Loading hydraulic system and method for fin stabilizer lift and resistance test

Abstract

The invention relates to a loading hydraulic system and method for fin stabilizer lift and resistance tests, and belongs to the technical field of ship fin stabilizer tests. The system comprises a hydraulic unit, a lift loading oil cylinder and a resistance loading oil cylinder; the hydraulic unit comprises a lift force loading loop and a resistance loading loop; the lift force loading loop comprises a lift force loading pump with a load sensitive function; the resistance loading loop comprises a resistance loading pump; the lift force loading pump and the resistance loading pump rotate synchronously; two output ends of the lift force loading loop are respectively connected with a rod cavity pipeline and a rodless cavity pipeline of the lift force loading oil cylinder through main pipelines; the lift force loading oil cylinder provides lift force for the fin shaft in a vertical upward posture of a piston rod; two output ends of the resistance loading loop are respectively connected with a rod cavity pipeline and a rodless cavity pipeline of the resistance loading oil cylinder; the resistance loading oil cylinder provides resistance for the fin shaft in the horizontal posture of the piston rod. According to the invention, a lift force and resistance simulation loading test can be simultaneously carried out on the fin stabilizer, the loading force can be controlled in real time, and the system energy consumption is reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of ship fin stabilizer testing, and in particular to a loading hydraulic system and method for lift and resistance tests of fin stabilizers. Background Art

[0002] As the main device for reducing ship roll, fin stabilizers have been widely used on actual ships. They can effectively reduce the ship's roll angle when encountering strong winds and waves during navigation.

[0003] According to airfoil theory, a fin moving in the water generates lift, drag, and torque loads. Fin stabilizers achieve their roll reduction function primarily by generating a balancing torque on the fin to offset the ship's rolling moment. The drag generated by the fin is the resistance that the ship must overcome during navigation. The torque applied to the fin is the torque that the fin stabilizer must overcome during its rotational motion.

[0004] Fin stabilizers primarily consist of fins, actuators, hydraulic units, electronic control equipment, and fin mounts or fin boxes. The lift, drag, and torque loads generated by the fins are transmitted from the fins to the fin stabilizer actuators. When developing new fin stabilizer products, loading tests are performed on the actuators. The loads to which the fins are subjected during shipboard operation, including lift, drag, and torque, are simulated and applied to the fin stabilizer research prototypes to verify whether the designed prototypes meet the requirements of actual shipboard operating conditions in terms of basic functionality, load-bearing capacity, and reliability.

[0005] Currently, verification of the lift and drag of fin stabilizers usually uses a combination of a metering pump and a relief valve for loading simulation. The lift and drag are loaded on the fin stabilizers by precisely controlling the fluid pressure through a manual relief valve. This results in high energy consumption of the equipment and the inability to control the lift and drag loading pressure in real time. The control pressure can only be adjusted through a manual pressure valve, resulting in low test efficiency. Summary of the Invention

[0006] In response to the above-mentioned deficiencies in the prior art, the present invention provides a loading hydraulic system and method for lift and drag tests on fin stabilizers. The system simultaneously performs lift and drag simulation loading tests on the fin stabilizers and can automatically control the lift and drag loading forces in real time. At the same time, the lift loading circuit has a load-sensing function, which achieves energy saving during the lift loading process and reduces system energy consumption.

[0007] To achieve the above object, the present invention provides the following technical solutions:

[0008] A loading hydraulic system for lift and drag tests of fin stabilizers, 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 a 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 output ends of the lift loading circuit are connected to the two input ends of a shuttle valve through a bypass, and the output end of the shuttle valve is connected to the lift loading pump; the shuttle valve is connected to the output end with high load pressure in the lift loading circuit and feeds the high load pressure back to the lift loading pump; the two output ends of the lift loading circuit are respectively connected to the rod chamber and rodless chamber pipelines of the lift loading cylinder through the main pipeline; the lift loading cylinder is connected to the fin shaft of the loaded stabilizer fin with the piston rod in a vertically upward posture, providing lift for the fin shaft;

[0011] The two output ends of the resistance loading circuit are respectively connected to the rod chamber and rodless chamber pipelines of the resistance loading cylinder; the resistance loading cylinder is connected to the fin shaft with the piston rod in a horizontal posture to provide resistance for the fin shaft.

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

[0013] The output end of the lift loading pump is connected to the input end pipeline of the proportional reversing valve, the two output ends of the proportional reversing valve are respectively connected to the rod chamber and rodless chamber pipelines of the lift loading cylinder, and the return oil end of the proportional reversing valve is connected to the oil tank through the return oil pipeline;

[0014] The first pressure sensors are respectively installed at the two output ends of the proportional reversing valve, for respectively monitoring the load pressures at the two output ends of the lift loading circuit in real time, and feeding back the monitored load pressures to the loading control unit; the first pressure sensor is provided at the output end of the lift loading pump, for monitoring the pump source outlet pressure of the lift loading pump in real time, and feeding back the pump source outlet pressure to the loading control unit;

[0015] The two output ends of the proportional reversing 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 end of the proportional reversing valve with high load pressure.

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

[0017] Furthermore, the lift loading circuit also includes a pressure measuring joint, a pressure measuring hose, and a first pressure gauge; the pressure measuring joint is respectively installed at the output end of the lift loading pump and the two output ends of the proportional reversing valve, and the pressure measuring joint is connected to the first pressure gauge through the pressure measuring hose, and the pump source outlet pressure of the lift loading pump and the load pressure of the two output ends of the lift loading circuit are respectively 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 oil return 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 reversing valve;

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

[0021] The second pressure sensors are respectively installed at the two output ends of the manual reversing valve and the output end of the resistance loading pump, for respectively monitoring the load pressure at the two output ends of the resistance loading circuit and the pump source outlet pressure of the resistance loading pump in real time, and feeding back the pressure to the loading control unit.

[0022] Furthermore, a pressure measuring joint is installed at the front end of the proportional relief valve, and the pressure measuring joint is connected to a second pressure gauge through a pressure measuring 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 further discloses a hydraulic method for loading lift and drag of a fin stabilizer. The method for performing a lift and drag loading test of a fin stabilizer according to any one of the above-mentioned loading hydraulic systems for testing lift and drag of a fin stabilizer comprises the following steps:

[0024] S1. The lift loading cylinder is connected to the fin shaft of the loaded fin stabilizer with the piston rod in a vertical upward position; the resistance loading cylinder is connected to the fin shaft of the loaded fin stabilizer 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 lift loading pump pumps hydraulic oil through the high-pressure filter and the first one-way valve to the proportional reversing valve. The lift loading pump provides vertical upward and downward lift for the fin shaft. The loading control unit controls the proportional reversing valve to switch the functional position and change the lift direction.

[0027] S4, during the lift loading process, the load pressure P on the lift loading circuit X1 side 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, and the loading control unit calculates the applied lift loading force;

[0028] The loading control unit controls the proportional reversing valve to adjust the valve port size according to the calculated deviation between the lift loading force and the lift loading target value, and closes the valve port of the proportional reversing valve after the lift loading pressure reaches the lift loading target value;

[0029] S5. While the lift loading pump is operating, the resistance loading pump supplies hydraulic oil to the manual reversing valve through the second one-way valve;

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

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

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

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

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

[0035] When the lift loading cylinder piston rod retracts, the lift 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 rod cavity area of the resistance loading cylinder, and A4 is the rodless cavity area of the resistance loading cylinder.

[0037] Beneficial effects of the present invention:

[0038] The loading hydraulic system and method for lift and drag tests of fin stabilizers of the present invention can simultaneously perform simulated lift and drag loading tests on fin stabilizers during the onshore bench test phase to verify technical indicators such as the basic functions, load-bearing capacity, and reliability of the fin stabilizers. The system and method can also automatically control the lift and drag loading forces in real time according to loading requirements. Furthermore, the lift loading circuit has a load-sensing function, thereby achieving energy conservation during the lift loading process and reducing system energy consumption.

[0039] The lift loading pump in the lift loading circuit of the present invention has a load-sensitive function. The lift loading circuit has a constant flow rate when the valve port of the proportional reversing valve is fixed, and no matter how the valve port opening changes, the pump source outlet pressure is only a fixed value higher than the load pressure. The fixed value is set by the maximum elastic force of the regulating spring B of the control valve B of the lift loading pump. When the control valve B is in a balanced state, the force formed on the valve core by the pressure difference between the pump outlet pressure and the load pressure is equal. The control valve A sets the maximum pressure of the pump port. When the pump port pressure does not exceed the maximum pressure, the lift loading pump is in the maximum displacement state. When the pump port pressure exceeds the maximum pressure, the pump displacement becomes smaller. Within the maximum pressure limit of the lift loading pump, the pump source outlet pressure can always automatically adapt to load changes, that is, the lift loading pump can always work in a working condition that matches the load function, with obvious energy-saving effects. BRIEF DESCRIPTION OF THE DRAWINGS

[0040] Figure 1 This is a schematic diagram of a loading hydraulic system for lift and drag tests of fin stabilizers according to 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 of the connection between the lift loading cylinder and the fin shaft of the present invention;

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

[0046] Among them: 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- motor, 9- first one-way valve, 10- second one-way valve, 11- electromagnetic relief valve, 12- high-pressure filter, 13- second pressure sensor, 14- pressure measuring joint, 15- pressure measuring hose, 16- first pressure gauge, 17- proportional reversing valve, 18- return oil filter, 19- cooler, 20- proportional relief valve, 21- manual reversing valve, 22- second pressure gauge, 23- lift loading cylinder, 24- resistance loading cylinder, 25- first connecting pin, 26- lift loading fin handle, 27- fin shaft, 28- first support rig, 29- first bearing, 30- second support rig, 31- resistance loading fin handle, 32- second connecting pin, 33- second bearing. DETAILED DESCRIPTION

[0047] The following embodiments of the present invention are described in further detail in conjunction with the accompanying drawings and examples. The following embodiments are only used to illustrate the present invention, but are not intended to limit the scope of the present invention.

[0048] Terms such as "upper," "lower," "left," "right," "inner," "outer," "front," "back," "head," and "tail" in this application are based on the directions or positions shown in the accompanying drawings. The corresponding positions may vary depending on the drawings, and should not be construed as limiting the scope of protection.

[0049] In the present invention, the terms "installed," "connected," "connected," "connected," "fixed," etc. should be understood in a broad sense. For example, they may refer to fixed connection, detachable connection, integral connection, mechanical connection, electrical connection, or mutual communication. They may be directly connected or indirectly connected through an intermediate medium. They may refer to internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0050] This embodiment describes a loading hydraulic system and method for lift and drag tests of fin stabilizers, which are used to perform lift and drag simulation loading tests on fin stabilizers.

[0051] like Figure 1As shown, the loading hydraulic system consists of a hydraulic unit, a lift loading cylinder 23, and a resistance loading cylinder 24. The hydraulic unit includes a hydraulic gauge 1, a liquid 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 one-way valve 9, a second one-way valve 10, an electromagnetic relief valve 11, a high-pressure filter 12, a second pressure sensor 13, a pressure measuring joint 14, a pressure measuring hose 15, a first pressure gauge 16, a proportional reversing valve 17, an oil return filter 18, a cooler 19, a proportional relief valve 20, a manual reversing valve 21, and a second pressure gauge 22.

[0052] The hydraulic pump 7 comprises a lift-loading pump 7.1 and a drag-loading pump 7.2, respectively used to apply lift and drag to the fin stabilizers. The output shaft of the motor 8 is sequentially connected to the lift-loading pump 7.1 and the drag-loading pump 7.2 via a coupling, driving the lift-loading pumps 7.1 and 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 sensing, and the drag-loading pump 7.2 is a vane pump or 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 swash plate, a control valve A, and a control valve B.

[0054] The control cylinder contains a piston with a piston rod connected to one side of the piston. The outer end of the piston rod is connected to a swash plate installed on the lift loading pump 7.1. A spring is sleeved on the piston rod. The expansion and contraction of the piston rod adjusts the angle of the swash plate, thereby adjusting the displacement of the lift loading pump 7.1.

[0055] Control valve A is a pressure control valve, equipped with a valve core and adjustment spring A. Control valve A adjusts the valve core position by adjusting the spring force of adjustment spring A, thereby setting the maximum operating pressure at the pump outlet of lift loading pump 7.1. The pump outlet of lift loading pump 7.1 is connected to port P of control valve A via a control oil circuit. Adjustment spring A applies pressure on one side of the valve core, while hydraulic oil applies pressure from the other side. 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 two function positions: a and b. Control valve A only switches to function position b when the valve core moves to the right a certain distance. Its internal oil circuit connects ports P and A, supplying hydraulic oil from the pump outlet of loading pump 7.1 directly to the rodless chamber of the control cylinder.

[0056] When the outlet pressure of lift-loading pump 7.1 does not exceed the maximum operating pressure, the high-pressure oil pressure in the valve cavity of control valve A is less than the pressure exerted on the valve core by adjusting spring A, and control valve A is in function position a. When the pump outlet pressure exceeds the maximum operating pressure, the high-pressure oil pressure in the valve cavity becomes greater than the pressure exerted on the valve core by adjusting spring A, causing the valve core of control valve A to shift right. Control valve A switches to function position b, and high-pressure oil enters the rodless chamber of the control cylinder through the oil passage within function b. The piston rod extends, minimizing the swashplate angle and reducing the output flow of lift-loading pump 7.1 to zero.

[0057] Control valve B is a flow control valve, i.e. a load-sensing valve, used to adjust the outlet flow of lift loading pump 7.1 to keep the inlet pressure drop of proportional reversing valve 17 constant. Control valve B is provided with a valve core and an adjusting spring B. The two ends of the adjusting spring B are respectively connected to the valve core and the pressure receiving end (i.e. Figure 2 The maximum spring force of regulating spring B is a preset fixed value. Under normal operating conditions, the set pressure of regulating spring B is much lower than that of regulating spring A. (For example, under typical operating conditions, the set pressure of regulating spring B for control valve B is 1.4 MPa, while the set pressure of regulating spring A for control valve A is determined by the maximum operating pressure of the loading hydraulic system, generally ranging from 10 MPa to 20 MPa, or even higher.)

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

[0059] The outlet pressure of lift-loading pump 7.1 is fed back to control valve B via the control oil circuit. The pressure exerted on the spool by control valve B's regulating spring B and the load pressure fed back to the pressure receiving end by the load act together on the right side of control valve B's spool. The high-pressure oil pressure in control valve B's valve chamber acts on the left side of control valve B's spool. When the pressures on the left and right sides of control valve B's spool are balanced, lift-loading pump 7.1 delivers stable oil. If the load pressure decreases due to load fluctuations or other factors, the pressure drop at the valve inlet increases, increasing the flow rate at the valve port. The high-pressure oil pressure on the left side of control valve B's spool exceeds the sum of the load pressure and the pressure exerted on the spool by regulating spring B, causing the spool to shift right. Control valve B switches to function B. High-pressure oil flows through the oil circuit within function B into the rodless chamber of the control cylinder, adjusting the maximum outlet flow of lift-loading pump 7.1 and reducing its displacement until the forces on the left and right sides of control valve B's spool are balanced. If the load pressure increases, control valve B automatically adjusts the outlet flow of lift loading pump 7.1 in the opposite direction. This means the valve core shifts left, switching control valve B to position a. The high-pressure oil in the rodless chamber returns to the tank through control valve B, increasing the displacement of lift loading pump 7.1. When the loading hydraulic system is stable, the pump outlet pressure exceeds the load pressure by only a fixed value, which is the pressure set by regulating spring B.

[0060] In the loading hydraulic system, the shuttle valve 5, the first pressure sensor 6, the lift loading pump 7.1, the first one-way valve 9, the electromagnetic relief valve 11, the high-pressure filter 12, the pressure measuring joint 14, the pressure measuring hose 15, the first pressure gauge 16, and the proportional reversing valve 17 constitute a lift loading circuit, while the resistance loading pump 7.2, the second one-way valve 10, the second pressure sensor 13, the pressure measuring joint 14, the pressure measuring hose 15, the proportional relief valve 20, the manual reversing valve 21, and the second pressure gauge 22 constitute a resistance loading circuit.

[0061] Proportional reversing valve 17 has an input, two outputs, and an oil return port. In the lift-loading circuit, the output of lift-loading pump 7.1 is sequentially connected to high-pressure filter 12, first check valve 9, and the input of proportional reversing valve 17. Its two outputs are connected to the rod chamber and rodless chamber pipelines of lift-loading cylinder 23, respectively. The oil return port of proportional reversing valve 17 is connected to the fuel tank via an oil return line, returning fluid to the tank.

[0062] The two output ends of the proportional reversing valve 17 are connected to the two input ends of the shuttle valve 5 through a bypass, and the output end 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 of the two output ends of the proportional reversing valve 17 to the control valve B. The control valve B, the proportional reversing valve 17, and the shuttle valve 5 work together to realize the flow control of the lift loading pump 7.1.

[0063] A first pressure sensor 6, a pressure measuring joint 14, and a first pressure gauge 16 are respectively provided between the first one-way valve 9 and the high-pressure filter 12 and at the two output ends of the proportional reversing valve 17, and the pressure measuring joint 14 is connected to the first pressure gauge 16 through a pressure measuring hose 15. Figure 3 As shown, the first pressure sensor 6 and the first pressure gauge 16 can monitor the fluid pressure in real time, and the first pressure sensor 6 feeds the monitored pressure back to the loading control unit while monitoring the fluid pressure. The loading control unit calculates the applied lift and compares it with the lift loading target value. The proportional reversing valve 17 is controlled according to the deviation value until the lift loading pressure reaches the control target value, and the valve port of the proportional reversing valve 17 is closed, forming a lift loading pressure closed-loop control system to achieve control of the loading pressure and thus accurately control the loading lift. In this embodiment, the first pressure sensor 6 #1 is used to monitor the lift loading circuit pump source outlet pressure P in real time. s1 , 1# first pressure gauge 16 is used to monitor the pump source outlet pressure P in real time s1 , 2# first pressure sensor 6 is used to monitor the load pressure P on the output side (i.e., lift loading circuit X1 side) of proportional reversing valve 17X1 in real time a ,2# first pressure gauge 16 is used to monitor the load pressure P in real time a , 3# first pressure sensor 6 is used to monitor the load pressure P on the output side (i.e., lift loading circuit X2 side) of proportional reversing valve 17X2 in real time b , 3# first pressure gauge 16 is used to monitor the load pressure P in real time b .

[0064] The loading hydraulic system of this embodiment can make the Figure 2 The pressure at point m is always equal to the load pressure P a With load pressure P b The medium pressure with higher pressure is connected, and the load pressure P a With load pressure P b The higher of the two pressures (i.e., the pressure at point m) is fed back to point n behind the control valve B of the lift loading pump 7.1 through the shuttle valve 5. The lift loading pump 7.1 controls the oil flow rate according to the received pressure.

[0065] The valve inlet pressure drop ΔP on the proportional reversing valve 17: (1) When P a >P b When ΔP=P s1 -P a ; (2) When P b >P a When ΔP=P s1 -P b .

[0066] When the valve core of control valve B is under balanced force, the spring force of regulating spring B / valve core effective area = pump outlet pressure P s1 -Load pressure P a With P b The higher of the medium pressure = proportional reversing valve inlet pressure drop ΔP, the valve inlet pressure drop ΔP is pre-set by the regulating spring B of the control valve B and is a preset constant. During the loading test, the proportional reversing valve 17 inlet pressure drop ΔP is a fixed value. When the valve port of the proportional reversing valve 17 is fixed, the flow through the proportional reversing valve 17 is a constant value, and no matter how the valve port opening changes, the pump outlet pressure P s1 The pump outlet pressure is only a fixed value higher than the load pressure. Within the maximum pressure limit of 7.1 of the lift loading pump, the pump outlet pressure can always automatically adapt to load changes and always operate under conditions that match the load function, achieving significant energy-saving effects.

[0067] The electromagnetic relief valve 11 serves as a safety valve for the lift loading circuit, limiting the maximum pressure within it. It is located between the lift loading pump 7.1 and the high-pressure filter 12. Its outlet is connected to the oil return line, returning any excess fluid to the tank. When the loading hydraulic system is activated, the solenoid valve on the electromagnetic relief valve 11 is de-energized, placing the loading hydraulic system in an unloaded state. When the motor 8 is activated, the solenoid valve on the electromagnetic relief valve 11 is energized, placing the loading hydraulic system in a loaded state.

[0068] In the resistance loading circuit, the output of the resistance loading pump 7.2, the second one-way valve 10, and the input of the manual reversing valve 21 are sequentially connected by pipelines. The output of the resistance loading pump 7.2 is connected to the return oil pipeline via a proportional relief valve 20. The two outputs of the manual reversing valve 21 are respectively connected to the rod chamber and rodless chamber pipelines of the resistance loading cylinder 24. The return oil end of the manual reversing valve 21 is connected to the oil tank via a return oil pipeline to return fluid to the tank. Because the fin shaft moves up and down under the loading lift, if the loading resistance is a tensile force, the loading resistance can be ensured to act near the equilibrium position during resistance loading. If the loading resistance is a thrust force, the loading resistance will deviate from the equilibrium position as the fin shaft moves up and down under the loading lift, and the deviation will become increasingly larger. Therefore, during the loading process, the resistance loading cylinder 24 only applies a tensile force to the fin stabilizer axial force. That is, during resistance loading, the cylinder piston rod is retracted.

[0069] A second pressure sensor 13 is provided at each of the two output ends of the manual reversing valve 21 and the front end of the proportional relief valve 20. The second pressure sensor 13 is used to monitor the load pressure P at the output side of the manual reversing valve 21X3 (i.e., the resistance loading circuit X3 side) in real time. c , 2# second pressure sensor 13 is used to monitor the load pressure P on the output side of the manual reversing valve 21X4 (output side of the resistance loading circuit X4) in real time d, 3# second pressure sensor 13 is used to monitor the resistance loading circuit pump source outlet pressure P 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 resistance loading target value, and controls the proportional relief valve 20 according to the deviation value until the resistance loading circuit reaches the resistance loading target value.

[0070] In order to facilitate on-site real-time observation of the pump source outlet pressure, this embodiment is further provided with a pressure measuring joint 14 in the front end pipeline of the proportional relief valve 20. The top end of the pressure measuring joint 14 is connected to a second pressure gauge 22 via a pressure measuring hose 15. The pump source outlet pressure can be monitored in real time via the second pressure gauge 22.

[0071] In this embodiment, a return oil filter 18 and a cooler 19 are installed on the return oil line. The oil passes through the cooler 19 and the return oil filter 18 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 its temperature.

[0072] The hydraulic 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. The level gauge 1 is used to monitor the oil level in the tank. The level control relay 2 monitors the oil level and provides 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 to protect it. The temperature relay 3 monitors the oil temperature in the tank and provides feedback to the loading control unit. When the set high temperature is reached, the loading control unit triggers an alarm and stops the loading hydraulic system to protect it. The air filter 4 filters impurities and dust from the air entering the tank to ensure the cleanliness of the loading hydraulic system.

[0073] When the loading hydraulic system of this embodiment loads the fin stabilizer, the rod cavity (Y1 port) of the lift loading cylinder 23 is connected to the hydraulic unit output port X1, the rodless cavity (Y2 port) of the lift loading cylinder 23 is connected to the hydraulic unit output port X2, the rod cavity (Y3 port) of the resistance loading cylinder 24 is connected to the hydraulic unit output port X3, and the rodless cavity (Y4 port) of the resistance loading cylinder 24 is connected to the hydraulic unit output port X4. The loading process is as follows:

[0074] 1. If Figure 5As shown, the lift-loading cylinder 23 is installed on the loading platform below the fin shaft 27 through the first supporting platform 28 with the piston rod in a vertically upward posture, and the earring at the piston rod end of the lift-loading cylinder 23 is connected to the lift-loading fin handle 26 through the first connecting pin 25. The lift-loading fin handle 26 is sleeved on the fin shaft 27 of the loaded anti-roll fin, and a first bearing 29 is provided between the lift-loading fin handle 26 and the fin shaft 27. The action force of the lift-loading cylinder 23 is transmitted to the lift-loading fin handle 26 through the first connecting pin 25, and the lift-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 installed on the loading platform through the second support platform 30 with the piston rod in a horizontal posture, that is, the resistance loading cylinder 24 is perpendicular to the axial direction of the lift loading cylinder 23, and the earring at the piston rod end of the resistance loading cylinder 24 is connected to the resistance loading fin handle 31 through the second connecting pin 32, the resistance loading fin handle 31 is sleeved on the fin shaft 27 of the loaded anti-roll fin, and a second bearing 33 is provided between the fin shaft 27 and the resistance loading fin handle 31, the action force of the resistance loading cylinder 24 is transmitted to the resistance loading fin handle 31 through the second connecting pin 32, and the resistance loading fin handle 31 applies the loading resistance to the fin shaft 27.

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

[0077] 3. The lift loading pump 7.1 pumps hydraulic oil through the high-pressure filter 12 and the first one-way valve 9 to the proportional reversing valve 17.

[0078] The loading control unit controls the operation of the proportional reversing valve 17. When the proportional reversing valve 17 is switched to the left functional position, hydraulic oil enters the rod chamber of the lift loading cylinder 23 through the loading oil line X1, providing a vertical downward lift for the fin shaft. When the proportional reversing valve 17 is switched to the right functional position, hydraulic oil enters the rodless chamber of the lift loading cylinder 23 through the loading oil line X2, providing a vertical upward lift for the fin shaft.

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

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

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

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

[0083] 5. While the lift loading pump 7.1 is operating, the resistance loading pump 7.2 supplies hydraulic oil to the manual reversing valve 21 through the second one-way valve 10.

[0084] When the loading hydraulic system operates normally, when the manual reversing 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 a retracted state, applying resistance loading to the fin axis of the stabilizer fin. 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 1# and 2# second pressure sensors 13 respectively monitor the load pressure P on the resistance loading circuit X3 side 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, and the loading control unit calculates the applied resistance loading force.

[0086] Resistance loading force F 阻 =P c A3-P d A4, where: A3 is the rod cavity area of the resistance loading cylinder 24, and A4 is the rodless cavity area 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 reversing valve 21 is switched to the intermediate functional position, the resistance loading circuit is unloaded.

[0089] 8. When the manual reversing valve 21 is switched to the functional position "b", the piston rod of the resistance loading cylinder 24 extends, making it easier to adjust the position of the cylinder piston rod.

[0090] Although the principles of the present invention have been described in detail above in conjunction with the preferred embodiments of the present invention, those skilled in the art should understand that the above embodiments are merely illustrative 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. Without departing from the spirit and scope of the present invention, any obvious changes such as equivalent transformations and simple substitutions based on the technical solution of the present invention fall within the scope of protection of the present invention.

Claims

1. A loading hydraulic system for fin stabilizer lift and drag tests, characterized in that: The loading hydraulic system includes a hydraulic unit, a lift loading cylinder (23), and a resistance loading cylinder (24); The hydraulic unit comprises a lift loading circuit and a resistance loading circuit; the lift loading circuit comprises a lift loading pump (7.1) with a load-sensing function; the resistance loading circuit comprises a resistance loading pump (7.2); the output shaft of the motor (8) is sequentially connected to the lift loading pump (7.1) and the resistance loading pump (7.2); the lift loading pump (7.1) and the resistance loading pump (7.2) rotate synchronously under the drive of the motor (8), and provide hydraulic oil to the lift loading circuit and the resistance loading circuit respectively; The two output ends of the lift loading circuit are connected to the two input ends of the shuttle valve (5) through a bypass, and the output end of the shuttle valve (5) is connected to the lift loading pump (7.1); the shuttle valve (5) is connected to the output end with high load pressure in the lift loading circuit, and feeds back the high load pressure to the lift loading pump (7.1); the two output ends of the lift loading circuit are respectively connected to the rod chamber and rodless chamber pipelines of the lift loading cylinder (23) through the main pipeline; the lift loading cylinder (23) is connected to the fin shaft of the loaded fin stabilizer with the piston rod in a vertically upward posture, providing lift for the fin shaft; The two output ends of the resistance loading circuit are respectively connected to the rod chamber and rodless chamber pipelines of the resistance loading oil cylinder (24); the resistance loading oil cylinder (24) is connected to the fin shaft with the piston rod in a horizontal posture to provide resistance for the fin shaft.

2. The loading hydraulic system for fin stabilizer lift and drag test according to claim 1, characterized in that: The lift loading circuit further includes a first pressure sensor (6) and a proportional reversing valve (17); The output end of the lift loading pump (7.1) is connected to the input end pipeline of the proportional reversing valve (17), the two output ends of the proportional reversing valve (17) are respectively connected to the rod chamber and rodless chamber pipelines of the lift loading oil cylinder (23), and the oil return end of the proportional reversing valve (17) is connected to the oil tank through the oil return pipeline; The first pressure sensor (6) is respectively installed at the two output ends of the proportional reversing valve (17) for respectively monitoring the load pressures at the two output ends of the lift loading circuit in real time and feeding back the monitored load pressures to the loading control unit; the first pressure sensor (6) is provided at the output end of the lift loading pump (7.1) for monitoring the pump source outlet pressure of the lift loading pump (7.1) in real time and feeding back the pump source outlet pressure to the loading control unit; The two output ends of the proportional reversing valve (17) are connected via the shuttle valve (5), and the shuttle valve (5) is connected to the lift loading pump (7.1), and the shuttle valve (5) is connected to the output end of the proportional reversing valve (17) with high load pressure.

3. The loading hydraulic system for fin stabilizer lift and drag test according to claim 2, characterized in that: The lift loading circuit further comprises a high-pressure filter (12) and a first one-way valve (9); the output end of the lift loading pump (7.1), the high-pressure filter (12), the first one-way valve (9), and the input end of the proportional reversing valve (17) are sequentially connected by pipelines.

4. The loading hydraulic system for fin stabilizer lift and drag test according to claim 2, characterized in that: The lift loading circuit further comprises a pressure measuring joint (14), a pressure measuring hose (15), and a first pressure gauge (16); the pressure measuring joint (14) is respectively installed at the output end of the lift loading pump (7.1) and the two output ends of the proportional reversing valve (17); the pressure measuring joint (14) is connected to the first pressure gauge (16) via the pressure measuring hose (15); and the pump source outlet pressure of the lift loading pump (7.1) and the load pressure at the two output ends of the lift loading circuit are respectively observed in real time via the first pressure gauge (16).

5. The loading hydraulic system for fin stabilizer lift and drag test according to claim 1, characterized in that: The lift loading circuit further comprises an electromagnetic overflow valve (11); the output end of the lift loading pump (7.1) is connected to the oil return pipeline via the electromagnetic overflow valve (11).

6. The loading hydraulic system for fin stabilizer lift and drag test according to claim 1, characterized in that: The resistance loading circuit further includes a second pressure sensor (13), a proportional relief valve (20), and a manual reversing valve (21); The output end of the resistance loading pump (7.2) is connected to the input end pipeline of the manual reversing valve (21), and the output end of the resistance loading pump (7.2) is connected to the oil return pipeline through 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 oil cylinder (24), and the oil return end of the manual reversing valve (21) is connected to the oil tank through the oil return pipeline; The second pressure sensors (13) are respectively installed at the two output ends of the manual reversing valve (21) and the output end of the resistance loading pump (7.2), for respectively monitoring the load pressures at the two output ends of the resistance loading circuit and the pump source outlet pressure of the resistance loading pump (7.2) in real time, and feeding back the pressures to the loading control unit.

7. The loading hydraulic system for fin stabilizer lift and drag test according to claim 1, characterized in that: A pressure measuring joint (14) is installed at the front end of the proportional relief valve (20). The pressure measuring joint (14) is connected to a second pressure gauge (22) via a pressure measuring hose (15). The pump source outlet pressure of the resistance loading pump (7.2) can be observed in real time via the second pressure gauge (22).

8. A hydraulic method for loading lift resistance of fin stabilizers, characterized in that: The method for performing a fin stabilizer lift and drag loading test using a loading hydraulic system for a fin stabilizer lift and drag test according to any one of claims 1 to 7 comprises the following steps: S1, the lift loading cylinder (23) is connected to the fin shaft of the loaded fin stabilizer with its piston rod in a vertical upward posture; the resistance loading cylinder (24) is connected to the fin shaft of the loaded fin stabilizer with its piston rod in a horizontal posture; S2, after the motor (8) is started, it drives the lift loading pump (7.1) and the resistance loading pump (7.2) to operate synchronously; S3, the lift loading pump (7.1) pumps hydraulic oil through the high-pressure filter (12) and the first one-way valve (9) to the proportional reversing valve (17); the lift loading pump (7.1) provides vertical upward and downward lift for the fin shaft, and the loading control unit controls the proportional reversing valve (17) to switch the functional position and change the lift direction; S4, during the lift loading process, the load pressure P on the lift loading circuit X1 side 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, and the loading control unit calculates the applied lift loading force; The loading control unit controls the proportional reversing valve (17) to adjust the valve opening size according to the calculated deviation between the lift loading force and the lift loading target value, and closes the valve opening of the proportional reversing valve (17) after the lift loading pressure reaches the lift loading target value; S5. While the lift loading pump (7.1) is operating, the resistance loading pump (7.2) supplies hydraulic oil to the manual reversing valve (21) through the second one-way valve (10); When the manual reversing 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 a retracted state, and the resistance loading is applied to the fin shaft; S6. During the resistance loading process, the load pressure P on the resistance loading circuit X3 side is monitored in real time by the second pressure sensor (13). c and the load pressure P on the X4 side d and feeds back the load pressure to the loading control unit, which 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 value between the calculated resistance loading force and the resistance loading target value, until the loading hydraulic system reaches the resistance loading target value.

9. The hydraulic method for loading lift resistance of fin stabilizers according to claim 8, characterized in that: In step S4, the lift loading force is calculated according to the following formula: When the piston rod of the lift loading cylinder (23) extends, the lift loading force F 升 =P b A2-P a A1, where: A1 is the area of the rod cavity of the lift loading cylinder (23), and A2 is the area of the rodless cavity of the lift loading cylinder (23); When the piston rod of the lift loading cylinder (23) is retracted, the lift loading force F 升 =P a A1-P b A2.

10. The hydraulic method for loading lift resistance of fin stabilizers according to claim 8, 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 cavity of the resistance loading cylinder (24), and A4 is the area of the rodless cavity of the resistance loading cylinder (24).

Images