Patent Application
20120181382
This application claims priority to Japanese Patent Application No. 2011-008709. The entire disclosure of Japanese Patent Application No. 2011-008709 is hereby incorporated herein by reference.
1. Field of the Invention
The present invention relates to a hydraulically operated aircraft actuator for driving a control surface of an aircraft.
2. Description of Related Art
An aircraft is provided with control surfaces that are formed as moving surfaces (flight control surfaces) and are configured as an aileron, an elevator, a rudder, and the like. Also, a hydraulically operated actuator (aircraft actuator) is attached to a control surface, and the control surface is driven by the aircraft actuator. As such hydraulically operated aircraft actuators capable of driving a control surface, those disclosed in Japanese Patent No. 3652642, U.S. Pat. No. 6,685,138, and U.S. Patent Application Publication No. 2008/0185476 are known.
Japanese Patent No. 3652642 and U.S. Pat. No. 6,685,138 disclose, as aircraft actuators, tandem actuators that are configured as a single cylinder mechanism including a piston rod provided with two pistons aligned in series. U.S. Patent Application Publication No. 2008/0185476 discloses an aircraft actuator having a structure in which two cylinder mechanisms each including a piston rod provided with a single piston are provided and the piston rods of the cylinder mechanisms are coupled at their ends. With the use of aircraft actuators as disclosed in Japanese Patent 3652642, U.S. Pat. No. 6,685,138, and U.S. Patent Application Publication No. 2008/0185476, it is possible to obtain an increased output due to an increased pressure receiving area.
Recently, there is a demand for coping with thinned wings, i.e., the reduction of the wing thickness, for the purpose of increasing the efficiency of the aircraft body to increase the fuel efficiency. Also, to install an aircraft actuator inside a thinned wing, it is very important to reduce the size of a high-output aircraft actuator. For this reason, there is a need to realize a reduction in size of a high-output aircraft actuator more efficiently than with aircraft actuators having structures as disclosed in Japanese Patent No. 3652642, U.S. Pat. No. 6,685,138, and U.S. Patent Application Publication No. 2008/0185476. When realizing the size reduction for a high-output aircraft actuator, it is also important that the stability and the reliability of control surface driving can be readily ensured.
In view of the foregoing circumstances, it is an object of the present invention to provide an aircraft actuator that can efficiently realize a reduction in size of a high-output aircraft actuator such that the aircraft actuator can be installed inside a wing with a reduced thickness, and also readily ensure the stability and the reliability of control surface driving.
According to a first aspect of an aircraft actuator according to the present invention for achieving the above-described object, there is provided a hydraulically operated aircraft actuator for driving a control surface of an aircraft, including: a plurality of tandem actuators each including two pistons and a piston rod that is arranged such that the two pistons are aligned in series, wherein the plurality of tandem actuators are disposed in parallel, each of the plurality of tandem actuators is provided with a case portion inside of which two piston movement areas are defined so as to be aligned in series along the piston rod, each of the piston movement areas being provided as an area in which the piston is moved and that is divided by the piston into a first hydraulic chamber and a second hydraulic chamber, a rod end portion is further provided that couples the respective piston rods of the plurality of tandem actuators on the outside of the case portions and that can be rotatably linked to the control surface, and, for each of the plurality of tandem actuators, the first hydraulic chambers disposed in the piston movement areas, respectively, on the side opposite to the side on which the rod end portion is provided are in communication with each other via a first hydraulic chamber communication path, and the second hydraulic chambers disposed in the piston movement areas, respectively, on the rod end portion side are in communication with each other via a second hydraulic chamber communication path.
With this configuration, the plurality of tandem actuators are provided in parallel. Moreover, in the tandem actuators, two piston movement areas that are divided by the pistons into the first and second hydraulic chambers are provided in series. Accordingly, four hydraulic chambers are disposed in series and the respective four hydraulic chambers are in a state of parallel, and therefore it is possible to achieve a structure in which many hydraulic chambers are disposed densely and compactly. Accordingly, the pressure receiving areas of the pistons can be efficiently increased in smaller areas, thus realizing a reduction in size of a high-output aircraft actuator such that the aircraft actuator can be installed inside a wing with a reduced thickness. Furthermore, due to the provision of the plurality of tandem actuators, it is possible to realize redundancy for the aircraft actuator whose size has been reduced, thus also readily ensuring the reliability of control surface driving.
Further, the respective piston rods of the plurality of tandem actuators are coupled by the rod end portion that can be rotatably linked to the control surface. Accordingly, it is possible to prevent the occurrence of a force fight in which the plurality of tandem actuators bias the control surface in opposite directions due to displacement between the positions of the piston rods. Furthermore, for each of the tandem actuators, the first hydraulic chambers that are disposed in the piston movement areas on the side opposite to the rod end portion side are in communication with each other, and the second hydraulic chambers that are disposed in the piston movement areas on the rod end portion side are in communication with each other. Accordingly, the states of pressures exerted on the two pistons can be readily synchronized in the tandem actuators. Thus, these configurations enable the stability of control surface driving to be readily ensured.
Therefore, with the above-described configuration, it is possible to provide an aircraft actuator that can efficiently realize a reduction in size of a high-output aircraft actuator such that the aircraft actuator can be installed inside a wing with a reduced thickness, and also readily ensure the stability and the reliability of control surface driving.
According to a second aspect of an aircraft actuator according to the present invention, in the aircraft actuator of the first aspect, the rod end portion is provided as a block-shaped member that couples ends of the plurality of piston rods, and holds a plurality of bearing portions that are disposed respectively on axial extensions of the plurality of piston rods and are linked to the control surface side.
With this configuration, the plurality of bearing portions that can be linked to the control surface side can be held by the block-shaped rod end portion, and the bearing portions can be disposed on the axial extensions of the piston rods. Accordingly, it is possible to suppress the biasing forces from the tandem actuators from acting on the control surface at positions displaced from the axial extensions of the piston rods. That is, it is possible to achieve a structure in which the biasing forces from the tandem actuators efficiently act on the axial directions of the piston rods.
According to a third aspect of an aircraft actuator according to the present invention, the aircraft actuator of the first aspect further includes a state switching valve that is disposed between a control valve for controlling supply and discharge of pressure oil in the first hydraulic chambers and the second hydraulic chambers and the first hydraulic chambers and the second hydraulic chambers, and that is provided with a plurality of switching positions to allow switching of the state of connection to the first hydraulic chambers and the second hydraulic chambers, wherein the state switching valve is provided with, as the switching positions: a control valve connection position to connect the control valve to all of the first hydraulic chambers and all of the second hydraulic chambers; and a damping position to connect the first hydraulic chambers to the second hydraulic chambers in at least one of the plurality of tandem actuators so as to provide communication between the first hydraulic chambers and the second hydraulic chambers via an orifice.
With this configuration, the state switching valve that allows switching of the state of connection to the first and second hydraulic chambers is provided between the control valve and the first and second hydraulic chambers. In addition to the control valve connection position, the damping position to provide communication between the first and second hydraulic chambers via the orifices is provided as a switching position of the state switching valve in at least one of the plurality of tandem actuators. Accordingly, a damping function can be realized by switching the state switching valve to the damping position. Depending on the relationship between the rigidity of the control surface and the aerodynamic drag exerted on the control surface, there is the possibility that pulsation of the control surface may occur during operation of the control surface. In such a case, for example, when a plurality of aircraft actuators are installed for driving a single control surface, switching the state switching valve of any one of the aircraft actuators to the damping position can suppress pulsation of the control surface by the damping function. Alternatively, it is also possible to suppress pulsation of a control surface by setting the state switching valve such that it can be switched to a damping position to provide communication between the first and second hydraulic chambers of any one of a plurality of tandem actuators via an orifice in a single aircraft actuator. Alternatively, it is also possible to suppress pulsation of a control surface by setting the state switching valve such that it can be switched to a damping position to provide communication between the first and second hydraulic chambers of any one of the tandem actuators via an orifice. Thus, with this configuration, it is also possible to improve the stability of control surface driving for a high-output aircraft actuator whose size has been effectively reduced.
According to a fourth aspect of an aircraft actuator according to the present invention, in the aircraft actuator of the first aspect, in the plurality of tandem actuators, the first hydraulic chambers are in communication with each other and the second hydraulic chambers are in communication with each other in first piston movement areas, which are the piston movement areas disposed on the side opposite to the rod end portion side, and the first hydraulic chambers are in communication with each other and the second hydraulic chambers are in communication with each other in second piston movement areas, which are the piston movement areas disposed on the rod end portion side.
With this configuration, between the plurality of tandem actuators, the corresponding first hydraulic chambers and the corresponding second hydraulic chambers are configured to be in communication with each other on the rod end portion side and the side opposite thereto. Accordingly, for an aircraft actuator including a plurality of tandem actuators, it is possible to simplify the configuration of the oil passages for supply and discharge of pressure oil in the first hydraulic chambers and the second hydraulic chambers.
According to a fifth aspect of an aircraft actuator according to the present invention, in the aircraft actuator of the fourth aspect, the case portions of the plurality of tandem actuators are formed integrally, and a communication passage that provides communication between the first hydraulic chambers and between the second hydraulic chambers of the first piston movement areas and a communication passage that provides communication between the first hydraulic chambers and between the second hydraulic chambers of the second piston movement areas are formed through the integrally formed case portions.
With this configuration, the case portions of the plurality of tandem actuators are formed integrally, and therefore it is possible to reduce the number of components and simplify the structure. Also, between the plurality of tandem actuators, the communication passages that provide communication between the corresponding first hydraulic chambers and between the corresponding second hydraulic chambers on the rod end portion side and the side opposite thereto are formed through the integrated case portions. Accordingly, it is possible to further simplify the configuration of the oil passages for supply and discharge of pressure oil in the hydraulic chambers.
It should be appreciated that the above and other objects, and features and advantages of the present invention will become apparent from the following description taken in conjunction with the accompanying drawings.
Hereinafter, an embodiment for carrying out the present invention will be described with reference to the accompanying drawings. It should be appreciated that the present invention is not limited to the configurations illustrated in the following embodiment, and can be widely applied to a hydraulically operated aircraft actuator for driving a control surface of an aircraft.
In the aircraft actuator 1, the first tandem actuator 11 includes two pistons (21a, 22a), namely a first piston 21a and a second piston 22a, a piston rod 23a, a first case portion (case portion) 24a, and so forth. On the other hand, the second tandem actuator 12 includes two pistons (21b, 22b), namely a first piston 21b and a second piston 22b, a piston rod 23b, a second case portion (case portion) 24b, and so forth. The plurality of tandem actuators (11, 12) are disposed in parallel such that the axial directions of the piston rod 23a and the piston rod 23b are disposed in a state of parallel.
In the first tandem actuator 11, the piston rod 23a is formed in the shape of a cylinder that is provided so as to be open at one end. The piston rod 23a is provided with the two pistons (21a, 22a) such that they are aligned in series in the axial direction. Also, the rod end portion 13, which will be described later, is fixed at one end of the piston rod 23a on the side opposite to the open end side. Installed inside the piston rod 23a is a position detection sensor 34 that has a support shaft structure for slidably supporting the piston rod 23a with respect to the first case portion 24a from inside and that detects a relative position of the piston rod 23a with respect to the first case portion 24a.
The first piston 21a and the second piston 22a are each formed in the shape of a disc that is fixed to the outer circumference of the cylindrical piston rod 23a integrally or as separate members. For example, the first piston 21a, which is provided on the open end side of the piston rod 23a, is formed integrally with the piston rod 23a. On the other hand, the second piston 22a, which is disposed in an axially intermediate portion of the piston rod 23a, is provided as a ring-shaped member into which the piston rod 23a is inserted, and is fixed to the outer circumference of the piston rod 23a via a seal (not shown).
Inside the first case portion 24a of the first tandem actuator 11, two piston movement areas (25a, 26a), which are provided as areas in which the pistons (21a, 22a) are moved, are defined such that they are aligned in series along the piston rod 23a. A first piston movement area 25a, which is an area in which the first piston 21a is moved, and a second piston movement area 26a, which is an area in which the second piston 22a is moved, are provided as the piston movement areas (25a, 26a).
The first piston movement area 25a is configured as an area that is divided by the first piston 21a into a first hydraulic chamber 27a and a second hydraulic chamber 29a in the first case portion 24a. With respect to the first piston 21a, the first hydraulic chamber 27a is disposed on the side opposite to the rod end portion 13 side, and the second hydraulic chamber 29a is disposed on the rod end portion 13 side.
The second piston movement area 26a is configured as an area that is divided by the second piston 22a into a first hydraulic chamber 28a and a second hydraulic chamber 30a in the first case portion 24a. With respect to the second piston 22a, the first hydraulic chamber 28a is disposed on the side opposite to the rod end portion 13 side, and the second hydraulic chamber 30a is disposed on the rod end portion 13 side.
The first hydraulic chamber 27a of the first piston movement area 25a and the first hydraulic chamber 28a of the second piston movement area 26a are in communication via a first hydraulic chamber communication path 35a. On the other hand, the second hydraulic chamber 29a of the first piston movement area 25a and the second hydraulic chamber 30a of the second piston movement area 26a are in communication via a second hydraulic chamber communication path 35b. That is, in the first tandem actuator 11, the first hydraulic chambers (27a, 28a) that are disposed in the piston movement areas (25a, 26a), respectively, on the side opposite to the rod end portion 13 side are in communication with each other via the first hydraulic chamber communication path 35a, and the second hydraulic chambers (29a, 30a) that are disposed in the piston movement areas (25a, 26a), respectively, on the rod end portion 13 side are in communication with each other via the second hydraulic chamber communication path 35b.
Although
In the second tandem actuator 12, the piston rod 23b is formed in the shape of a cylinder that is provided so as to be open at one end. The piston rod 23b is provided with the two pistons (21b, 22b) such that they are aligned in series in the axial direction. Also, the rod end portion 13, which will be described later, is fixed at one end of the piston rod 23b on the side opposite to the open end side. Installed inside the piston rod 23b is a support shaft 36 for slidably supporting the piston rod 23b with respect to the second case portion 24b from inside.
The first piston 21b and the second piston 22b are each formed in the shape of a disc that is fixed to the outer circumference of the cylindrical piston rod 23b integrally or as separate members. For example, the first piston 21b, which is provided on the open end side of the piston rod 23b, is formed integrally with the piston rod 23b. On the other hand, the second piston 22b, which is disposed in an axially intermediate portion of the piston rod 23b, is provided as a ring-shaped member in which the piston rod 23b is inserted, and is fixed to the outer circumference of the piston rod 23b via a seal (not shown).
Inside the second case portion 24b of the second tandem actuator 12, two piston movement areas (25b, 26b), which are provided as areas in which the pistons (21b, 22b) are moved, are defined such that they are aligned in series along the piston rod 23b. A first piston movement area 25b, which is an area in which the first piston 21b is moved, and a second piston movement area 26b, which is an area in which the second piston 22b is moved, are provided as the piston movement areas (25b, 26b).
The first piston movement area 25b is configured as an area that is divided by the first piston 21b into a first hydraulic chamber 27b and a second hydraulic chamber 29b in the second case portion 24b. With respect to the first piston 21b, the first hydraulic chamber 27b is disposed on the side opposite to the rod end portion 13 side, and the second hydraulic chamber 29b is disposed on the rod end portion 13 side.
The second piston movement area 26b is configured as an area that is divided by the second piston 22b into a first hydraulic chamber 28b and a second hydraulic chamber 30b in the second case portion 24b. With respect to the second piston 22b, the first hydraulic chamber 28b is disposed on the side opposite to the rod end portion 13 side, and the second hydraulic chamber 30b is disposed on the rod end portion 13 side.
The first hydraulic chamber 27b of the first piston movement area 25b in the second tandem actuator 12 is in communication with the first hydraulic chamber 27a of the first piston movement area 25a in the first tandem actuator 11 via a first communication passage 31a formed in the first case portion 24a and the second case portion 24b. Also, the second hydraulic chamber 29b of the first piston movement area 25b in the second tandem actuator 12 is in communication with the second hydraulic chamber 29a of the first piston movement area 25a in the first tandem actuator 11 via a second communication passage 32a formed in the first case portion 24a and the second case portion 24b.
Furthermore, the first hydraulic chamber 28b of the second piston movement area 26b in the second tandem actuator 12 is in communication with the first hydraulic chamber 28a of the second piston movement area 26a in the first tandem actuator 11 via a first communication passage 31b formed in the first case portion 24a and the second case portion 24b. The second hydraulic chamber 30b of the second piston movement area 26b in the second tandem actuator 12 is in communication with the second hydraulic chamber 30a of the second piston movement area 26a in the first tandem actuator 11 via a second communication passage 32b formed in the first case portion 24a and the second case portion 24b.
Accordingly, in the plurality of tandem actuators (11, 12), the first hydraulic chambers (27a, 27b) are in communication with each other and the second hydraulic chambers (29a, 29b) are in communication with each other in the first piston movement areas (25a, 25b), which are the areas disposed on the side opposite to the rod end portion 13 side. The first hydraulic chambers (28a, 28b) are in communication with each other and the second hydraulic chambers (30a, 30b) are in communication with each other in the second piston movement areas (26a, 26b), which are the areas disposed on the rod end portion 13 side.
The first case portion 24a and the second case portion 24b of the plurality of tandem actuators (11, 12) are formed integrally. Also, the first communication passage 31a and the second communication passage 32a that provide communication between the first hydraulic chambers (27a, 27b) and between the second hydraulic chambers (29a, 29b) of the first piston movement areas (25a, 25b) are formed through the first case portion 24a and the second case portion 24b that are formed integrally. The first communication passage 31b and the second communication passage 32b that provide communication between the first hydraulic chambers (28a, 28b) and between the second hydraulic chambers (30a, 30b) in the second piston movement areas (26a, 26b) are also formed through the first case portion 24a and the second case portion 24b that are formed integrally.
Although the first case portion 24a and the second case portion 24b of the plurality of tandem actuators (11, 12) are formed integrally in this embodiment, this need not be the case. That is, the first case portion 24a and the second case portion 24b may be formed as separate members.
The first hydraulic chamber 27b of the first piston movement area 25b and the first hydraulic chamber 28b of the second piston movement area 26b in the second tandem actuator 12 are in communication via the first hydraulic chambers (27a, 28a), the first communication passages (31a, 31b), and the first hydraulic chamber communication path 35a of the first tandem actuator 11. On the other hand, the second hydraulic chamber 29b of the first piston movement area 25b and the second hydraulic chamber 30b of the second piston movement area 26b are in communication via the second hydraulic chambers (29a, 30a), the second communication passages (32a, 32b), and the second hydraulic chamber communication path 35b of the first tandem actuator 11. That is, in the second tandem actuator 12, the first hydraulic chambers (27b, 28b) that are disposed in the piston movement areas (25b, 26b), respectively, on the side opposite to the rod end portion 13 side are in communication with each other via the first hydraulic chamber communication path 35a and so forth, and the second hydraulic chambers (29b, 30b) that are disposed in the piston movement areas (25b, 26b), respectively, on the rod end portion 13 side are in communication with each other via the second hydraulic chamber communication path 35b and so forth.
Although
The rod end portion 13 is configured to couple the respective piston rods (23a, 23b) of the plurality of tandem actuators (11, 12) on the outside of the case portions (24a, 24b) and to be rotatably linked to the control surface 100. Also, the rod end portion 13 is provided as a block-shaped member that couples ends of the plurality of piston rods (23a, 23b).
Further, the rod end portion 13 is configured to hold a plurality of bearing portions (50a, 50b) that are connected on the control surface 100 side. A bearing portion 50a is disposed on the axial extension of the piston rod 23a. On the other hand, a bearing portion 50b is disposed on the axial extension of the piston rod 23b. The bearing portion 50a and the bearing portion 50b are disposed on the rotation centerline of the rod end portion 13 that can be rotatably linked to the control surface 100.
As shown in
The reservoir circuit 102 includes a tank (not shown) into which pressure oil that is supplied as the pressure oil from the aircraft central hydraulic power source 101 and is thereafter discharged from the plurality of tandem actuators (11, 12) flows back, and the reservoir circuit 102 is configured to be in communication with the aircraft central hydraulic power source 101. Consequently, the pressure of the oil that has returned to the reservoir circuit 102 is raised by the aircraft central hydraulic power source 101 and the oil is supplied to the plurality of tandem actuators (11, 12).
Supply of the pressure oil from the aircraft central hydraulic power source 101 to the plurality of tandem actuators (11, 12) and discharge of the pressure oil from the plurality of tandem actuators (11, 12) to the reservoir circuit 102 are performed via a control valve 53 and the state switching valve 14 of the aircraft actuator 1. Additionally, a filter 54 for removing foreign matter contained in the oil and a check valve 55 that permits flow of pressure oil from the aircraft central hydraulic power source 101 and prevents flow of the oil in a direction flowing back to the aircraft central hydraulic power source 101 are provided between the aircraft central hydraulic power source 101 and the control valve 53. An accumulator 56 including a relief valve is provided between the reservoir circuit 102 and the control valve 53. By provision of the accumulator 56 in this way, the pressure of the pressure oil in the circuit on the upstream side of the accumulator 56 (the side opposite to the side in communication with the reservoir circuit 102) is maintained at a pressure equal to or greater than a relief pressure generated by the relief valve of the accumulator 56.
The control valve 53 is provided as a valve mechanism for controlling supply and discharge of the pressure oil in the first hydraulic chambers (27a, 27b, 28a, 28b) and the second hydraulic chambers (29a, 29b, 30a, 30b) of the plurality of tandem actuators (11, 12). The control valve 53 is provided, for example, as an electrohydraulic servo valve (EHSV), is configured such that the position of its spool (not shown) can be proportionally switched, and is driven based on a command signal from a controller 103 that controls the operation of the plurality of tandem actuators (11, 12).
The control valve 53 is switched based on a command signal from the controller 103, and thereby the pressure oil is supplied from the aircraft central hydraulic power source 101 to one of the first hydraulic chamber communication path 35a and the second hydraulic chamber communication path 35b and the pressure oil is discharged from the other of the first hydraulic chamber communication path 35a and the second hydraulic chamber communication path 35b.
By supply of the pressure oil to the first hydraulic chamber communication path 35a, the pressure oil is supplied to the first hydraulic chambers (27a, 27b, 28a, 28b). When the pressure oil is supplied to the first hydraulic chamber communication path 35a, the pressure oil is discharged from the second hydraulic chambers (29a, 29b, 30a, 30b) via the second hydraulic chamber communication path 35b. On the other hand, by supply of the pressure oil to the second hydraulic chamber communication path 35b, the pressure oil is supplied to the second hydraulic chambers (29a, 29b, 30a, 30b). When the pressure oil is supplied to the second hydraulic chamber communication path 35b, the pressure oil is discharged from the first hydraulic chambers (27a, 27b, 28a, 28b) via the first hydraulic chamber communication path 35a. Consequently, the piston rod 23a is moved relative to the first case portion 24a, and the piston rod 23b is moved relative to the second case portion 24b. Then, the rod end portion 13 that couples ends of the piston rods (23a, 23b) is moved together with the piston rods (23a, 23b), and thereby the control surface 100 is driven.
The controller 103 for driving the control valve 53 drives the control valve 53 based on a command signal from a superordinate computer (not shown) that commands the operation of the control surface 100, thus controlling the operation of the plurality of tandem actuators (11, 12). The controller 103 is configured to receive input of a position detection signal that is detected by the position detection sensor 34 provided in the first tandem actuator 11. Also, the controller 103 is configured to perform a feedback control of the position of the piston rod 23a based on the command signal from the superordinate computer for operation of the control surface 100 and the position detection signal from the position detection sensor 34.
As described above, the first hydraulic chambers (27a, 27b) are in communication with each other and the second hydraulic chambers (29a, 29b) are in communication with each other in the first piston movement areas (25a, 25b), and the first hydraulic chambers (28a, 28b) are in communication with each other and the second hydraulic chambers (30a, 30b) are in communication with each other in the second piston movement areas (26a, 26b). Also, the piston rod 23a and the piston rod 23b are coupled integrally at the rod end portion 13. Accordingly, by performing the feedback control of the position of the piston rod 23a, the position of the piston rod 23b is also controlled at the same time.
The state switching valve 14 of the aircraft actuator 1 is disposed between the control valve 53 and the first hydraulic chambers (27a, 27b, 28a, 28b) and the second hydraulic chambers (29a, 29b, 30a, 30b) of the plurality of tandem actuators (11, 12). Additionally, a port that is in communication with the first hydraulic chamber communication path 35a and a port that is in communication with the second hydraulic chamber communication path 35b are formed in the state switching valve 14. Also, the state switching valve 14 is configured as a valve mechanism provided with a plurality of switching positions (14a, 14b, 14c) to allow switching of the state of connection to the first hydraulic chambers (27a, 27b, 28a, 28b) and the second hydraulic chambers (29a, 29b, 30a, 30b).
The state switching valve 14 is provided with, as the above-mentioned switching positions (14a, 14b, 14c), a control valve connection position 14a, a bypass position 14b, and a damping position 14c.
The control valve connection position 14a is provided as a switching position to connect one port of the control valve 53 to the first hydraulic chamber communication path 35a, and connect the other port of the control valve 53 to the second hydraulic chamber communication path 35b. That is, the control valve connection position 14a is configured to connect the control valve 53 to all of the first hydraulic chambers (27a, 27b, 28a, 28b) and all of the second hydraulic chambers (29a, 29b, 30a, 30b).
The bypass position 14b is provided as a switching position to provide communication between the first hydraulic chamber communication path 35a and the second hydraulic chamber communication path 35b, and provide communication between the first and second hydraulic chamber communication paths (35a, 35b) and the reservoir circuit 102. That is, the bypass position 14b is configured to provide communication between all of the first hydraulic chambers (27a, 27b, 28a, 28b) and all of the second hydraulic chambers (29a, 29b, 30a, 30b), and connect them to the reservoir circuit 102.
The damping position 14c is provided as a switching position to provide communication between the first hydraulic chamber communication path 35a and the second hydraulic chamber communication path 35b via an orifice 33a and an orifice 33b. That is, the damping position 14c is configured to connect the first hydraulic chambers (27a, 27b , 28a, 28b) to the second hydraulic chambers (29a, 29b, 30a, 30b) in the plurality of tandem actuators (11, 12) so as to provide communication between the first hydraulic chambers (27a, 27b, 28a, 28b) and the second hydraulic chambers (29a, 29b, 30a, 30b) via the orifices (33a, 33b).
In a state in which the state switching valve 14 is switched to the damping position 14c, the first hydraulic chambers (27a, 27b, 28a, 28b) are connected to the reservoir circuit 102 via the orifice 33a, and the second hydraulic chambers (29a, 29b, 30a, 30b) are connected to the reservoir circuit 102 via the orifice 33b. Note that the orifices (33a, 33b) may be a fixed orifice in which the area of its portion where the cross-sectional area of the flow path of pressure oil is reduced is fixed without being varied, or may be a variable orifice that is configured such that the area of its portion where the cross-sectional area of the flow path of pressure oil is reduced is varied by a bimetal mechanism.
Further, the state switching valve 14 is configured such that the operation of switching the switching positions (14a, 14b, 14c) is performed by operating solenoid valves (51, 52) that are driven by the controller 103. As shown in
As shown in
The controller 103 controls the solenoid valves (51, 52) to be magnetized or demagnetized based on a command signal from the superordinate computer that commands the operation of the control surface 100, thus controlling the switching positions (14a, 14b, 14c) of the state switching valve 14. In a state in which both of the solenoid valves (51, 52) are magnetized and switched to the supply positions (51a, 52a), the state switching valve 14 is maintained in the state of being switched to the control valve connection position 14a. In a state in which one of the solenoid valves (51, 52) is magnetized, including, for example, a state in which the solenoid valve 51 is switched to the supply position 51a and the solenoid valve 52 is in the discharge position 52b, the state switching valve 14 is maintained in the state of being switched to the bypass position 14b. In a state in which both of the solenoid valves (51, 52) are demagnetized and switched to the discharge positions (51b, 52b), the state switching valve 14 is maintained in the state of being switched to the damping position 14c.
With the aircraft actuator 1 described thus far, the plurality of tandem actuators (11, 12) are provided in parallel. Moreover, in the tandem actuators (11, 12), two piston movement areas (namely, the piston movement areas 25a and 26a, or the piston movement areas 25b and 26b) that are divided by the pistons (21a, 22a, 21b, 22b) into the first and second hydraulic chambers (27a and 29a, 28a and 30a, 27b and 29b, 28b and 30b) are provided in series. Accordingly, four hydraulic chambers (the hydraulic chambers 27a, 29a, 28a, and 30a, or the hydraulic chambers 27b, 29b, 28b, and 30b) are disposed in series and the respective four hydraulic chambers are in a state of parallel, and therefore it is possible to achieve a structure in which many hydraulic chambers are disposed densely and compactly. Accordingly, the pressure receiving areas of the pistons can be efficiently increased in smaller areas, thus realizing a reduction in size of a high-output aircraft actuator 1 such that the aircraft actuator 1 can be disposed inside a wing with a reduced thickness. Furthermore, due to the provision of the plurality of tandem actuators (11, 12), it is possible to realize redundancy for the aircraft actuator 1 whose size has been reduced, thus also readily ensuring the reliability of control surface driving.
Further, the respective piston rods (23a, 23b) of the plurality of tandem actuators (11, 12) are coupled by the rod end portion 13 that can be rotatably linked to the control surface 100. Accordingly, it is possible to prevent the occurrence of a force fight in which the plurality of tandem actuators (11, 12) bias the control surface 100 in opposite directions due to displacement between the positions of the piston rods (23a, 23b). Furthermore, in each of the tandem actuators (11 or 12), the first hydraulic chambers (the hydraulic chambers 27a and 28a, or the hydraulic chambers 27b and 28b) that are disposed in the piston movement areas (the piston movement areas (25a, 26a), or the piston movement areas (25b, 26b)) on the side opposite to the rod end portion 13 side are in communication with each other, and the second hydraulic chambers (the hydraulic chambers 29a and 30a, or the hydraulic chambers 29b and 30b) that are disposed in the piston movement areas (the piston movement areas (25a, 26a), or the piston movement areas (25b, 26b)) on the rod end portion 13 side are in communication with each other. Accordingly, the states of pressures exerted on the two pistons (the pistons 21a and 22a, or the pistons 21b and 22b) can be readily synchronized in the tandem actuators (11, 12). Thus, these configurations enable the stability of control surface driving to be readily ensured.
Therefore, according to this embodiment, it is possible to efficiently realize a reduction in size of a high-output aircraft actuator 1 such that the aircraft actuator 1 can be installed inside a wing with a reduced thickness, and also readily ensure the stability and the reliability of control surface driving.
With the aircraft actuator 1, the plurality of bearing portions (50a, 50b) that are linked to the control surface 100 side can be held by the block-shaped rod end portion 13, and the bearing portions (50a, 50b) can be disposed on the axial extensions of the piston rods (23a, 23b). Accordingly, it is possible to suppress the biasing forces from the tandem actuators (11, 12) from acting on the control surface 100 at positions displaced from the axial extensions of the piston rods (23a, 23b). That is, it is possible to achieve a structure in which the biasing forces from the tandem actuators (11, 12) efficiently act on the axial directions of the piston rods (23a, 23b).
With the aircraft actuator 1, the state switching valve 14 that allows switching of the state of connection to the first and second hydraulic chambers (27a, 27b, 28a, 28b, 29a, 29b, 30a, 30b) is provided between the control valve 53 and the first and second hydraulic chambers (27a, 27b, 28a, 28b, 29a, 29b, 30a, 30b). In addition to the control valve connection position 14a, the damping position 14c to provide communication between the first and second hydraulic chambers (27a, 27b, 28a, 28b, 29a, 29b, 30a, 30b) via the orifices (33a, 33b) is provided as a switching position of the state switching valve 14. Accordingly, a damping function can be realized by switching the state switching valve 14 to the damping position 14c.
Depending on the relationship between the rigidity of the control surface 100 and the aerodynamic drag exerted on the control surface 100, there is the possibility that pulsation of the control surface 100 may occur during operation of the control surface 100. In such a case, when a plurality of aircraft actuators 1 are installed for driving a single control surface 100 as in this embodiment, switching the state switching valve 14 of any one of the aircraft actuators 1 to the damping position 14c can suppress pulsation of the control surface 100 by the damping function. Thus, according to this embodiment, it is also possible to improve the stability of control surface driving for a high-output aircraft actuator 1 whose size has been effectively reduced.
With the aircraft actuator 1, between the plurality of tandem actuators (11, 12), the corresponding first hydraulic chambers (27a and 27b, 28a and 28b) and the corresponding second hydraulic chambers (29a and 29b, 30a and 30b) are configured to be in communication with each other on the rod end portion 13 side and the side opposite thereto. Accordingly, for an aircraft actuator 1 including a plurality of tandem actuators (11, 12), it is possible to simplify the configuration of the oil passages for supply and discharge of pressure oil in the first hydraulic chambers (27a, 27b, 28a, 28b) and the second hydraulic chambers (29a, 29b, 30a, 30b).
With the aircraft actuator 1, the case portions (24a, 24b) of the plurality of tandem actuators (11, 12) are formed integrally, and therefore it is possible to reduce the number of components and simplify the structure. Also, between the plurality of tandem actuators (11, 12), the communication passages (the first communication passages (31a, 31b), the second communication passages (32a, 32b)) that provide communication between the corresponding first hydraulic chambers (27a and 27b, 28a and 28b) and between the corresponding second hydraulic chambers (29a and 29b, 30a and 30b) on the rod end portion 13 side and the side opposite thereto are formed through the integrated case portions (24a, 24b). Accordingly, it is possible to further simplify the configuration of the oil passages for supply and discharge of pressure oil in the hydraulic chambers (27a, 27b, 28a, 28b, 29a, 29b, 30a, 30b).
Although an embodiment of the present invention has been described thus far, the present invention is not limited to the embodiment described above, and various modifications may be made within the scope recited in the claims. For example, the following modifications are possible.
(1) Although the above embodiment has been described, taking, as an example, an aircraft actuator including two tandem actuators, this need not be the case. That is, it is possible to implement an aircraft actuator in which three or more tandem actuators are disposed in parallel.
(2) Although the above embodiment has been described, taking, as an example, a configuration in which the case portions respectively provided for the plurality of tandem actuators are formed integrally, this need not be the case. That is, it is possible to adopt a configuration in which case portions that are respectively provided for a plurality of tandem actuators are formed as separate bodies.
(3) Although the above embodiment has been described, taking, as an example, a configuration in which the same hydraulic power source supplies pressure oil to a plurality of tandem actuators, this need not be the case. That is, hydraulic power sources that are different from each other may supply pressure oil to a plurality of tandem actuators.
(4) The configuration of the rod end portion is not limited to the configuration illustrated in the above embodiment, and various modification can be made as long as the rod end portion couples the respective piston rods of the plurality of tandem actuators on the outside of the case portions. It is possible to adopt a configuration in which the number of the bearing portions that are held by the rod end portion and are linked to the control surface side is different from the number of the piston rods.
(5) The configuration of the damping position is not limited to the above-described configuration, and various combinations may be implemented as long as the damping position is configured as a position to connect the first hydraulic chambers to the second hydraulic chambers in at least one of the plurality of tandem actuators so as to provide communication between the first hydraulic chambers and the second hydraulic chambers via an orifice. For example, it is also possible to suppress pulsation of a control surface by setting the state switching valve such that it can be switched to a damping position to provide communication between the first and second hydraulic chambers of any one of a plurality of tandem actuators via an orifice in a single aircraft actuator. Alternatively, it is also possible to suppress pulsation of the control surface by setting the state switching valve such that it can be switched to a damping position to provide communication between the first and second hydraulic chambers of any one of the tandem actuators via an orifice.
(6)
In the aircraft actuator 1, the first communication passages (31a, 31b) and the second communication passages (32a, 32b) are formed through the integrally formed case portions (24a, 24b). However, in the aircraft actuator 2, the first communication passages (42a, 42b) and the second communication passages (43a, 43b) are provided as oil passages external to the case portions (24a, 42b). That is, the first communication passage 42a that provides communication between the first hydraulic chambers (27a, 27b) and the second communication passage 43a that provides communication between the second hydraulic chambers (29a, 29b) in the first piston movement areas (25a, 25b) on the side opposite to the rod end portion 13 side are provided as oil passages external to the case portions (24a, 24b). The first communication passage 42b that provides communication between the first hydraulic chambers (28a, 28b) and the second communication passage 43b that provides communication between the second hydraulic chambers (30a, 30b) in the second piston movement areas (26a, 26b) on the rod end portion 13 side are also provided as oil passages external to the case portions (24a, 24b).
In the aircraft actuator 2, the first hydraulic chamber communication path 41a that provides communication between the first hydraulic chamber 27a of the first piston movement area 25a and the first hydraulic chamber 28a of the second piston movement area 26a is configured to pass through the state switching valve 40. Also, the first hydraulic chamber communication path 41a is configured to provide communication also between the first hydraulic chamber 27b of the first piston movement area 25b and the first hydraulic chamber 28b of the second piston movement area 26b via the state switching valve 40. Note that the first hydraulic chamber communication path 41a is configured as a path that connects the first communication passage 42a to the first communication passage 42b via the state switching valve 40.
The second hydraulic chamber communication path 41b that provides communication between the second hydraulic chamber 29a of the first piston movement area 25a and the second hydraulic chamber 30a of the second piston movement area 26a is configured to pass through the state switching valve 40. Also, the second hydraulic chamber communication path 41b is configured to provide communication also between the second hydraulic chamber 29b of the first piston movement area 25b and the second hydraulic chamber 30b of the second piston movement area 26b via the state switching valve 40. Note that the second hydraulic chamber communication path 41b is configured as a path that connects the second communication passage 43a to the second communication passage 43b via the state switching valve 40.
The state switching valve 40 of the aircraft actuator 2 is disposed between the control valve 53 and the first hydraulic chambers (27a, 27b, 28a, 28b) and the second hydraulic chambers (29a, 29b, 30a, 30b) of the plurality of tandem actuators (11, 12). Additionally, two ports that are in communication with the first hydraulic chamber communication path 41a and two ports that are in communication with the second hydraulic chamber communication path 41b are formed in the state switching valve 40. Also, the state switching valve 40 is configured as a valve mechanism provided with a plurality of switching positions (40a, 40b, 40c) to allow switching of the state of connection to the first hydraulic chambers (27a, 27b, 28a, 28b) and the second hydraulic chambers (29a, 29b, 30a, 30b).
The state switching valve 40 is provided with, as the above switching positions (40a, 40b, 40c), a control valve connection position 40a, a first damping position 40b, and a second damping position 40c.
The control valve connection position 40a is provided as a switching position to connect one port of the control valve 53 to the two ports that are in communication with the first hydraulic chamber communication path 41a, and connect the other port of the control valve 53 to the two ports that are in communication with the second hydraulic chamber communication path 41b. That is, the control valve connection position 40a is configured to connect the control valve 53 to all of the first hydraulic chambers (27a, 27b, 28a, 28b) and all of the second hydraulic chambers (29a, 29b, 30a, 30b).
The first damping position 40b connects the port that is in communication with the first hydraulic chamber communication path 41a on the side connecting to the first communication passage 42a to one port of the control valve 53. Furthermore, the first damping position 40b connects the port that is in communication with the second hydraulic chamber communication path 41b on the side connecting to the second communication passage 43b to the other port of the control valve 53. Also, the first damping position 40b connects the port that is in communication with the first hydraulic chamber communication path 41a on the side connecting to the first communication passage 42b to the port that is in communication with the second hydraulic chamber communication path 41b on the side connecting to the second communication passage 43a, thus providing communication between the first communication passage 42b and the second communication passage 43a via an orifice 44a. Accordingly, the first damping position 40b is configured to connect the first hydraulic chambers (28a, 28b) of the second piston movement areas (26a, 26b) and the second hydraulic chambers (29a, 29b) of the first piston movement areas (25a, 25b) in the two tandem actuators (11, 12) so as to provide communication between the first hydraulic chambers (28a, 28b) and the second hydraulic chambers (29a, 29b) via the orifice 44a.
The second damping position 40c connects the port that is in communication with the first hydraulic chamber communication path 41a on the side connecting to the first communication passage 42a to the port that is in communication with the second hydraulic chamber communication path 41b on the side connecting to the second communication passage 43b, thus providing communication between the first communication passage 42a and the second communication passage 43b via an orifice 44b. Accordingly, the second damping position 40c is configured to connect the first hydraulic chambers (27a, 27b) of the first piston movement areas (25a, 25b) and the second hydraulic chambers (30a, 30b) of the second piston movement areas (26a, 26b) in the two tandem actuators (11, 12) so as to provide communication between the first hydraulic chambers (27a, 27b) and the second hydraulic chambers (30a, 30b) via the orifice 44b.
Further, the second damping position 40c connects the port that is in communication with the first hydraulic chamber communication path 41a on the side connecting to the first communication passage 42b to the port that is in communication with the second hydraulic chamber communication path 41b on the side connecting to the second communication passage 43a, thus providing communication between the first communication passage 42b and the second communication passage 43a via an orifice 44c. Accordingly, the second damping position 40c is further configured to connect the first hydraulic chambers (28a, 28b) of the second piston movement areas (26a, 26b) and the second hydraulic chambers (29a, 29b) of the first piston movement areas (25a, 25b) in the two tandem actuators (11, 12) so as to provide communication between the first hydraulic chambers (28a, 28b) and the second hydraulic chambers (29a, 29b) via the orifice 44c.
It is possible to implement an aircraft actuator 2 including a state switching valve 40 provided with a plurality of damping positions (40b, 40c) as described above. Note that the orifices (44a, 44b, 44c) may be fixed orifices or variable orifices.
The present invention is widely applicable as a hydraulically operated aircraft actuator for driving a control surface of an aircraft. The present invention is not limited to the above-described embodiment, and all modifications, applications and equivalents thereof that fall within the claims, for which modifications and applications would become apparent by reading and understanding the present specification, are intended to be embraced therein.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2011-008709 | Jan 2011 | JP | national |
