A loading hydraulic system and method for fin lift and drag testing

Abstract

The application relates to a loading hydraulic system and method for lift and drag test of a stabilizer fin, belonging to the technical field of stabilizer fin test of a ship, which comprises a hydraulic unit, a lift loading oil cylinder and a drag loading oil cylinder; the hydraulic unit comprises a lift loading circuit and a drag loading circuit; the lift loading circuit comprises a lift loading pump with a load sensing function; the drag loading circuit comprises a drag loading pump; the lift loading pump and the drag loading pump rotate synchronously; two output ends of the lift loading circuit are connected with a rod cavity and a rodless cavity pipeline of the lift loading oil cylinder through a main pipeline; the lift loading oil cylinder provides lift for a fin shaft in a vertical upward posture of a piston rod; two output ends of the drag loading circuit are connected with a rod cavity and a rodless cavity pipeline of the drag loading oil cylinder; the drag loading oil cylinder provides drag for the fin shaft in a horizontal posture of a piston rod. The application can simultaneously carry out lift and drag simulation loading test on the stabilizer fin, can control the loading force in real time, and reduces the system energy consumption.

Description

Technical Field

[0001] This invention relates to the field of ship roll fin testing technology, specifically to a loading hydraulic system and method for testing the lift and drag of roll fins. 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] According to airfoil theory, fins moving in water generate lift, drag, and torque loads. Anti-roll fins achieve their anti-roll function primarily by relying on the lift generated on the fins to create a balancing torque that counteracts the rolling torque. The drag generated on the fins is the resistance that the ship must overcome during navigation. The torque acting on the fins is the torque that the anti-roll 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 experienced by the roll-damping fin during actual ship operation, including lift, drag, and torque loads, 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] Currently, the verification of lift and drag of the anti-roll fin usually uses a combination of a metering pump and an overflow valve for loading simulation. The fluid pressure is precisely controlled by manually using the overflow valve to apply lift and drag to the anti-roll fin, which results in high energy consumption of the equipment and the inability to control the loading pressure of lift and drag in real time. The pressure can only be adjusted and controlled by manually using the pressure valve, resulting in low experimental efficiency. Summary of the Invention

[0006] To address the shortcomings of the existing technology, this invention provides a loading hydraulic system and method for lift and drag testing of anti-roll fins. It simultaneously performs lift and drag simulation loading tests on anti-roll fins and can automatically control the loading force of lift and drag in real time. At the same time, the lift loading circuit has a load-sensitive function, realizing energy saving in the lift loading process and reducing system energy consumption.

[0007] To achieve the above objectives, the present invention provides the following technical solution:

[0008] A loading hydraulic system for testing the lift and drag of anti-roll fins, the loading hydraulic system comprising a hydraulic unit, a lift loading cylinder, and a drag loading cylinder;

[0009] The hydraulic unit includes a lift loading circuit and a resistance loading circuit; the lift loading circuit includes a lift loading pump with load-sensing function; the resistance loading circuit includes a resistance loading pump; the output shaft of the motor is sequentially connected to the lift loading pump and the resistance loading pump, and the lift loading pump and the resistance loading pump rotate synchronously under the drive of the motor to provide hydraulic oil to the lift loading circuit and the resistance loading circuit respectively;

[0010] The two outputs of the lifting loading circuit are connected to the two inputs of the shuttle valve via a bypass. The output of the shuttle valve is connected to the lifting loading pump. The shuttle valve connects to the output with the high load pressure in the lifting loading circuit and feeds back the high load pressure to the lifting loading pump. The two outputs of the lifting loading circuit are respectively connected to the rod-side and rodless-side pipelines of the lifting loading cylinder via a main pipeline. The lifting loading cylinder is connected to the fin shaft of the loaded anti-roll fin with the piston rod vertically upward, providing lift to the fin shaft.

[0011] The two outputs of the resistance loading circuit are respectively connected to the rod-side and rodless-side pipelines of the resistance loading cylinder; the resistance loading cylinder is connected to the fin shaft with the piston rod in a horizontal position to provide resistance to the fin shaft.

[0012] Furthermore, the lift loading circuit also includes a first pressure sensor and a proportional directional valve;

[0013] The output end of the lifting loading pump is connected to the input end of the proportional directional valve. The two output ends of the proportional directional valve are respectively connected to the rod chamber and rodless chamber of the lifting loading cylinder. The return end of the proportional directional valve is connected to the oil tank through the return oil pipeline.

[0014] The first pressure sensor is installed at each of the two output terminals of the proportional directional valve to monitor the load pressure at the two output terminals of the lift loading circuit in real time and to feed back the monitored load pressure to the loading control unit; the first pressure sensor is provided at the output terminal of the lift loading pump to monitor the pump source outlet pressure of the lift loading pump in real time and to feed back the pump source outlet pressure to the loading control unit.

[0015] The two outputs of the proportional directional valve are connected through the shuttle valve, and the shuttle valve is connected to the lift loading pump. The shuttle valve is connected to the output of the proportional directional valve with the high load pressure.

[0016] Furthermore, the lift loading circuit also includes a high-pressure filter and a first check valve; the output end of the lift loading pump, the high-pressure filter, the first check valve, and the input end of the proportional directional valve are connected in sequence via pipelines.

[0017] Furthermore, the lifting loading circuit also includes a pressure testing connector, a pressure testing hose, and a first pressure gauge; the pressure testing connector is installed at the output end of the lifting loading pump and at the two output ends of the proportional reversing valve, respectively. The pressure testing connector is connected to the first pressure gauge through the pressure testing hose, and the pump source outlet pressure of the lifting loading pump and the load pressure at the two output ends of the lifting loading circuit are observed in real time through the first pressure gauge.

[0018] Furthermore, the lift loading circuit also includes an electromagnetic overflow valve; the output end of the lift loading pump is connected to the return oil pipeline through the electromagnetic overflow valve.

[0019] Furthermore, the resistance loading circuit also includes a second pressure sensor, a proportional relief valve, and a manual directional valve;

[0020] The output end of the resistance loading pump is connected to the input end of the manual directional valve, and the output end of the resistance loading pump is connected to the return oil line through the proportional relief valve; the two output ends of the manual directional valve are respectively connected to the rod chamber and rodless chamber of the resistance loading cylinder, and the return oil end of the manual directional valve is connected to the oil tank through the return oil line.

[0021] The two outputs of the manual reversing valve and the output of the resistance loading pump are respectively equipped with the second pressure sensor, which is used to monitor the load pressure of the two outputs of the resistance loading circuit and the pump source outlet pressure of the resistance loading pump in real time, and feed the pressure back to the loading control unit.

[0022] Furthermore, a pressure testing connector is installed at the front end of the proportional relief valve. The pressure testing connector is connected to a second pressure gauge through a pressure testing hose. The pump source outlet pressure of the resistance loading pump can be observed in real time through the second pressure gauge.

[0023] The present invention also discloses a hydraulic loading method for reducing fin lift and drag. The method for conducting fin lift and drag loading tests according to any one of the above-mentioned hydraulic loading systems for fin lift and drag tests includes the following steps:

[0024] S1. The lift loading cylinder is connected to the fin shaft of the loaded anti-roll fin with the piston rod in a vertically upward position; the resistance loading cylinder is connected to the fin shaft of the loaded anti-roll fin with the piston rod in a horizontal position.

[0025] S2. After the motor starts, it drives the lift loading pump and the resistance loading pump to operate synchronously.

[0026] S3. The lifting loading pump pumps hydraulic oil into the proportional directional valve through the high-pressure filter and the first check valve. The lifting loading pump provides vertical upward and downward lift to the fin shaft. The loading control unit controls the proportional directional valve to switch the functional position and change the direction of lift.

[0027] S4. During the lift loading process, the load pressure P on the X1 side of the lift loading circuit is monitored in real time by the first pressure sensor. a and X2 side load pressure P b The load pressure is fed back to the loading control unit, which calculates the applied lift loading force.

[0028] The loading control unit controls the proportional directional valve to adjust the valve opening size based on the deviation between the calculated lifting loading force and the lifting loading target value, until the lifting loading pressure reaches the lifting loading target value, and then closes the proportional directional valve opening.

[0029] S5. While the lifting loading pump is operating, the resistance loading pump supplies hydraulic oil to the manual directional valve through the second check valve.

[0030] When the manual directional valve is switched to the functional position "a", the hydraulic oil enters the rod chamber of the resistance loading cylinder, and the piston rod of the resistance loading cylinder is in the retracted state, applying resistance loading to the fin shaft.

[0031] S6. During the resistance loading process, the load pressure P on the X3 side of the resistance loading circuit is monitored in real time by the second pressure sensor. c and the load pressure P on the X4 side d The load pressure is fed back to the loading control unit, which then calculates the applied resistance loading force.

[0032] The loading control unit controls the proportional relief valve to adjust the output pressure based on the deviation between the calculated resistance loading force and the resistance loading target value, until the loading hydraulic system reaches the resistance loading target value.

[0033] Further, in step S4, the lift loading force is calculated according to the following formula:

[0034] When the piston rod of the lifting loading cylinder extends, the lifting loading force F 升 =P b A2-P a A1, where: A1 is the area of ​​the rod-side chamber of the lifting loading cylinder, and A2 is the area of ​​the rodless chamber of the lifting loading cylinder;

[0035] When the piston rod of the lifting loading cylinder retracts, the lifting loading force F 升 =P a A1-P b A2.

[0036] Furthermore, in step S6, the resistance loading force F 阻 =P c A3-P d A4, where: A3 is the area of ​​the rod-side cavity of the resistance-loading cylinder, and A4 is the area of ​​the rodless cavity of the resistance-loading cylinder.

[0037] The beneficial effects of this invention are:

[0038] The hydraulic loading system and method of the present invention for lifting and drag testing of anti-roll fins can simultaneously conduct simulated lifting and drag loading tests on anti-roll fins during the land-based test bench stage to verify the basic functions, load-bearing capacity and reliability of the anti-roll fins, and can automatically control the loading force of lifting and drag in real time according to the loading requirements. At the same time, the lifting loading circuit has a load-sensitive function, realizing energy saving in the lifting loading process and reducing system energy consumption.

[0039] The lifting loading pump in the lifting loading circuit of this invention has a load-sensitive function. When the proportional directional valve orifice is fixed, the lifting loading circuit has a constant flow rate. Regardless of changes in the valve opening, the pump source outlet pressure is only a fixed value higher than the load pressure. This fixed value is set by the maximum elastic force of the adjusting spring B of the control valve B of the lifting loading pump. When the control valve B is in a balanced state, the force formed by the pressure difference between the control valve B and the pump outlet pressure and the load pressure acting on the valve core is equal. The control valve A sets the maximum pump outlet pressure. When the pump outlet pressure does not exceed the maximum pressure, the lifting loading pump is in maximum displacement mode. When the pump outlet pressure exceeds the maximum pressure, the pump displacement decreases. Within the maximum pressure limit range of the lifting loading pump, the pump source outlet pressure can always automatically adapt to load changes, meaning the lifting loading pump can always operate under conditions matching the load function, resulting in significant energy-saving effects. Attached Figure Description

[0040] Figure 1 This is a schematic diagram of the loading hydraulic system used in the anti-roll fin lift and drag test of the present invention;

[0041] Figure 2 This is a load-sensing schematic diagram of the lift loading circuit of the present invention;

[0042] Figure 3 This is a schematic diagram of the lift loading pressure control principle of the present invention;

[0043] Figure 4 This is a schematic diagram of the resistance loading pressure control principle of the present invention;

[0044] Figure 5 This is a schematic diagram showing the connection between the lifting loading cylinder and the fin shaft of the present invention;

[0045] Figure 6 This is a schematic diagram showing the connection between the resistance loading cylinder and the fin shaft of the present invention.

[0046] The components are as follows: 1-Hydraulic gauge, 2-Level control relay, 3-Temperature relay, 4-Air filter, 5-Shuttle valve, 6-First pressure sensor, 7-Hydraulic pump, 7.1-Lift loading pump, 7.2-Resistance loading pump, 8-Electric motor, 9-First check valve, 10-Second check valve, 11-Solenoid relief valve, 12-High pressure filter, 13-Second pressure sensor, 14-Pressure test connector, 15-Pressure test hose, 16-First pressure gauge, 17-Proportional directional valve, 18-Return oil filter, 19-Cooler, 20-Proportional relief valve, 21-Manual directional valve, 22-Second pressure gauge, 23-Lift loading cylinder, 24-Resistance loading cylinder, 25-First connecting pin, 26-Lift loading fin, 27-Fin shaft, 28-First support frame, 29-First bearing, 30-Second support frame, 31-Resistance loading fin, 32-Second connecting pin, 33-Second bearing. Detailed Implementation

[0047] 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.

[0048] 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.

[0049] 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.

[0050] This embodiment describes a loading hydraulic system and method for lifting and drag testing of anti-roll fins, used to conduct lift and drag simulation loading tests on anti-roll fins.

[0051] like Figure 1As shown, the loading hydraulic system consists of a hydraulic unit, a lifting loading cylinder 23, and a resistance loading cylinder 24. The hydraulic unit includes a hydraulic gauge 1, a level control relay 2, a temperature relay 3, an air filter 4, a shuttle valve 5, a first pressure sensor 6, a hydraulic pump 7, an electric motor 8, a first check valve 9, a second check valve 10, a solenoid relief valve 11, a high-pressure filter 12, a second pressure sensor 13, a pressure testing connector 14, a pressure testing hose 15, a first pressure gauge 16, a proportional directional valve 17, a return oil filter 18, a cooler 19, a proportional relief valve 20, a manual directional valve 21, and a second pressure gauge 22.

[0052] The hydraulic pump 7 consists of a lift loading pump 7.1 and a resistance loading pump 7.2, which are used to apply lift and resistance to the anti-roll fins, respectively. The output shaft of the motor 8 is connected to the lift loading pump 7.1 and the resistance loading pump 7.2 in sequence via a coupling, driving the lift loading pump 7.1 and the resistance loading pump 7.2 to rotate synchronously. In this embodiment, the motor 8 is a three-phase asynchronous motor, the lift loading pump 7.1 is an axial piston pump with load-sensitive function, and the resistance loading pump 7.2 is a vane pump or a gear pump.

[0053] The lift loading pump 7.1 has pressure and flow control functions, such as... Figure 2 As shown, the lift loading pump 7.1 includes a control cylinder, a swashplate, control valve A, and control valve B.

[0054] The control cylinder contains a piston, and a piston rod is connected to one side of the piston. The outer end of the piston rod is connected to a swashplate installed on the lifting loading pump 7.1. A spring is fitted on the piston rod. The angle of the swashplate is adjusted by the extension and retraction of the piston rod, thereby adjusting the pump displacement of the lifting loading pump 7.1.

[0055] Control valve A is a pressure control valve, containing a valve core and an adjusting spring A. Control valve A adjusts the valve core position by adjusting the spring force of spring A, thereby setting the maximum working pressure at the outlet of the lifting loading pump 7.1. The outlet of the lifting loading pump 7.1 is connected to port P of control valve A via a control oil circuit. The adjusting spring A applies pressure to one side of the valve core, and hydraulic oil applies pressure from the other side of the valve core. Port A of control valve A is connected to the rodless chamber of the control cylinder, and port T of control valve A is connected to the return oil circuit. Control valve A has functional positions a and b. Control valve A switches to functional position b only when the valve core moves to the right to a certain extent. Its internal oil circuit connects port P and port A, directly supplying the hydraulic oil output from the outlet of the loading pump 7.1 to the rodless chamber of the control cylinder.

[0056] When the pump outlet pressure of the lifting loading pump 7.1 does not exceed the maximum working pressure, the high-pressure oil pressure in the valve chamber of control valve A is less than the pressure exerted on the valve core by the adjusting spring A, and control valve A is in function position a. When the pump outlet pressure exceeds the maximum working pressure, the high-pressure oil pressure in the valve chamber is greater than the pressure exerted on the valve core by the adjusting spring A, which causes the valve core of control valve A to move to the right, and control valve A switches to function position b. The high-pressure oil enters the rodless chamber of the control cylinder through the oil passage in function b, and the piston rod extends to minimize the swashplate angle, making the output flow of the lifting loading pump 7.1 zero.

[0057] Control valve B is a flow control valve, i.e., a load-sensitive valve, used to regulate the outlet flow of the lift-loading pump 7.1 to maintain a constant inlet pressure drop at the proportional directional valve 17. Control valve B contains a valve core and an adjusting spring B, with the two ends of the adjusting spring B connected to the valve core and the pressure receiving end (i.e.,...) respectively. Figure 2 The maximum spring force of adjusting spring B is a preset fixed value, which is offset by the n-point (where the load pressure is received) in the middle. Under normal working conditions, the set pressure value of adjusting spring B is much smaller than the set pressure value of adjusting spring A (for example, in typical working conditions, the set pressure of adjusting spring B of control valve B is 1.4MPa, and the set pressure of adjusting spring A of control valve A is determined according to the maximum working pressure of the loading hydraulic system, which is generally 10MPa to 20MPa, or even larger).

[0058] The P port of control valve B is connected to the pump outlet of the lifting loading pump 7.1 via a control oil circuit. The A port of control valve B is connected to the rodless chamber of the control cylinder, and the T port is connected to the return oil circuit. Control valve B has functional positions a and b. When control valve B is in functional position a, its internal oil circuit connects to ports A and T. When control valve B is in functional position b, its internal oil circuit connects to ports P and A.

[0059] The outlet pressure of the lifting loading pump 7.1 is fed back to the control valve B through the control oil circuit. The pressure applied to the valve core by the adjusting spring B of the control valve B, together with the load pressure fed back to the pressure receiving end, acts on the right side of the valve core of the control valve B. The pressure of the high-pressure oil in the valve chamber of the control valve B acts on the left side of the valve core of the control valve B. When the pressures on the left and right sides of the valve core of the control valve B are balanced, the lifting loading pump 7.1 outputs oil stably. When the load pressure decreases due to load changes or other reasons, the valve inlet pressure drop increases, the valve port flow increases, and the high-pressure oil pressure on the left side of the valve core of the control valve B exceeds the sum of the load pressure and the pressure of the adjusting spring B on the valve core. The valve core moves to the right, and the control valve B switches to function b position. The high-pressure oil flows into the rodless chamber of the control cylinder through the oil circuit in function b, adjusting the maximum outlet flow of the lifting loading pump 7.1, so that the displacement of the lifting loading pump 7.1 decreases until the forces on the left and right sides of the valve core of the control valve B are balanced. If the load pressure increases, control valve B automatically adjusts the outlet flow of the lifting loading pump 7.1 in the reverse direction. This means the valve core moves to the left, control valve B switches to function position a, and the high-pressure oil in the rodless chamber returns to the oil tank through control valve B, increasing the displacement of the lifting loading pump 7.1. When the loading hydraulic system is in a stable state, the pump outlet pressure is only a fixed value higher than the load pressure, i.e., the pressure value set by adjusting spring B.

[0060] The hydraulic loading system consists of shuttle valve 5, first pressure sensor 6, lifting loading pump 7.1, first check valve 9, solenoid relief valve 11, high pressure filter 12, pressure test connector 14, pressure test hose 15, first pressure gauge 16, and proportional directional valve 17, forming a lifting loading circuit. The resistance loading system consists of resistance loading pump 7.2, second check valve 10, second pressure sensor 13, pressure test connector 14, pressure test hose 15, proportional relief valve 20, manual directional valve 21, and second pressure gauge 22, forming a resistance loading circuit.

[0061] The proportional directional valve 17 has one input end, two output ends, and one return end. In the lift loading circuit, the output end of the lift loading pump 7.1 is sequentially connected to the high-pressure filter 12, the first check valve 9, and the input end of the proportional directional valve 17. The two output ends of the proportional directional valve 17 are respectively connected to the rod chamber and rodless chamber pipelines of the lift loading cylinder 23. The return end of the proportional directional valve 17 is connected to the oil tank through a return pipeline to return the fluid to the oil tank.

[0062] The two outputs of the proportional directional valve 17 are connected to the two inputs of the shuttle valve 5 via a bypass, and the output of the shuttle valve 5 is connected to the control valve B of the lift loading pump 7.1. The shuttle valve 5 feeds back the higher load pressure from the two outputs of the proportional directional valve 17 to the control valve B. The control valve B, together with the proportional directional valve 17 and the shuttle valve 5, realizes the flow control of the lift loading pump 7.1.

[0063] A first pressure sensor 6, a pressure testing connector 14, and a first pressure gauge 16 are respectively installed between the first one-way valve 9 and the high-pressure filter 12, and at the two output terminals of the proportional directional valve 17. The pressure testing connector 14 is connected to the first pressure gauge 16 via a pressure testing hose 15. Figure 3 As shown, the fluid pressure can be monitored in real time by the first pressure sensor 6 and the first pressure gauge 16. While monitoring the fluid pressure, the first pressure sensor 6 feeds back the monitored pressure to the loading control unit. The loading control unit calculates the applied lift force and compares it with the target lift loading value. Based on the deviation value, it controls the proportional directional valve 17 to operate until the lift loading pressure reaches the control target value, at which point the proportional directional valve 17 is closed. This constitutes a closed-loop control system for the lift loading pressure, thereby achieving control of the loading pressure and accurately controlling the loading lift. In this embodiment, the first pressure sensor 6 (#1) is used to monitor the pump source outlet pressure P of the lift loading loop in real time. s1 Pressure gauge #16 is used to monitor the pump outlet pressure P in real time. s1 #2, the first pressure sensor 6, is used to monitor the load pressure P on the output side of the proportional directional valve 17X1 (i.e., the lift loading circuit X1 side) in real time. a #2, the first pressure gauge 16 is used for real-time monitoring of load pressure P. a The first pressure sensor 6 (#3) is used to monitor the load pressure P on the output side of the proportional directional valve 17X2 (i.e., the lift loading circuit X2 side) in real time. b Pressure gauge #3 (16) is used for real-time monitoring of load pressure P. b .

[0064] The loading hydraulic system in this embodiment, through shuttle valve 5, can... Figure 2 The pressure at point m is always related to the load pressure P. a With load pressure P b Connect the medium-pressure and high-pressure components, load pressure P a With load pressure P b The pressure at the higher end of the medium pressure range (i.e., the pressure at point m) is fed back to point n after the control valve B of the lifting pump 7.1 via shuttle valve 5. The lifting pump 7.1 controls the flow rate of the pumped oil based on the received pressure.

[0065] The valve inlet pressure drop ΔP on the proportional directional valve 17: (1) When P a >P b At that time, ΔP = P s1 -P a (2) When P b >P a At that time, ΔP = P s1 -P b .

[0066] When the valve core of control valve B is in equilibrium, the spring force of adjusting spring B / the effective area of ​​the valve core = the pump outlet pressure P. s1 -Load pressure P a With P b The pressure drop at the inlet of the proportional directional valve is equal to the pressure drop ΔP at the valve inlet. This pressure drop ΔP is preset by the adjusting spring B of control valve B and is a constant. During the loading test, the pressure drop ΔP at the inlet of proportional directional valve 17 is a fixed value. When the valve port of proportional directional valve 17 is fixed, the flow rate through proportional directional valve 17 is constant, and regardless of changes in the valve opening, the pump outlet pressure P remains constant. s1 It is only one fixed value higher than the load pressure. Within the maximum pressure limit range of the 7.1 lift-load pump, the pump outlet pressure can always automatically adapt to load changes and always operate under conditions that match the load function, resulting in significant energy-saving effects.

[0067] The electromagnetic relief valve 11 is a safety valve in the lift loading circuit, used to limit the maximum pressure of the lift loading circuit. The electromagnetic relief valve 11 is located between the lift loading pump 7.1 and the high-pressure filter 12. The outlet of the electromagnetic relief valve 11 is connected to the return oil line, returning the overflowing fluid to the oil tank. When the loading hydraulic system starts, the solenoid valve on the electromagnetic relief valve 11 is de-energized, putting the loading hydraulic system in an unloaded state. After the motor 8 starts, the solenoid valve on the electromagnetic relief valve 11 is energized, putting the loading hydraulic system in a loaded state.

[0068] In the resistance loading circuit, the output end of the resistance loading pump 7.2, the second check valve 10, and the input end of the manual directional valve 21 are sequentially connected by pipelines. Simultaneously, the output end of the resistance loading pump 7.2 is connected to the return oil pipeline via the proportional relief valve 20. The two output ends of the manual directional valve 21 are respectively connected to the rod-side and rodless-side pipelines of the resistance loading cylinder 24. The return oil end of the manual directional valve 21 is connected to the oil tank via the return oil pipeline to return the fluid to the oil tank. Because the fin shaft moves up and down under the loading lift, during resistance loading, if the loading resistance is tension, it ensures that the loading resistance acts near the equilibrium position. If the loading resistance is thrust, when the fin shaft moves up and down under the loading lift, the loading resistance will deviate from the equilibrium position, and the deviation will become increasingly larger. Therefore, during loading, the direction of the force exerted by the resistance loading cylinder 24 on the anti-roll fin shaft is only tension; that is, during resistance loading, the cylinder piston rod is in a retracted state.

[0069] Second pressure sensors 13 are respectively installed at the two output ends of the manual directional valve 21 and at the front end of the proportional relief valve 20. Among them, the first second pressure sensor 13 is used to monitor the load pressure P on the output side of the manual directional valve 21X3 (i.e., the resistance loading circuit X3 side) in real time. c The second pressure sensor 13 (#2) is used to monitor the load pressure P on the output side of the manual directional valve 21X4 (output side of the resistance loading circuit X4) in real time. dThe second pressure sensor (#3) is used to monitor the outlet pressure P of the pump source in the resistance loading circuit in real time. s2 .like Figure 4 As shown, the second pressure sensor 13 transmits the monitored pressure to the loading control unit while monitoring the pressure in real time. The loading control unit calculates the applied loading resistance and compares it with the target value of the resistance loading. Based on the deviation value, it controls the proportional relief valve 20 until the resistance loading circuit reaches the target value of the resistance loading.

[0070] In this embodiment, to facilitate real-time observation of the pump source outlet pressure, a pressure testing connector 14 is installed in the pipeline at the front end of the proportional relief valve 20. The top of the pressure testing connector 14 is connected to the second pressure gauge 22 through the pressure testing hose 15. The pump source outlet pressure can be monitored in real time through the second pressure gauge 22.

[0071] In this embodiment, a return oil filter 18 and a cooler 19 are installed on the return oil pipeline. The oil flows through the cooler 19 and the return oil filter 18 in sequence before returning to the oil tank. The return oil filter 18 filters the return oil, cleaning the loading hydraulic system. The cooler 19 removes heat from the loading hydraulic system through heat exchange, reducing the temperature of the loading hydraulic system.

[0072] The hydraulic press unit's oil tank is equipped with a level gauge 1, a level control relay 2, a temperature relay 3, and an air filter 4. Level gauge 1 is used to observe the oil level in the tank. Level control relay 2 monitors the oil level and sends feedback to the loading control unit. When the oil level is too low, the loading control unit triggers an alarm and stops the loading hydraulic system, protecting it. Temperature relay 3 monitors the oil temperature in the tank and sends the temperature information back to the loading control unit. When the set high temperature value is reached, the loading control unit triggers an alarm and stops the loading hydraulic system, protecting it. Air filter 4 filters impurities and dust from the air entering the tank, ensuring the cleanliness of the loading hydraulic system.

[0073] In this embodiment, when the hydraulic loading system loads the anti-roll fins, the rod-side chamber (Y1 port) of the lift loading cylinder 23 is connected to the output port X1 of the hydraulic unit, the rodless chamber (Y2 port) of the lift loading cylinder 23 is connected to the output port X2 of the hydraulic unit, the rod-side chamber (Y3 port) of the resistance loading cylinder 24 is connected to the output port X3 of the hydraulic unit, and the rodless chamber (Y4 port) of the resistance loading cylinder 24 is connected to the output port X4 of the hydraulic unit. The loading process is as follows:

[0074] 1. For example Figure 5As shown, the lifting loading cylinder 23 is mounted on the loading platform below the fin shaft 27 with its piston rod vertically upward via the first support frame 28. The lug at the piston rod end of the lifting loading cylinder 23 is connected to the lifting loading fin handle 26 via the first connecting pin 25. The lifting loading fin handle 26 is fitted onto the fin shaft 27 of the loaded anti-roll fin, and a first bearing 29 is provided between the lifting loading fin handle 26 and the fin shaft 27. The force of the lifting loading cylinder 23 is transmitted to the lifting loading fin handle 26 via the first connecting pin 25, and the lifting loading fin handle 26 applies the loading lift to the fin shaft 27.

[0075] like Figure 6 As shown, the resistance loading cylinder 24 is mounted on the loading platform with its piston rod in a horizontal position via the second support frame 30. That is, the axial direction of the resistance loading cylinder 24 is perpendicular to that of the lift loading cylinder 23. The lug at the piston rod end of the resistance loading cylinder 24 is connected to the resistance loading fin handle 31 via the second connecting pin 32. The resistance loading fin handle 31 is fitted onto the fin shaft 27 of the loaded anti-roll fin. A second bearing 33 is provided between the fin shaft 27 and the resistance loading fin handle 31. The force of the resistance loading cylinder 24 is transmitted to the resistance loading fin handle 31 via the second connecting pin 32. The resistance loading fin handle 31 applies the loading resistance to the fin shaft 27.

[0076] 2. After the motor 8 starts, it drives the lifting loading pump 7.1 and the resistance loading pump 7.2 to operate synchronously and output hydraulic power.

[0077] 3. The lifting loading pump 7.1 pumps hydraulic oil into the proportional directional valve 17 through the high-pressure filter 12 and the first check valve 9.

[0078] The loading control unit controls the proportional directional valve 17 to operate. When the proportional directional valve 17 switches to the left functional position, hydraulic oil enters the rod chamber of the lifting loading cylinder 23 through the loading oil circuit X1, providing a vertically downward lift to the fin shaft. When the proportional directional valve 17 switches to the right functional position, hydraulic oil enters the rodless chamber of the lifting loading cylinder 23 through the loading oil circuit X2, providing a vertically upward lift to the fin shaft.

[0079] 4. During the lift loading process, pressure sensors 6#2 and 3# monitor the load pressure P on the X1 side of the lift loading circuit in real time. a and X2 side load pressure P b The load pressure is fed back to the loading control unit, which then calculates the applied lift loading force.

[0080] When the piston rod of the lifting loading cylinder 23 extends, the lifting loading force F 升 =P b A2-P a A1, where: A1 is the area of ​​the rod-side cavity of the lifting loading cylinder 23, and A2 is the area of ​​the rodless cavity of the lifting loading cylinder 23.

[0081] When the piston rod of the lifting loading cylinder 23 retracts, the lifting loading force F 升 =P a A1-P b A2.

[0082] The loading control unit controls the proportional directional valve 17 to adjust the valve port size according to the deviation between the calculated lifting loading force and the lifting loading target value, until the lifting loading pressure reaches the lifting loading target value, and then closes the valve port of the proportional directional valve 17.

[0083] 5. While the lifting loading pump 7.1 is operating, the resistance loading pump 7.2 supplies hydraulic oil to the manual directional valve 21 through the second check valve 10.

[0084] When the hydraulic system is running normally, when the manual directional valve 21 is switched to the functional position "a", the hydraulic oil enters the rod chamber of the resistance loading cylinder 24. The piston rod of the resistance loading cylinder 24 is in the retracted state, and resistance loading is applied to the anti-roll fin shaft. The loading direction is horizontal tension, and the loading pressure is controlled by the proportional relief valve 20.

[0085] 6. During the resistance loading process, the second pressure sensors 1# and 2# monitor the load pressure P on the X3 side of the resistance loading circuit in real time. c and the load pressure P on the X4 side d The load pressure is fed back to the loading control unit, which then calculates the applied resistance loading force.

[0086] Resistance loading force F 阻 =P c A3-P d A4, where: A3 is the area of ​​the rod-side cavity of the resistance loading cylinder 24, and A4 is the area of ​​the rodless cavity of the resistance loading cylinder 24.

[0087] The loading control unit controls the proportional relief valve 20 to adjust the output pressure according to the deviation between the calculated resistance loading force and the resistance loading target value, until the loading hydraulic system reaches the resistance loading target value.

[0088] 7. When the manual directional valve 21 is switched to the intermediate functional position, the resistance loading circuit is unloaded.

[0089] 8. When the manual directional valve 21 is switched to the functional position "b", the piston rod of the resistance loading cylinder 24 extends, which facilitates the adjustment of the position of the cylinder piston rod.

[0090] 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 loading hydraulic system for testing the lift and drag of anti-roll fins, characterized in that, The loading hydraulic system includes a hydraulic unit, a lifting loading cylinder (23), and a resistance loading cylinder (24). The hydraulic unit includes a lifting loading circuit and a resistance loading circuit; the lifting loading circuit includes a lifting loading pump (7.1) with load-sensitive function, a first pressure sensor (6), and a proportional directional valve (17); the resistance loading circuit includes a resistance loading pump (7.2), a second pressure sensor (13), a proportional relief valve (20), and a manual directional valve (21); the output shaft of the motor (8) is sequentially connected to the lifting loading pump (7.1) and the resistance loading pump (7.2), and the lifting loading pump (7.1) and the resistance loading pump (7.2) rotate synchronously under the drive of the motor (8) to provide hydraulic oil to the lifting loading circuit and the resistance loading circuit respectively; The output end of the lifting loading pump (7.1) is connected to the input end of the proportional directional valve (17) via a pipeline. The two output ends of the proportional directional valve (17) are respectively connected to the rod chamber and rodless chamber of the lifting loading cylinder (23) via a main pipeline. The return end of the proportional directional valve (17) is connected to the oil tank via a return pipeline. The lifting loading cylinder (23) is connected to the fin shaft of the loaded anti-roll fin with the piston rod vertically upward, providing lift to the fin shaft. The first pressure sensor (6) is installed at each of the two output ends of the proportional directional valve (17) to monitor the load pressure at the two output ends of the lifting loading circuit in real time and to feed back the monitored load pressure to the loading control unit; the first pressure sensor (6) is provided at the output end of the lifting loading pump (7.1) to monitor the pump source outlet pressure of the lifting loading pump (7.1) in real time and to feed back the pump source outlet pressure to the loading control unit; The two outputs of the proportional directional valve (17) are connected to the two inputs of the shuttle valve (5) via a bypass. The output of the shuttle valve (5) is connected to the lift loading pump (7.1). The shuttle valve (5) connects to the output of the proportional directional valve (17) with high load pressure and feeds back the high load pressure to the lift loading pump (7.1). The output end of the resistance loading pump (7.2) is connected to the input end of the manual reversing valve (21) via a pipeline, and the output end of the resistance loading pump (7.2) is connected to the return oil pipeline via the proportional relief valve (20); the two output ends of the manual reversing valve (21) are respectively connected to the rod chamber and rodless chamber pipelines of the resistance loading cylinder (24), and the return oil end of the manual reversing valve (21) is connected to the oil tank via the return oil pipeline; the resistance loading cylinder (24) is connected to the fin shaft with the piston rod in a horizontal position to provide resistance to the fin shaft; The two outputs of the manual reversing valve (21) and the output of the resistance loading pump (7.2) are respectively equipped with the second pressure sensor (13), which is used to monitor the load pressure of the two outputs of the resistance loading circuit and the pump source outlet pressure of the resistance loading pump (7.2) in real time, and feed the pressure back to the loading control unit.

2. The loading hydraulic system for the anti-roll fin lift and drag test according to claim 1, characterized in that, The lifting loading circuit also includes a high-pressure filter (12) and a first check valve (9); the output end of the lifting loading pump (7.1), the high-pressure filter (12), the first check valve (9), and the input end of the proportional directional valve (17) are connected in sequence by pipeline.

3. The loading hydraulic system for the anti-roll fin lift and drag test according to claim 1, characterized in that, The lifting loading circuit also includes a pressure testing connector (14), a pressure testing hose (15), and a first pressure gauge (16). The pressure testing connector (14) is installed at the output end of the lifting loading pump (7.1) and at the two output ends of the proportional directional valve (17). The pressure testing connector (14) is connected to the first pressure gauge (16) through the pressure testing hose (15). The first pressure gauge (16) is used to observe the pump source outlet pressure of the lifting loading pump (7.1) and the load pressure at the two output ends of the lifting loading circuit in real time.

4. The loading hydraulic system for the anti-roll fin lift and drag test according to claim 1, characterized in that, The lifting loading circuit also includes an electromagnetic overflow valve (11); the output end of the lifting loading pump (7.1) is connected to the return oil pipeline through the electromagnetic overflow valve (11).

5. The loading hydraulic system for the anti-roll fin lift and drag test according to claim 1, characterized in that, A pressure test connector (14) is installed at the front end of the proportional relief valve (20). The pressure test connector (14) is connected to the second pressure gauge (22) through the pressure test hose (15). The pump source outlet pressure of the resistance loading pump (7.2) can be observed in real time through the second pressure gauge (22).

6. A hydraulic loading method for reducing fin lift resistance, characterized in that, The method for conducting a fin lift and drag loading test using a loading hydraulic system according to any one of claims 1 to 5 comprises the following steps: S1, the lifting loading cylinder (23) is connected to the fin shaft of the loaded anti-roll fin with the piston rod in a vertically upward posture; the resistance loading cylinder (24) is connected to the fin shaft of the loaded anti-roll fin with the piston rod in a horizontal posture. S2. After the motor (8) starts, it drives the lifting loading pump (7.1) and the resistance loading pump (7.2) to operate synchronously; S3, the lifting loading pump (7.1) pumps hydraulic oil into the proportional directional valve (17) through the high pressure filter (12) and the first check valve (9); the lifting loading pump (7.1) provides vertical upward and downward lift to the fin shaft, and the loading control unit controls the proportional directional valve (17) to switch the functional position and change the direction of lift; S4. During the lifting loading process, the load pressure P on the X1 side of the lifting loading circuit is monitored in real time by the first pressure sensor (6). a and X2 side load pressure P b The load pressure is fed back to the loading control unit, which calculates the applied lift loading force. The loading control unit controls the proportional directional valve (17) to adjust the valve port size according to the deviation between the calculated lifting loading force and the lifting loading target value, until the lifting loading pressure reaches the lifting loading target value, and then closes the valve port of the proportional directional valve (17). S5. While the lifting loading pump (7.1) is operating, the resistance loading pump (7.2) supplies hydraulic fluid to the manual directional valve (21) through the second check valve (10). When the manual directional valve (21) is switched to the functional position "a", the hydraulic oil enters the rod chamber of the resistance loading cylinder (24), and the piston rod of the resistance loading cylinder (24) is in the retracted state, applying resistance loading to the fin shaft; S6. During the resistance loading process, the load pressure on the X3 side of the resistance loading circuit is monitored in real time by the second pressure sensor (13). and the load pressure on the X4 side The load pressure is fed back to the loading control unit, which then calculates the applied resistance loading force. The loading control unit controls the proportional relief valve (20) to adjust the output pressure according to the deviation between the calculated resistance loading force and the resistance loading target value, until the loading hydraulic system reaches the resistance loading target value.

7. The hydraulic method for reducing fin lift resistance according to claim 6, characterized in that, In step S4, the lift loading force is calculated according to the following formula: When the piston rod of the lifting loading cylinder (23) extends, the lifting loading force F 升 =P b A2-P a A1, where: A1 is the area of ​​the rod chamber of the lifting loading cylinder (23), and A2 is the area of ​​the rodless chamber of the lifting loading cylinder (23). When the piston rod of the lifting loading cylinder (23) retracts, the lifting loading force F 升 =P a A1-P b A2.

8. The hydraulic loading method for reducing fin lift resistance according to claim 6, characterized in that, In step S6, the resistance loading force F 阻 =P c A3-P d A4, where: A3 is the area of ​​the rod-side cavity of the resistance loading cylinder (24), and A4 is the area of ​​the rodless cavity of the resistance loading cylinder (24).

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