Energy-saving fin stabilizer fin rotating control system based on single-piston-rod double-acting oil cylinder

Abstract

The invention relates to an energy-saving fin stabilizer fin rotating control system based on a single-piston-rod double-acting oil cylinder, and belongs to the technical field of ship stabilization, and the fin stabilizer fin rotating control system comprises a fin rotating execution mechanism and a fin rotating hydraulic mechanism; the fin rotating executing mechanism comprises a single-rod double-acting oil cylinder, a fin handle and a fin shaft; the fin rotating hydraulic mechanism comprises a hydraulic oil source, an electro-hydraulic proportional direction valve and a one-way valve; an oil outlet of the hydraulic oil source is connected with an input port pipeline of the electro-hydraulic proportional direction valve; a first output port and a second output port of the electro-hydraulic proportional direction valve are respectively connected with a rodless cavity and a rod cavity pipeline of the single-rod double-acting oil cylinder, and the rod cavity is connected with an input port pipeline of the electro-hydraulic proportional direction valve through a one-way valve; an oil return opening of the electro-hydraulic proportional direction valve is connected with the oil tank; a hydraulic oil source supplies oil to a rodless cavity or a rod cavity of the single-rod double-acting oil cylinder through the electro-hydraulic proportional direction valve, and the fin shaft is driven to rotate. On the premise that the control precision is met, the size, power and cost of the fin stabilizer device are effectively reduced.

Description

Technical Field

[0001] This invention relates to the field of ship roll reduction technology, specifically to an energy-saving roll-damping fin control system based on a single-acting double-rod hydraulic cylinder. Background Technology

[0002] Ship roll damping fins are used to reduce the severity of ship rolling and are integrated mechanical, electrical, hydraulic, and fluid systems. The fin rotation movement of the roll damping fin device is achieved through a fin rotation control system. The system control loop mainly consists of a servo controller, a fin rotation hydraulic mechanism (including electro-hydraulic servo valves, etc.), a fin rotation actuator (including fin rotation cylinders, etc.), and a fin angle transmitter. For example... Figure 1 As shown, the control principle of the anti-roll fin and fin-spinning control system is as follows:

[0003] The anti-roll fin device detects the ship's rolling motion through sensors, and the top controller calculates and generates a fin-turning command signal U. αi The fin control system receives the fin-turning command signal U from the controller. αi And the fin-turning command signal U is amplified by the servo controller. αi The servo valve changes its valve core opening according to the fin rotation command, thereby controlling the flow rate Q and direction of the pressure oil entering the fin rotation mechanism (fin cylinder), causing the fin to produce corresponding fin rotation movement. The fin rotation angle signal is fed back to the servo controller via the fin angle transmitter, forming a position closed loop, thereby controlling the fin rotation angle.

[0004] like Figure 2 As shown, a fin-rotating actuator comprises a double-rod fin-rotating cylinder 1, an clevis 2, a fin handle pin 3, a fin handle 4, a key 5, a fin shaft 6, and a hinge shaft 8. The double-rod fin-rotating cylinder 1 is mounted on the relevant support parts of the anti-roll fin via the hinge shaft 8. The clevis 2, mounted on the lower end of the piston rod of the double-rod fin-rotating cylinder 1, is hinged to the fin handle 4 via the fin handle pin 3. The fin handle 4 is connected to the fin shaft 6 via the key 5. The fin shaft 6 drives the fin 7 to rotate via the connection. The piston rod of the double-rod fin-rotating cylinder 1 reciprocates linearly and oscillates around the hinge shaft 8, thereby driving the fin handle 4 and the fin shaft 6 to achieve reciprocating fin rotation.

[0005] like Figure 3 The illustrated rotary fin hydraulic mechanism consists of a double-rod rotary fin cylinder 1, a hydraulic oil source 9, and an electro-hydraulic servo valve 10. The double-rod rotary fin cylinder 1 drives the fin shaft 6 to rotate, thus achieving the rotary fin movement. The rotary fin hydraulic mechanism uses the electro-hydraulic servo valve 10 as the control valve to control the flow rate and direction of the oil entering the double-rod rotary fin cylinder 1, thereby controlling the rotary fin movement. Since the rotary fin hydraulic mechanism using the electro-hydraulic servo valve 10 requires that the two chamber areas of the rotary fin cylinder 1 be equal, traditional rotary fin actuators use a double-rod symmetrical rotary fin cylinder 1 as the actuator.

[0006] The aforementioned fin control system uses an electro-hydraulic servo valve 10 to control a double-rod symmetrical fin-rotating cylinder 1, which is a valve-controlled cylinder structure. The double-rod fin-rotating cylinder 1 essentially functions as a servo cylinder. To facilitate precise control, the two chamber areas of the double-rod fin-rotating cylinder 1 are generally required to be equal. However, only the lower end of the piston rod of the double-rod fin-rotating cylinder 1 carries the load; the upper piston rod is unnecessary from a load-bearing perspective. This unnecessary length increases the space occupied by the anti-roll fin device, thus increasing its height. For anti-roll fin devices, a type of marine equipment, which are often installed in the confined space at the bottom of the hull, a large height requirement will reduce the suitability of the anti-roll fin device for installation on the ship, or even make installation impossible.

[0007] To address the drawback of the large height space occupied by the double-acting fin-rotating cylinder 1, single-acting symmetrical servo cylinder designs have also been developed, such as the double-acting single-acting symmetrical hydraulic cylinder disclosed in CN110513350A. This reduces the overall height, thus achieving the goal of lowering the height of the anti-roll fin device. However, this double-acting single-acting symmetrical hydraulic cylinder consists of a top end cap, cylinder barrel, hollow piston rod, internal oil pipe, piston, and bottom end cap, resulting in a complex structure, numerous kinematic pairs, high precision requirements, and difficulties in manufacturing and maintenance, leading to high costs. Furthermore, its large radial dimension places significant demands on the overall radial space required of the ship.

[0008] Therefore, there is an urgent need for a relatively small, simple, and low-cost anti-roll fin control system to improve the adaptability of anti-roll fin devices. Summary of the Invention

[0009] To address the needs of the prior art, this invention provides an energy-saving anti-roll fin control system based on a single-acting double-rod hydraulic cylinder. Through a novel fin-rotating actuator and a fin-rotating hydraulic control circuit, it uses a common single-acting double-rod hydraulic cylinder for fin rotation, which not only meets the control accuracy requirements and reduces the cylinder height, but also reduces energy consumption and cost.

[0010] To achieve the above objectives, the present invention provides the following technical solution:

[0011] An energy-saving anti-roll fin and fin-rotating control system based on a single-rod double-acting hydraulic cylinder, the anti-roll fin and fin-rotating control system includes a fin-rotating actuator and a fin-rotating hydraulic mechanism;

[0012] The rotating fin actuator includes a single-rod double-acting hydraulic cylinder, a fin handle, and a fin shaft; the piston rod of the single-rod double-acting hydraulic cylinder is connected to the fin shaft through the fin handle;

[0013] The rotary fin hydraulic mechanism includes a hydraulic oil source, an electro-hydraulic proportional directional valve, and a check valve; the oil outlet of the hydraulic oil source is connected to the input port of the electro-hydraulic proportional directional valve; the first and second output ports of the electro-hydraulic proportional directional valve are respectively connected to the rodless chamber and the rod chamber of the single-rod double-acting cylinder, and the rod chamber is connected to the input port of the electro-hydraulic proportional directional valve via the check valve; the return port of the electro-hydraulic proportional directional valve is connected to the oil tank.

[0014] The hydraulic oil source supplies oil to the rodless chamber or the rod chamber of the single-rod double-acting cylinder through the electro-hydraulic proportional directional valve, thereby driving the fin shaft to rotate.

[0015] Furthermore, the piston rod is only installed in the rod chamber of the single-rod double-acting hydraulic cylinder, and the effective working area of ​​the rodless chamber is twice the effective working area of ​​the rod chamber.

[0016] Furthermore, when the anti-roll fin rotation control system controls the single-acting cylinder with a single rod to rotate the anti-roll fin via the rotation hydraulic mechanism, the output flow rate Q of the hydraulic oil source is... p =Q b , where Q b This refers to the required flow rate of working oil in the rod chamber of a single-rod double-acting hydraulic cylinder.

[0017] Furthermore, the electro-hydraulic proportional directional valve has the function of being suitable for differential circuit connection.

[0018] Furthermore, the electro-hydraulic proportional directional valve is switched to the functional Y position, and the input port of the electro-hydraulic proportional directional valve is connected to the first output port; the hydraulic oil source supplies oil to the rodless chamber of the single-rod double-acting cylinder through the electro-hydraulic proportional directional valve; the piston rod of the single-rod double-acting cylinder extends outward to realize the forward rotation of the fin actuator; the oil in the rod chamber flows through the check valve to the output oil circuit of the hydraulic oil source, and then flows through the electro-hydraulic proportional directional valve to the rodless chamber.

[0019] Furthermore, the electro-hydraulic proportional directional valve is switched to the functional X position, the input port of the electro-hydraulic proportional directional valve is connected to the second output port, and the first output port is connected to the return port; the hydraulic oil source supplies oil to the rod chamber of the single-rod double-acting cylinder through the electro-hydraulic proportional directional valve, the piston rod of the single-rod double-acting cylinder retracts, realizing the reverse rotation of the fin actuator; the oil in the rodless chamber returns through the electro-hydraulic proportional directional valve.

[0020] Furthermore, the piston rod of the single-rod double-acting hydraulic cylinder is hinged to one end of the fin handle via a fin handle pin, and the other end of the fin handle is connected to the fin shaft.

[0021] Furthermore, the single-acting double-acting hydraulic cylinder is supported on the support component of the anti-roll fin via a hinge shaft.

[0022] Furthermore, the fin shank is connected to the fin shaft by a key and bolts.

[0023] This invention also discloses a method for controlling the rotation of a roll-damping fin. This method is implemented using the energy-saving roll-damping fin control system based on a single-rod double-acting hydraulic cylinder as described above, wherein the effective working area A1 of the rodless chamber of the single-rod double-acting hydraulic cylinder is equal to twice the effective working area A2 of the rod chamber. The process is as follows:

[0024] When the anti-roll fin is controlled to rotate forward, the electro-hydraulic proportional directional valve switches to the functional Y position, and the input port of the electro-hydraulic proportional directional valve is connected to the first output port; the hydraulic oil source supplies oil to the rodless chamber of the single-rod double-acting cylinder through the electro-hydraulic proportional directional valve, the piston rod of the single-rod double-acting cylinder extends, and the fin shaft drives the anti-roll fin to rotate forward; the oil in the rod chamber of the single-rod double-acting cylinder returns to the output oil circuit of the hydraulic oil source through the check valve, and together with the oil output by the hydraulic oil source, it supplies oil to the rodless chamber of the single-rod double-acting cylinder through the electro-hydraulic proportional directional valve;

[0025] During the forward fin rotation process, the working oil flow rate Q in the rodless chamber of the single-rod double-acting hydraulic cylinder is... a =Q p +Q b , where Q p Q is the output flow rate of the hydraulic oil source. b This refers to the working oil flow rate in the rod chamber of a single-rod double-acting hydraulic cylinder; because Q a =2Q b Then Q p =Q b The equivalent working area of ​​the high-pressure oil in a single-rod double-acting cylinder is equal to A2.

[0026] When controlling the anti-roll fin to rotate in the opposite direction, the electro-hydraulic proportional directional valve switches to the X position, with the input port connected to the second output port and the first output port connected to the return port. The hydraulic oil source supplies oil to the rod chamber of the single-rod double-acting cylinder through the electro-hydraulic proportional directional valve. The piston rod of the single-rod double-acting cylinder retracts, realizing the reverse rotation of the anti-roll fin. The oil in the rodless chamber flows back into the oil tank through the return port of the electro-hydraulic proportional directional valve. The output flow rate Q of the hydraulic oil source... p =Q b The equivalent working area of ​​the high-pressure oil in a single-rod double-acting cylinder is A2.

[0027] The beneficial effects of this invention are:

[0028] The present invention relates to an energy-saving anti-roll fin control system based on a single-acting double-acting cylinder. It adopts a common single-acting double-acting cylinder and a fin-turning hydraulic mechanism with a differential proportional control loop. Compared with the existing anti-roll fin control system, the present invention simplifies the system structure, reduces the system size, lowers the required power and cost, and improves the adaptability of the anti-roll fin device while meeting the control accuracy requirements. This allows more ships to be equipped with anti-roll fin devices.

[0029] This invention solves the control problem caused by the asymmetry between the areas of the rodless and rod chambers by setting the effective working area of ​​the piston rod in the rodless chamber of the single-rod double-acting cylinder to twice that in the rod chamber, and by using a rotary fin hydraulic control circuit based on a differential electro-hydraulic proportional directional valve. This ensures that the working area of ​​the high-pressure hydraulic fluid in the single-rod double-acting cylinder is equal when the piston rod extends and retracts, thus resolving the issue of the asymmetry between the areas of the rodless and rod chambers. Furthermore, this invention, through differential proportional control, reduces the hydraulic oil flow rate required for the rotary fin hydraulic mechanism to half, significantly reducing system power.

[0030] When controlling the anti-roll fin to rotate in the forward direction, the oil in the rod chamber of the single-rod double-acting cylinder does not return to the oil tank, but instead returns to the input port of the electro-hydraulic proportional directional valve through a one-way valve, continuing to supply oil to the rodless chamber of the single-rod double-acting cylinder. This reduces the hydraulic oil output flow, reduces the overall energy consumption of the system, and also helps to reduce the size and power of the fin-rotating hydraulic mechanism.

[0031] This invention uses a common single-rod double-acting hydraulic cylinder as the fin-turning cylinder, which reduces the cylinder's height space requirement by at least 2 times compared to a double-rod hydraulic cylinder, thus improving the system's adaptability. Attached Figure Description

[0032] Figure 1 This is a block diagram of a typical fin control system for anti-roll fins;

[0033] Figure 2 A schematic diagram of a typical existing rotary fin actuator;

[0034] Figure 3 A schematic diagram of a typical existing rotary fin hydraulic mechanism;

[0035] Figure 4 This is a block diagram illustrating the principle of the energy-saving anti-roll fin and fin-rotating control system based on a single-rod double-acting hydraulic cylinder of the present invention.

[0036] Figure 5 This is a schematic diagram of the rotating fin actuator of the present invention;

[0037] Figure 6 This is a schematic diagram of the rotating fin hydraulic mechanism of the present invention;

[0038] Figure 7This is a schematic diagram of the oil circuit connection of the rotating fin hydraulic mechanism of the present invention when the piston rod of the oil cylinder extends (forward rotating fin);

[0039] Figure 8 This is a schematic diagram of the oil circuit connection of the rotating fin hydraulic mechanism of the present invention when the cylinder piston rod retracts (reverse fin rotation);

[0040] Figure 9 This is a schematic diagram of a hydraulic mechanism for reducing swaying fins and rotating fins, in comparison with the present invention.

[0041] Among them: 1-Double rod rotating fin cylinder, 2-Earring, 3-Fin shank pin, 4-Fin shank, 5-Key, 6-Fin shaft, 7-Fin, 8-Hinge shaft, 9-Hydraulic oil source, 10-Electro-hydraulic servo valve, 11-Single rod double-acting cylinder, 111-Piston rod, 112-Rodless chamber, 113-Rod chamber, 12-Electro-hydraulic proportional directional valve, 13-Check valve, 14-Asymmetrical valve port electro-hydraulic proportional directional valve. Detailed Implementation

[0042] 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.

[0043] 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.

[0044] 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.

[0045] This embodiment describes an energy-saving anti-roll fin control system based on a single-rod double-acting hydraulic cylinder, which effectively reduces the size, power, and cost of the anti-roll fin device while meeting control accuracy requirements.

[0046] The anti-roll fin and fin-rotation control system adopts Figure 4 The control principle shown controls the fin rotation, which mainly consists of a proportional controller, a fin rotation actuator, a fin rotation hydraulic mechanism, and a fin angle transmitter. In this embodiment, the fin rotation actuator adopts a single-rod double-acting hydraulic cylinder 11 (see...). Figure 5As an actuator, the rotary fin hydraulic mechanism adopts a novel rotary fin hydraulic control circuit. The rotary fin hydraulic mechanism controls the flow and direction of high-pressure oil entering the single-rod double-acting cylinder 11 to control the piston rod movement of the single-rod double-acting cylinder 11, thereby achieving rotary fin movement control.

[0047] like Figure 5 As shown, in this embodiment, the rotating fin actuator consists of a single-rod double-acting hydraulic cylinder 11, a fin handle 4, and a fin shaft 6. The single-rod double-acting hydraulic cylinder 11 includes a piston rod 111, a rodless chamber 112, and a rod chamber 113. The piston rod 111 is installed only in the rod chamber 113. An earring 2 is connected to the end of the piston rod 111. The earring 2 is hinged to one end of the fin handle 4 via a fin handle pin 3. The other end of the fin handle 4 is mounted on the fin shaft 6 and connected to the fin shaft 6 via a key 5, bolts, etc. The single-rod double-acting hydraulic cylinder 11 is supported on the support components (such as a rotating body) of the anti-roll fin via a hinge shaft 8. When the piston rod 111 in the single-rod double-acting hydraulic cylinder 11 reciprocates linearly, the single-rod double-acting hydraulic cylinder 11 oscillates around the hinge shaft 8, thereby driving the fin handle 4 and the fin shaft 6 to rotate, thus achieving the reciprocating rotation of the fin. In this embodiment, a single-rod double-acting hydraulic cylinder 11 is used for fin rotation, which requires at least twice the hydraulic cylinder working stroke compared to a double-rod fin rotation hydraulic cylinder.

[0048] In this embodiment, the high-pressure oil in the single-rod double-acting cylinder 11 has an effective action area A1 in the rodless chamber 112 and an effective action area A2 in the rod chamber 113, and A1 = 2A2.

[0049] like Figure 6 As shown, in this embodiment, the rotary fin hydraulic mechanism consists of a hydraulic oil source 9, an electro-hydraulic proportional directional valve 12, and a check valve 13. In order to solve the control problem caused by the asymmetry of the areas of the rodless chamber 112 and the rod chamber 113, the electro-hydraulic proportional directional valve 12 has the function of being suitable for differential circuit connection and has an input port (i.e., P port), a first output port (i.e., A port), a second output port (i.e., B port), and a return port (i.e., T port).

[0050] The outlet of the hydraulic oil source 9 is connected to the input pipeline of the electro-hydraulic proportional directional valve 12. The first and second output ports of the electro-hydraulic proportional directional valve 12 are respectively connected to the connection port J1 of the rodless chamber 112 and the connection port J2 of the rod chamber 113 of the single-rod double-acting cylinder 11. At the same time, the rod chamber 113 is also connected to the input pipeline of the electro-hydraulic proportional directional valve 12 through the check valve 13. That is, the second output port of the electro-hydraulic proportional directional valve 12 is connected to the parallel rod chamber 113 and check valve 13 pipelines. The outlet of the check valve 13 is connected to the input pipeline of the electro-hydraulic proportional directional valve 12. The return port of the electro-hydraulic proportional directional valve 12 is connected to the oil tank, forming the return pipeline of the anti-roll fin control system.

[0051] When the anti-roll fin control system controls the operation of the anti-roll fin, the output flow rate of hydraulic oil source 9 is Q. p The working oil flow rate of the rodless chamber 112 of the single-rod double-acting hydraulic cylinder 11 is Q. a The working oil flow rate of the rod chamber 113 of the single-rod double-acting hydraulic cylinder 11 is Q. b The electro-hydraulic proportional directional valve 12 includes a functional X position, a functional Y position, and a functional Z position.

[0052] When the anti-roll fin rotation control system controls the anti-roll fin to rotate in the forward direction, the electro-hydraulic proportional directional valve 12 switches to the functional Y position, such as... Figure 6 and Figure 7 As shown, the input port of the electro-hydraulic proportional directional valve 12 is connected to the first output port (i.e., connecting port P and port A). At this time, a differential proportional control circuit is formed in the fin-rotating hydraulic mechanism, and the single-rod double-acting cylinder 11 becomes a differential cylinder. The hydraulic oil source 9 supplies oil to the rodless chamber 112 of the single-rod double-acting cylinder 11 through the electro-hydraulic proportional directional valve 12. The piston rod 111 of the single-rod double-acting cylinder 11 extends outward and drives the fin shaft 6 to rotate counterclockwise through the fin handle 4. The fin shaft 6 drives the anti-roll fin to rotate clockwise. The oil in the rod chamber 113 returns to the output oil circuit of the hydraulic oil source 9 through the check valve 3, and together with the oil output by the hydraulic oil source 9, it supplies oil to the rodless chamber 112 of the single-rod double-acting cylinder 11 through the electro-hydraulic proportional directional valve 12. This differential circuit connection method can reduce the output flow of the hydraulic oil source 9.

[0053] During the forward fin rotation process, the working oil flow rate Q in the rodless chamber 112 is... a =Q p +Q b Since the effective working area A1 of the rodless chamber 112 and the effective working area A2 of the rod chamber 113 are in the relationship A1:A2 = 2:1, and since the general formula for calculating oil flow rate Q is Q = A × v, where A is the effective working area and v is the piston speed, then Q... a =2Q b Therefore, the hydraulic oil source 9 required for the anti-roll fin and fin-rotating control system has an output flow rate Q. p =Q b At this time, the equivalent working area of ​​the high-pressure oil in the single-rod double-acting cylinder 11 is equal to A2.

[0054] The anti-roll fin rotation control system, when controlling the anti-roll fin to rotate in the opposite direction, such as Figure 6 and Figure 8As shown, the electro-hydraulic proportional directional valve 12 is switched to the functional X position, with the input port connected to the second output port (i.e., port P connected to port B), and the first output port connected to the return port (i.e., port A connected to port T). The hydraulic oil source 9 supplies oil to the rod chamber 113 of the single-rod double-acting cylinder 11 through the electro-hydraulic proportional directional valve 12. The piston rod 111 of the single-rod double-acting cylinder 11 retracts, driving the fin shaft to rotate clockwise via the fin handle 4, thus achieving the reverse rotation of the anti-roll fin. The oil in the rodless chamber 112 flows into the oil tank through the return port of the electro-hydraulic proportional directional valve 12, achieving the return of oil from the rodless chamber 112. At this time, the effective working area of ​​the high-pressure oil in the rod chamber 113 of the single-rod double-acting cylinder 11 is A2, then the output flow rate Q of the hydraulic oil source 9 is... p =Q b At this point, the equivalent working area of ​​the high-pressure oil in the single-acting double-acting cylinder 11 is A2.

[0055] In this embodiment, before the anti-roll fin rotation control system controls the anti-roll fin to rotate in the forward direction, the electro-hydraulic proportional directional valve 12 is first switched to the functional Z position. The functional Z position is a transition position. At this time, the input port of the electro-hydraulic proportional directional valve 12 is connected to the first output port (i.e., connected to port P and port A), and the second output port is connected to the return oil port (i.e., connected to port B and port T). After the valve core of the electro-hydraulic proportional directional valve 12 moves a certain displacement, it is switched to the functional Y position.

[0056] If the rotary fin hydraulic mechanism does not use the differential control circuit of this embodiment, the electro-hydraulic proportional directional valve 12 can be replaced with an electro-hydraulic proportional directional valve 14 with an asymmetrical valve port, such as... Figure 9 As shown, the hydraulic oil source 9 is connected to the single-rod double-acting cylinder 11 via an electro-hydraulic proportional directional valve 14. The electro-hydraulic proportional directional valve 14 has an input port (P port), a first output port (A port), a second output port (B port), and a return port (T port). During forward rotation, the input port of the electro-hydraulic proportional directional valve 14 connects to the first output port, and the second output port connects to the return port. The hydraulic oil source 9 supplies oil to the rodless chamber 112 of the single-rod double-acting cylinder 11 through the electro-hydraulic proportional directional valve 14, and the oil in the rod chamber 113 returns to the oil tank through the electro-hydraulic proportional directional valve 14. The output flow rate Q of the hydraulic oil source 9... p =Q a =2Q b During reverse fin rotation, the input port of the electro-hydraulic proportional directional valve 14 is connected to the second output port, and the first output port is connected to the return port. The hydraulic oil source 9 supplies oil to the rod chamber 113, and the rodless chamber 112 returns oil to the oil tank through the electro-hydraulic proportional directional valve 14; the output flow rate Q of the hydraulic oil source 9... p =Q bIt is evident that the hydraulic hydraulic mechanism using the electro-hydraulic proportional directional valve 12 requires twice the hydraulic oil flow rate output by the hydraulic oil source 9 compared to the hydraulic hydraulic mechanism using the electro-hydraulic proportional directional valve 14. To meet the conveying requirements, a large-flow hydraulic oil source 9 and a large-size hydraulic pump are required, which increases the size and power of the hydraulic mechanism and is not conducive to the precise control of the anti-roll fin control system.

[0057] As can be seen, in this embodiment, the hydraulic mechanism of the rotating fin uses a differential connection to make the equivalent working area of ​​the high-pressure oil in the single-rod double-acting cylinder 11 equal when rotating the fin in both the forward and reverse directions. The oil flow rate that the hydraulic oil source 9 needs to output is equal to the oil flow rate of the rod chamber 113 of the single-rod double-acting cylinder 11. Under the condition that the piston rod moves at the same speed, the anti-rolling fin rotating fin control system of this embodiment requires half the flow rate of the ordinary anti-rolling fin rotating fin control system, and the system power is also greatly reduced.

[0058] 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. An energy-saving anti-roll fin control system based on a single-acting double-rod hydraulic cylinder, characterized in that, The anti-roll fin control system includes a fin-rotating actuator and a fin-rotating hydraulic mechanism; The rotating fin actuator includes a single-rod double-acting hydraulic cylinder (11), a fin handle (4), and a fin shaft (6); the piston rod (111) of the single-rod double-acting hydraulic cylinder (11) is connected to the fin shaft (6) through the fin handle (4); The rotary fin hydraulic mechanism includes a hydraulic oil source (9), an electro-hydraulic proportional directional valve (12), and a check valve (13); the oil outlet of the hydraulic oil source (9) is connected to the input port of the electro-hydraulic proportional directional valve (12); the first output port and the second output port of the electro-hydraulic proportional directional valve (12) are respectively connected to the rodless chamber (112) and the rod chamber (113) of the single-rod double-acting cylinder (11), and the rod chamber (113) is connected to the input port of the electro-hydraulic proportional directional valve (12) through the check valve (13); the oil return port of the electro-hydraulic proportional directional valve (12) is connected to the oil tank; The hydraulic oil source (9) supplies oil to the rodless chamber (112) or the rod chamber (113) of the single-rod double-acting cylinder (11) through the electro-hydraulic proportional directional valve (12), thereby driving the fin shaft (6) to rotate.

2. The energy-saving anti-roll fin control system based on a single-acting double-rod hydraulic cylinder according to claim 1, characterized in that, The piston rod (111) is installed only in the rod chamber (113) of the single-rod double-acting cylinder (11), and the effective working area of ​​the rodless chamber (112) is twice the effective working area of ​​the rod chamber (113).

3. The energy-saving anti-roll fin control system based on a single-acting double-rod hydraulic cylinder according to claim 2, characterized in that, When the anti-roll fin rotation control system controls the single-acting double-rod cylinder (11) to rotate the anti-roll fin via the rotation hydraulic mechanism, the output flow rate Q of the hydraulic oil source (9) is... p =Q b , where Q b The required working oil flow rate for the rod chamber (113) of the single-rod double-acting hydraulic cylinder (11).

4. The energy-saving anti-roll fin control system based on a single-acting double-rod hydraulic cylinder according to claim 1, characterized in that, The electro-hydraulic proportional directional valve (12) has the function of being suitable for differential circuit connection.

5. The energy-saving anti-roll fin control system based on a single-acting double-rod hydraulic cylinder according to claim 1, characterized in that, The electro-hydraulic proportional directional valve (12) is switched to the functional Y position, and the input port of the electro-hydraulic proportional directional valve (12) is connected to the first output port; the hydraulic oil source (9) supplies oil to the rodless chamber (112) of the single-rod double-acting cylinder (11) through the electro-hydraulic proportional directional valve (12); the piston rod (111) of the single-rod double-acting cylinder (11) extends outward to realize the forward rotation of the rotating fin actuator; the oil in the rod chamber (113) flows through the check valve (3) to the output oil circuit of the hydraulic oil source (9), and flows through the electro-hydraulic proportional directional valve (12) to the rodless chamber (112).

6. The energy-saving anti-roll fin control system based on a single-acting double-acting hydraulic cylinder according to claim 1, characterized in that, The electro-hydraulic proportional directional valve (12) is switched to the functional X position. The input port of the electro-hydraulic proportional directional valve (12) is connected to the second output port, and the first output port is connected to the return port. The hydraulic oil source (9) supplies oil to the rod chamber (113) of the single-rod double-acting cylinder (11) through the electro-hydraulic proportional directional valve (12). The piston rod (111) of the single-rod double-acting cylinder (11) retracts, realizing the reverse rotation of the rotating fin actuator. The oil in the rodless chamber (112) returns through the electro-hydraulic proportional directional valve (12).

7. The energy-saving anti-roll fin control system based on a single-acting double-rod hydraulic cylinder according to claim 1, characterized in that, The piston rod (111) of the single-rod double-acting hydraulic cylinder (11) is hinged to one end of the fin (4) via the fin pin (3), and the other end of the fin (4) is connected to the fin shaft (6).

8. The energy-saving anti-roll fin control system based on a single-acting double-rod hydraulic cylinder according to claim 7, characterized in that, The single-acting double-acting cylinder (11) is supported on the support parts of the anti-roll fin by a hinge (8).

9. The energy-saving anti-roll fin control system based on a single-acting double-rod hydraulic cylinder according to claim 7, characterized in that, The fin shank (4) is connected to the fin shaft (6) by a key (5) and a bolt.

10. A method for controlling fin rotation to reduce roll, characterized in that, The fin control method is implemented by the energy-saving anti-rolling fin control system based on a single-rod double-acting hydraulic cylinder as described in any one of claims 1 to 9, and the effective working area A1 of the rodless chamber (112) of the single-rod double-acting hydraulic cylinder (11) is equal to twice the effective working area A2 of the rod chamber (113), and the process is as follows: When the anti-roll fin rotates forward, the electro-hydraulic proportional directional valve (12) switches to the functional Y position, and the input port of the electro-hydraulic proportional directional valve (12) is connected to the first output port; the hydraulic oil source (9) supplies oil to the rodless chamber (112) of the single rod double-acting cylinder (11) through the electro-hydraulic proportional directional valve (12), the piston rod (111) of the single rod double-acting cylinder (11) extends, and the fin shaft (6) drives the anti-roll fin to rotate forward; the oil in the rod chamber (113) of the single rod double-acting cylinder (11) returns to the output oil circuit of the hydraulic oil source (9) through the check valve (3), and together with the oil output by the hydraulic oil source (9), it supplies oil to the rodless chamber (112) of the single rod double-acting cylinder (11) through the electro-hydraulic proportional directional valve (12); During the forward fin rotation process, the working oil flow rate Q in the rodless chamber (112) of the single-rod double-acting cylinder (11) is... a =Q p +Q b , where Q p Q is the output flow rate of the hydraulic oil source (9). b The working oil flow rate of the rod chamber (113) of the single-rod double-acting hydraulic cylinder (11); because Q a =2Q b Then Q p =Q b The equivalent working area of ​​the high-pressure oil in the single-rod double-acting cylinder (11) is equal to A2; When controlling the anti-roll fin to rotate in the opposite direction, the electro-hydraulic proportional directional valve (12) switches to the function X position, with the input port connected to the second output port and the first output port connected to the return port; the hydraulic oil source (9) supplies oil to the rod chamber (113) of the single-rod double-acting cylinder (11) through the electro-hydraulic proportional directional valve (12), and the piston rod (111) of the single-rod double-acting cylinder (11) retracts, realizing the anti-roll fin to rotate in the opposite direction. The oil in the rodless chamber (112) flows into the oil tank for return through the return port of the electro-hydraulic proportional directional valve (12); the output flow rate Q of the hydraulic oil source (9) p =Q b The equivalent working area of ​​the high-pressure oil in the single-rod double-acting cylinder (11) is A2.

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