type cartridge check valve with a nominal diameter of 80mm can achieve a maximum flow rate of 4000L / min.
[0069] The output port of the cover-type cartridge relief valve 6 is connected to the input port of the first cooler 8 via the X3 port of the hydraulic circuit. The output port of the first cooler 8 is connected to the input port of the first relief valve 9 via the X4 port of the hydraulic circuit, and this pipeline intersects with the pipeline on the output side of the first filter 5 at point J6. The output port of the first relief valve 9 is connected to the oil tank pipeline via the second filter 10. When the oil pressure after cooling by the first cooler 8 is lower than the set pressure of the first relief valve 9, the first relief valve 9 is in the closed state, and the oil at point J6 can flow together with the oil output from the first filter 5 to either the #1 cover-type cartridge check valve 7.1 or the #2 cover-type cartridge check valve 7.2 to replenish the torque-loaded cylinder 25. When the oil pressure after cooling by the first cooler 8 is not lower than the set pressure of the first relief valve 9, the first relief valve 9 opens, and the oil flows through the first relief valve 9 and the second filter 10 in sequence before returning to the oil tank. The second filter 10 can prevent impurities from entering the oil tank.
[0070] In this embodiment, the cover-type cartridge relief valve 6 mainly consists of a valve core insert and a pressure control cover plate. The opening and closing of the valve core insert is adjusted by a pilot relief valve within the pressure control cover plate, thereby controlling the pressure of the main oil circuit. When the pressure control cover plate uses a mechanically adjustable pressure control valve, the loading pressure can be manually adjusted. When the pressure control cover plate uses an electro-proportional control pressure control valve, the loading pressure can be electrically adjusted. The cover-type cartridge relief valve 6 is suitable for high-flow-rate applications. For example, a cover-type cartridge relief valve with a nominal diameter of 80mm and a valve port pressure drop of 5 bar results in a flow rate of 4600 L / min.
[0071] In this embodiment, a first pressure sensor 20.1 (#1), a first pressure testing connector 15.3 (#3), and a first pressure gauge 16.3 (#3) are installed in the first oil circuit to monitor the oil pressure within the first oil circuit, i.e., the oil pressure flowing through port X1. The first pressure sensor 20.1 (#1) feeds back the oil pressure of the first oil circuit to the electronic control unit. Similarly, a first pressure sensor 20.2 (#2), a first pressure testing connector 15.4 (#4), and a first pressure gauge 16.4 (#4) are installed in the second oil circuit to monitor the oil pressure within the second oil circuit, i.e., the oil pressure flowing through port X2. The first pressure sensor 20.2 (#2) feeds back the oil pressure of the second oil circuit to the electronic control unit.
[0072] The input port of the second manual directional valve 11 and the input port of the second relief valve 13 are connected in parallel and connected to the output port pipeline corresponding to the functional position B of the first manual directional valve 3. The intersection point of the parallel pipelines is point J7. A #5 first pressure test connector 15.5 and a #5 first pressure gauge 16.5 are also installed at point J7 for monitoring the active torque loading pressure. In this embodiment, the active loading pressure is adjusted and set by the second relief valve 13, and during the active torque loading test, the set pressure of the cover-type cartridge relief valve 6 is greater than the set pressure of the second relief valve 13.
[0073] The second manual directional valve 11 has a functional position A and a functional position B. The output ports corresponding to functional positions A and B are respectively connected to the end pipelines of the first oil circuit and the second oil circuit through a superimposed hydraulic control check valve 12. The second manual directional valve 11 selects to supply oil to the first oil circuit or the second oil circuit by switching between functional positions A and B. The return port of the first manual directional valve 3, the return port of the second manual directional valve 11, and the output port of the second relief valve 13 are connected in parallel to the input pipeline of the second cooler 14. The output port of the second cooler 14 is connected to the input pipeline of the second filter 10. Excess oil is filtered by the second filter 10 and returned to the oil tank.
[0074] The level controller 21, level gauge 22, air filter 23, and thermometer 24 are integrated into the oil tank. The level controller 21 monitors the oil level in the tank and triggers an alarm when the oil level is too low, stopping the torque-loaded hydraulic system to protect the entire system. The level gauge 22 monitors and displays the oil level in the tank, allowing on-site personnel to observe the oil level in real time. The air filter 23 filters impurities and dust from the air entering the oil tank. The thermometer 24 monitors and displays the oil temperature in the tank; when the set maximum or minimum temperature value is reached, it triggers an alarm, stopping the torque-loaded hydraulic system to protect the entire system.
[0075] Two torque-loading cylinders 25 cooperate with the hydraulic press unit to achieve torque loading for the anti-roll fins. The hydraulic press unit is connected to the two torque-loading cylinders 25 through ports X1 and X2. Specifically, port Y2 of torque-loading cylinder 1 (i.e., the rodless chamber port of torque-loading cylinder 25.1) and port Y3 of torque-loading cylinder 25.2 (i.e., the rod chamber port of torque-loading cylinder 25.2) are connected in parallel to point J8 through pipelines, and then connected to port X2 of the hydraulic press unit through pipelines. Port Y1 of torque-loading cylinder 1 (i.e., the rod chamber port of torque-loading cylinder 25.1) and port Y4 of torque-loading cylinder 25.2 (i.e., the rodless chamber port of torque-loading cylinder 25.2) are connected in parallel to point J9 through pipelines, and then connected to port X1 of the hydraulic press unit through pipelines.
[0076] In this embodiment, the pressure testing connector and pressure gauge are used in combination. The pressure testing end of the pressure testing connector is placed in the pipeline, and the pressure gauge is installed at the top of the pressure testing connector. The pressure gauge detects the oil pressure through the pressure testing connector.
[0077] The torque-loading hydraulic system of this embodiment performs the following loading test when applying torque to the anti-roll fin actuator:
[0078] 1. The piston rods of the two torque loading cylinders 25 are connected to the left and right ends of the loading fin handle 26 fixed on the fin shaft 27 by connecting pins respectively;
[0079] like Figure 2 As shown, the fin shaft 27 of the actuator at the center of the loading fin 26 is connected to the loading fin 26 by a key. Torque loading cylinders 25.1 and 25.2 are symmetrically arranged on both sides of the fin shaft 27 and are mounted on the support by hinges. The left and right ends of the loading fin 26 are connected to the piston rods of the torque loading cylinders 25.1 and 25.2 by connecting pins, respectively.
[0080] 2. Start the motor 1 and hydraulic pump 2 to deliver oil to the first manual directional valve 3. The first manual directional valve 3 switches between function A and function B to allow oil to flow into the passive torque loading oil circuit and the active torque loading oil circuit until the entire torque loading hydraulic system is filled with oil.
[0081] 3. When passively applying torque to the anti-roll fins, the first manual directional valve 3 is selected to function A, and the entire torque-loading hydraulic system enters the passive torque-loading mode. The passive loading pressure is adjusted through the cover-type cartridge relief valve 6. Figure 3 As shown;
[0082] 3.1 The fin shaft 27 of the anti-roll fin actuator rotates at a predetermined speed. The fin shaft 27 drives the loading fin handle 26 to rotate to realize the fin rotation action. The piston rods of torque loading cylinder 25.1 and torque loading cylinder 25.2 of No.1 torque loading cylinder 25.2 perform telescopic movement under the drive of loading fin handle 26.
[0083] When the fin shaft 27 drives the loading fin handle 26 to rotate clockwise, the oil in the rod chamber of torque loading cylinder 1# 25.1 and the rodless chamber of torque loading cylinder 25.2 25.2 flows out through ports Y1 and Y4 respectively, and converges at point J9, entering the first oil circuit of the hydraulic unit together. The oil is then transported to point J3 through the cover-type cartridge check valve 7.4, and then flows to the cover-type cartridge relief valve 6. At this time, the oil can flow from point J5 to point J3, but cannot flow from point J3 to point J4.
[0084] When the fin shaft 27 rotates counterclockwise, the oil in the rodless chamber of torque loading cylinder 25.1 (No. 1) and the rod chamber of torque loading cylinder 25.2 (No. 2) flows out through ports Y2 and Y3 respectively, and converges at point J8, entering the second oil circuit of the hydraulic unit together. The oil is then transported to point J3 through the cover-type cartridge check valve 7.3 (No. 3) and flows to the cover-type cartridge relief valve 6. At this time, the oil can flow from point J4 to point J3, but cannot flow from point J3 to point J5.
[0085] At this point, the oil in the oil circuit between point J3 and the cover-type cartridge relief valve 6 is high-pressure oil. When the high-pressure oil pressure does not exceed the set pressure of the cover-type cartridge relief valve 6, the oil stops flowing and enters a pressure-stagnant state, generating resistance to the piston movement of the torque loading cylinder 25, causing the fin shaft 27 to be passively loaded. At this time, the oil pressure in the oil circuit between point J3 and the cover-type cartridge relief valve 6, monitored in real time by the first pressure gauge 16.2 (#2), is the passive loading pressure. When the passive loading pressure reaches the set pressure of the cover-type cartridge relief valve 6, the cover-type cartridge relief valve 6 begins to overflow.
[0086] 3.2 When the cover-type cartridge overflow valve 6 starts to overflow; the overflowed oil flows through port X3 to the first cooler 8 for heat exchange and cooling. The cooled oil flows through port X4 back to point J6, that is, back to the outlet side of the first filter 5, and merges with the oil that flows through the first manual reversing valve 3, check valve 4 and first filter 5 in sequence. Then it flows to point J1, that is, the front end of the parallel connection point of cover-type cartridge check valve 7.1 and cover-type cartridge check valve 7.2.
[0087] When the fin shaft 27 rotates clockwise, the first oil circuit contains high-pressure oil, and the second oil circuit contains low-pressure oil. The oil flowing to point J1 is replenished to the low-pressure side of the second oil circuit via the #2 cover-type cartridge check valve 7.2. The oil flows from the second oil circuit to the rodless chamber of the #1 torque loading cylinder 25.1 and the rod chamber of the #2 torque loading cylinder 25.2, applying passive torque loading to the fin shaft 27.
[0088] When the fin shaft 27 rotates counterclockwise, the first oil circuit contains low-pressure oil, and the second oil circuit contains high-pressure oil. The oil flowing to point J1 is replenished to the low-pressure side of the first oil circuit via the #1 cover-type cartridge check valve 7.1. The oil flows from the first oil circuit to the rod chamber of the #1 torque loading cylinder 25.1 and the rodless chamber of the #2 torque loading cylinder 25.2, applying passive torque to the fin shaft 27.
[0089] In this embodiment, the replenishment pressure is regulated by the first overflow valve 9, and the replenishment pressure is generally less than 1.4 MPa.
[0090] During the passive torque loading test, the electronic control unit can display the real-time oil pressure of the first and second oil circuits monitored by the #1 second pressure sensor 20.1 and the #2 second pressure sensor 20.2. During the oil replenishment process, the first pressure sensor 17 monitors the replenishment pressure in real time, feeds it back to the electronic control unit, and displays it.
[0091] 3.3. Through the above steps, achieve passive torque loading when the anti-roll fin actuator is actively operating, and calculate the passive loading torque;
[0092] Passive loading torque = passive loading pressure × (area of rod chamber of torque loading cylinder 25 + area of rodless chamber of torque loading cylinder 25) × radius of loading fin 26.
[0093] 4. When actively applying torque to the anti-roll fins, the first manual directional valve 3 is selected to function B, and the entire torque-loading hydraulic system enters the active torque-loading mode, such as... Figure 4 As shown, the active loading pressure is set by the second relief valve 13, and during the active torque loading test, the set pressure of the cover-type cartridge relief valve 6 is greater than the set pressure of the second relief valve 13.
[0094] 4.1 The oil output from the first manual directional valve 3 is delivered to the second manual directional valve 11 after passing through point J7;
[0095] 4.2 When the second manual directional valve 11 is selected for function A, the oil output from the second manual directional valve 11 flows into the first oil circuit after passing through the superimposed hydraulic control check valve 12. After passing through port X1, it actively supplies oil to the rod chamber of torque loading cylinder 25.1 and the rodless chamber of torque loading cylinder 25.2. The torque loading cylinder 25 drives the loading fin 26 to rotate counterclockwise, realizing the active loading of counterclockwise torque on the fin shaft 27. The oil in the rodless chamber of torque loading cylinder 25.1 and the rod chamber of torque loading cylinder 25.2 flows to the second manual directional valve 11 through the second oil circuit, and enters the return oil circuit through the return port of the second manual directional valve 11.
[0096] 4.3 When the second manual directional valve 11 is selected for function B, the oil output from the second manual directional valve 11 flows into the second oil circuit after passing through the superimposed hydraulic control check valve 12. After passing through port X2, it actively supplies oil to the rodless chamber of torque loading cylinder 25.1 and the rod chamber of torque loading cylinder 25.2. The torque loading cylinder 25 drives the loading fin handle 26 to rotate clockwise, realizing the clockwise torque active loading on the fin shaft 27. The oil in the rod chamber of torque loading cylinder 25.1 and the rodless chamber of torque loading cylinder 25.2 flows to the second manual directional valve 11 through the first oil circuit, and enters the return oil circuit through the return port of the second manual directional valve 11.
[0097] 4.4 The oil returned by the first manual reversing valve 3 and the second manual reversing valve 11, as well as the excess oil overflowing through the second overflow valve 13, are cooled by heat exchange in the second cooler 14 and filtered by the second filter 10 before returning to the oil tank.
[0098] 4.5. The active torque loading of the anti-roll fin actuator is achieved through the above active torque loading steps, and the active loading torque is calculated;
[0099] Active loading torque = Active loading pressure × (Area of rod chamber of torque loading cylinder 25 + Area of rodless chamber of torque loading cylinder 25) × Radius of loading fin 26.
[0100] Although the principles of the present invention have been described in detail above with reference to preferred embodiments, those skilled in the art should understand that the above embodiments are merely illustrative explanations of the implementation of the present invention and are not intended to limit the scope of the present invention. The details in the embodiments do not constitute a limitation on the scope of the present invention. Any obvious changes, such as equivalent transformations or simple substitutions, based on the technical solutions of the present invention without departing from the spirit and scope of the present invention fall within the protection scope of the present invention.
Claims
1. A large-scale anti-roll fin integrated active and passive torque-loading hydraulic system, characterized in that, The torque loading hydraulic system includes a hydraulic unit and two torque loading cylinders (25); The hydraulic unit includes an electric motor (1), a hydraulic pump (2), a hydraulic oil circuit, and an oil tank; the electric motor (1) is connected to the hydraulic pump (2), the electric motor (1) drives the hydraulic pump (2) to draw oil from the oil tank, and supplies oil to the torque loading cylinder (25) through the hydraulic oil circuit; The hydraulic circuit includes a first manual directional valve (3), a check valve (4), a cover-type cartridge relief valve (6), a cover-type cartridge check valve assembly (7), a first relief valve (9), a second manual directional valve (11), a stacked hydraulic control check valve (12), and a second relief valve (13); wherein the cover-type cartridge check valve assembly (7) includes a 1# cover-type cartridge check valve (7.1), a 2# cover-type cartridge check valve (7.2), a 3# cover-type cartridge check valve (7.3), and a 4# cover-type cartridge check valve (7.4); The outlet of the hydraulic pump (2) is connected to the inlet pipe of the first manual directional valve (3); the first manual directional valve (3) has a functional A position and a functional B position; The output port corresponding to the functional position A of the first manual directional valve (3) is connected to the inlet pipes of the parallel-connected 1# cover-type cartridge check valve (7.1) and 2# cover-type cartridge check valve (7.2) via the check valve (4); the outlets of the 1# cover-type cartridge check valve (7.1) and 2# cover-type cartridge check valve (7.2) are connected to the first oil circuit and the second oil circuit respectively via pipes; the input port of the cover-type cartridge relief valve (6) is connected to the parallel-connected 3# cover-type cartridge check valve. The outlet pipes of valve (7.3) and the 4# cover-type cartridge check valve (7.4) are connected. The inlet pipes of the 3# cover-type cartridge check valve (7.3) and the 4# cover-type cartridge check valve (7.4) are respectively connected to the second oil circuit and the first oil circuit. The output port of the cover-type cartridge relief valve (6) is connected to the input port pipe of the first relief valve (9) and intersects with the output side pipe of the check valve (4). The output port of the first relief valve (9) is connected to the oil tank pipe. The input port of the second manual directional valve (11) and the input port of the second relief valve (13) are connected in parallel and connected to the output port pipeline corresponding to the function B position of the first manual directional valve (3); the two output ports of the second manual directional valve (11) are respectively connected to the first oil circuit and the second oil circuit pipeline through the superimposed hydraulic control check valve (12); The oil return port of the first manual reversing valve (3), the oil return port of the second manual reversing valve (11), and the output port of the second overflow valve (13) are connected in parallel to the oil tank pipeline; The rod chamber of torque loading cylinder 1 (25.1) and the rodless chamber of torque loading cylinder 2 (25.2) are connected in parallel and then connected to the first oil circuit; the rodless chamber of torque loading cylinder 1 (25.1) and the rod chamber of torque loading cylinder 2 (25.2) are connected in parallel and then connected to the second oil circuit; the torque loading cylinder 1 (25.1) and the torque loading cylinder 2 (25.2) drive the loading fin handle (26) of the anti-roll fin to rotate through the extension and retraction movement of the piston rod.
2. The large-scale anti-roll fin integrated active and passive torque-loading hydraulic system according to claim 1, characterized in that, The hydraulic circuit also includes a first pressure sensor (17), a first second pressure sensor (20.1), and a second second pressure sensor (20.2). The first pressure sensor (17) is installed at the front end of the parallel connection point of the No. 1 cover-type cartridge check valve (7.1) and the No. 2 cover-type cartridge check valve (7.2) to monitor the replenishment pressure and feed the replenishment pressure back to the electronic control unit; The #1 second pressure sensor (20.1) and the #2 second pressure sensor (20.2) are respectively installed on the first oil circuit and the second oil circuit, and are used to monitor the oil pressure in the first oil circuit and the second oil circuit, and to feed the oil pressure back to the electronic control unit.
3. The large-scale anti-roll fin integrated active and passive torque-loading hydraulic system according to claim 1, characterized in that, The hydraulic circuit further includes a first pressure testing connector group (15), a first pressure gauge group (16), a second pressure testing connector (18), and a second pressure gauge (19); the first pressure testing connector group (15) includes a first pressure testing connector 1# (15.1), a first pressure testing connector 2# (15.2), a first pressure testing connector 3# (15.3), a first pressure testing connector 4# (15.4), and a first pressure testing connector 5# (15.5); the first pressure gauge group (16) includes a first pressure gauge 1# (16.1), a first pressure gauge 2# (16.2), a first pressure gauge 3# (16.3), a first pressure gauge 4# (16.4), and a first pressure gauge 5# (16.5); The first pressure gauge (16.1) is installed on the outlet side of the hydraulic pump (2) via the first pressure test connector (15.1) to monitor the pump outlet pressure of the hydraulic pump (2); the first pressure gauge (16.2) is installed on the front end pipeline of the cover-type cartridge relief valve (6) via the first pressure test connector (15.2) to monitor the passive loading pressure; the first pressure gauge (16.3) is installed on the first oil circuit via the first pressure test connector (15.3) to monitor the oil pressure in the first oil circuit; the first pressure gauge (16.4)... The first pressure test connector (15.4) is installed in the second oil circuit to monitor the oil pressure in the second oil circuit; the first pressure gauge (16.5) is installed in the pipeline at the parallel connection of the second manual directional valve (11) and the second relief valve (13) through the first pressure test connector (15.5) to monitor the active torque loading pressure; the second pressure gauge (19) is installed in the pipeline at the front end of the parallel connection of the first cover-type cartridge check valve (7.1) and the second cover-type cartridge check valve (7.2) through the second pressure test connector (18) to monitor the replenishment pressure.
4. The large-scale anti-roll fin integrated active and passive torque-loading hydraulic system according to claim 1, characterized in that, The hydraulic circuit also includes a first filter (5); the check valve (4) is connected to the parallel pipelines of the 1# cover plate cartridge check valve (7.1) and the 2# cover plate cartridge check valve (7.2) through the first filter (5).
5. The large-scale anti-roll fin integrated active and passive torque-loading hydraulic system according to claim 1, characterized in that, The hydraulic circuit also includes a second filter (10); the output port of the first relief valve (9) and the output port of the second relief valve (13) are connected in parallel and then connected to the oil tank pipeline through the second filter (10).
6. The large-scale anti-roll fin integrated active and passive torque-loading hydraulic system according to claim 1, characterized in that, The hydraulic unit also includes a first cooler (8) and a second cooler (14); The cover-type cartridge overflow valve (6) is connected to the inlet pipe of the first overflow valve (9) via the first cooler (8); the outlet of the second overflow valve (13) is connected to the oil tank via the second cooler (14).
7. The large-scale anti-roll fin integrated active and passive torque-loading hydraulic system according to claim 1, characterized in that, The hydraulic unit also includes a level controller (21) and a level gauge (22); the level controller (21) and the level gauge (22) are respectively installed on the oil tank; the level controller (21) is used to monitor the oil level in the oil tank and trigger an alarm when the oil level is too low; the level gauge (22) is used to monitor and display the oil level in the oil tank.
8. The large-scale anti-roll fin integrated active and passive torque-loading hydraulic system according to claim 1, characterized in that, The hydraulic unit also includes an air filter (23) and a thermometer (24); the air filter (23) and the thermometer (24) are respectively installed on the oil tank; the air filter (23) is used to filter impurities and dust in the air entering the oil tank; the thermometer (24) is used to monitor the oil temperature in the oil tank, and triggers an alarm when the oil temperature reaches the set temperature value.
9. A torque loading test method for a rock-damping fin actuator, characterized in that, The torque loading test method is implemented using the large-scale anti-roll fin active-passive integrated torque loading hydraulic system as described in any one of claims 1 to 8, and the torque loading test method includes the following steps: S1. The piston rods of the two torque loading cylinders (25) are connected to the two ends of the loading fin handle (26) of the anti-roll fin by connecting pins, and the loading fin handle (26) is fixedly connected to the fin shaft (27) of the anti-roll fin. S2. Start the electric motor (1) and hydraulic pump (2), and fill the oil circuit of the entire torque loading hydraulic system with oil through the first manual directional valve (3); S3, the first manual directional valve (3) selects function A position, and the entire torque loading hydraulic system enters the passive torque loading mode; the fin shaft (27) of the anti-roll fin actuator drives the loading fin handle (26) to rotate at a predetermined speed, and the loading fin handle (26) drives the hydraulic unit to passively load the fin shaft (27) through the extension and retraction movement of the piston rod of the torque loading cylinder (25), and adjusts the passive loading pressure through the cover plate type cartridge relief valve (6); S4. The first manual directional valve (3) selects the function B position, and the entire torque loading hydraulic system enters the active torque loading mode; the active loading pressure is set by the second relief valve (13), and the set pressure of the cover-type cartridge relief valve (6) is greater than the set pressure of the second relief valve (13); S4.1 The oil output from the first manual directional valve (3) is delivered to the second manual directional valve (11); S4.2 When the second manual directional valve (11) selects function A, the oil output by the second manual directional valve (11) passes through the superimposed hydraulic control check valve (12) and is actively supplied with oil through the first oil circuit, which is the rod chamber of the #1 torque loading cylinder (25.1) and the rodless chamber of the #2 torque loading cylinder (25.2). The torque loading cylinder (25) drives the loading fin handle (26) to rotate counterclockwise, and applies counterclockwise torque to the fin shaft (27). The oil in the rodless chamber of the #1 torque loading cylinder (25.1) and the rod chamber of the #2 torque loading cylinder (25.2) flows to the second manual directional valve (11) through the second oil circuit and returns through the second manual directional valve (11). S4.3 When the second manual directional valve (11) selects function B, the oil output by the second manual directional valve (11) passes through the superimposed hydraulic control check valve (12) and then actively supplies oil through the second oil circuit, which is the rodless chamber of the #1 torque loading cylinder (25.1) and the rod chamber of the #2 torque loading cylinder (25.2). The torque loading cylinder (25) drives the loading fin handle (26) to rotate clockwise, and actively loads the fin shaft (27) with clockwise torque. The oil in the rod chamber of the #1 torque loading cylinder (25.1) and the rodless chamber of the #2 torque loading cylinder (25.2) flows to the second manual directional valve (11) through the first oil circuit and returns through the second manual directional valve (11). S4.4 The oil returned by the first manual reversing valve (3) and the second manual reversing valve (11) and the excess oil overflowing through the second overflow valve (13) are cooled by the second cooler (24) and filtered by the second filter (10) before returning to the oil tank. S4.5 Calculate the active loading torque. Active loading torque = active loading pressure × (area of rod chamber of torque loading cylinder (25) + area of rodless chamber of torque loading cylinder (25)) × radius of loading fin (26).
10. The torque loading test method for the anti-roll fin actuator according to claim 9, characterized in that, In step S3, the hydraulic unit applies passive torque to the anti-roll fins, including the following steps: S3.1 The fin shaft (27) of the anti-roll fin actuator rotates at a predetermined speed. The fin shaft (27) drives the loading fin handle (26) to rotate. The piston rods of the #1 torque loading cylinder (25.1) and the #2 torque loading cylinder (25.2) move in extension and retraction under the drive of the loading fin handle (26). When the fin shaft (27) drives the loading fin handle (26) to rotate clockwise, the oil in the rod chamber of the #1 torque loading cylinder (25.1) and the rodless chamber of the #2 torque loading cylinder (25.2) enters the first oil circuit of the hydraulic unit and is transported to the cover plate type cartridge relief valve (6) through the #4 cover plate type cartridge check valve (7.4). When the fin shaft (27) rotates counterclockwise, the oil in the rodless chamber of the #1 torque loading cylinder (25.1) and the rod chamber of the #2 torque loading cylinder (25.2) enters the second oil circuit of the hydraulic unit and is transported to the cover plate type cartridge relief valve (6) through the #3 cover plate type cartridge check valve (7.3). When the oil pressure at the front end of the cover-type cartridge relief valve (6), i.e. the passive loading pressure, does not exceed the set pressure of the cover-type cartridge relief valve (6), the oil stops flowing and enters a pressure-stagnant state, causing the fin shaft (27) to be passively loaded; when the oil pressure at the front end of the cover-type cartridge relief valve (6) reaches the set pressure of the cover-type cartridge relief valve (6), the cover-type cartridge relief valve (6) begins to overflow outward; S3.2 When the cover-type cartridge overflow valve (6) starts to overflow; the overflowing oil is cooled by the first cooler (8) and then merges with the oil that flows through the first manual reversing valve (3), check valve (4) and first filter (5) in sequence, and flows together to the front end of the parallel connection point of the 1# cover-type cartridge check valve (7.1) and the 2# cover-type cartridge check valve (7.2); When the fin shaft (27) rotates clockwise, the first oil circuit contains high-pressure oil and the second oil circuit contains low-pressure oil. The collected oil is replenished to the second oil circuit on the low-pressure side through the 2# cover plate type cartridge check valve (7.2). The oil flows through the second oil circuit to the rodless chamber of the 1# torque loading cylinder (25.1) and the rod chamber of the 2# torque loading cylinder (25.2) to passively load the fin shaft (27). When the fin shaft (27) rotates counterclockwise, the first oil circuit contains low-pressure oil and the second oil circuit contains high-pressure oil. The oil is replenished to the first oil circuit on the low-pressure side through the No. 1 cover plate type cartridge check valve (7.1). The oil flows from the first oil passage to the rod chamber of the #1 torque loading cylinder (25.1) and the rodless chamber of the #2 torque loading cylinder (25.2) to passively load the fin shaft (27); S3.3 Calculate the passive loading torque; Passive loading torque = passive loading pressure × (area of rod chamber of torque loading cylinder (25) + area of rodless chamber of torque loading cylinder (25)) × radius of loading fin (26).