JP2014202224A - Fluid actuator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid actuator capable of realizing a droop function through a simple mechanical structure, suppressing reduction in aerodynamic characteristics of a blade, reliably suppressing generation of contact between a first moving blade and a second moving blade, and preventing a fluctuation center position of a cylinder from being displaced.SOLUTION: The fluid actuator includes a cylinder 11, a piston 12, a rod 13, an output part 14, a link mechanism 15, an arm member 16, a stopper member 17, and a stopper driving part 18. The link mechanism 15 is displaced in association with movement of a second moving blade 103. The arm member 16 is displaced in association with the displacement of the link mechanism 15. The stopper driving part 18 is rotated in association with the displacement of the arm member 16. The stopper driving part 18 drives the stopper member 17 so as to change a position of the stopper member 17 in the cylinder 11 by rotation in accordance with the displacement of the arm member 16.

Description

  The present invention is installed in a wing in which the first moving blade on the front side and the second moving blade on the rear side are installed side by side along the longitudinal direction of the wing of the aircraft, and fluid is supplied and discharged. And a fluid actuator that drives the first moving blade to swing relative to the blade.

  In an aircraft, a wing having a configuration in which a first moving blade on the front side and a second moving blade on the rear side are installed side by side along the front-rear direction of the wing is provided. For example, in an aircraft main wing, a spoiler is installed as the first moving blade, and a flap is installed as the second moving blade. The blades on which the first and second moving blades are installed are provided with actuators that drive the first moving blade to swing relative to the blades. As such an actuator, a fluid actuator that operates by supplying and discharging a fluid is often used.

  In the fluid actuator that is installed on the blade provided with the first and second moving blades as described above and drives the first moving blade, the droop function is required to be realized in order to improve the aerodynamic characteristics of the blade. . This droop function is performed so that the gap between the first moving blade and the second moving blade does not increase when the second moving blade on the rear side of the blade is driven. The function is to drive the first moving blade on the front side of the blade in accordance with the operation of the moving blade. Specifically, when the second moving blade is driven so that the rear end portion of the second moving blade swings downward, the first moving blade also has the first moving blade. It is driven so that the rear end portion swings downward. Thereby, it adjusts so that the clearance gap between the rear-end part of a 1st moving blade and the front-end part of a 2nd moving blade may not become large.

  Patent Document 1 discloses a configuration for realizing a droop function for driving a spoiler in response to the operation of the flap when the flap is driven. On the first page of the specification of FIG. 1 and FIG. 1-2, a configuration that realizes a droop function by a mechanical structure that adjusts the position of the spoiler actuator (30) is disclosed. Specifically, the mechanical structure includes a first flap link (71), a first interconnect link (61), and a second interconnect link (62).

  In the configuration disclosed in FIG. 1-2 of Patent Document 1, the driving force from the flap drive unit (50) is transmitted via the lever (73), the second flap link (72), and the first flap link (71). Is transmitted to the flap (96), and the flap (96) is driven. As the first flap link (71) swings, the first interconnect link (61) and the second interconnect link (62) operate to drive the spoiler actuator (30). At this time, the second interconnect link (62) swings around the fixed point (C). The spoiler actuator (30) is attached to the middle position of the second interconnect link (62) in the cylinder. For this reason, the swing center position of the cylinder of the spoiler actuator (30) is displaced by the second interconnect link (62). And the drooping operation | movement of a spoiler (94) is performed because the oscillation center position itself of the cylinder of a spoiler actuator (30) displaces.

  Also, in the specification, page 2-3, and FIG. 3-5 of Patent Document 1, the rotational position of the eccentric cam (320) is controlled to adjust the position of the anchor portion (331) of the actuator device (330). A configuration for realizing the droop function is disclosed. In the configuration disclosed in FIG. 3-5 of Patent Document 1, the rotational driving force from the drive mechanism (310) is transmitted to the eccentric cam (320) via the coupling element (397). And the position of the anchor part (331) of an actuator apparatus (330) is displaced by adjusting the rotational position of the eccentric cam (320) by control by a drive mechanism (310). The anchor portion (331) is provided integrally with the cylinder of the actuator device (330). For this reason, with the rotation of the eccentric cam (320), the oscillation center position of the cylinder of the actuator device (330) is displaced. And the droop operation | movement of a spoiler (394) is performed because the rocking | swiveling center position itself of the cylinder of an actuator apparatus (330) displaces.

US Patent Application Publication No. 2007/0176051

  According to the configuration disclosed in FIG. 1-2 of Patent Document 1, the first flap link (71), the first interconnect link (61), and the second interconnect link (62) are configured to realize the droop function. A complicated mechanical structure is required. For this reason, it is desired that the droop function can be realized by a simpler mechanical structure.

  Furthermore, according to the configuration disclosed in FIG. 1-2 of Patent Document 1, the drooping operation of the spoiler (94) is performed by the displacement center position of the cylinder of the spoiler actuator (30) itself being displaced. For this reason, when the rod extends from the cylinder of the spoiler actuator (30) and the first moving blade (spoiler) stands up with respect to the blade, the rising angle of the first moving blade varies. Become. That is, the steering angle of the first moving blade varies. For this reason, when realizing the droop function, it is desirable to be able to prevent displacement of the swing center position of the cylinder.

  According to the configuration disclosed in FIG. 3-5 of Patent Document 1, in order to realize the droop function, it is necessary to adjust the rotational position of the eccentric cam (320) by the control by the drive mechanism (310). For this reason, electrical control of the electric motor etc. which comprise a drive mechanism (310) is needed. And since a droop function is implement | achieved by electrical position control, there exists a possibility that the contact with a 1st moving blade (spoiler) and a 2nd moving blade (flap) may generate | occur | produce in relation to a control intersection. is there. Note that if the rotational position of the eccentric cam is controlled within a range that has a sufficient margin with respect to the above control intersection, the gap between the first moving blade and the second moving blade becomes large. In this case, the aerodynamic characteristics of the wing are deteriorated.

  Furthermore, according to the configuration disclosed in FIG. 3-5 of Patent Document 1, the swing center position of the cylinder of the actuator device (330) is displaced, so that the droop operation of the spoiler (394) is performed. Therefore, when the movable part (332) constituting the rod extends from the cylinder of the actuator device (330) and the first moving blade (spoiler) stands up with respect to the blade, the first moving blade There will be variations in the standing angle. That is, similarly to the configuration disclosed in FIG. 1-2 of Patent Document 1, the steering angle of the first moving blade varies.

  In view of the above circumstances, the present invention can realize a droop function with a simple mechanical structure, can suppress a decrease in aerodynamic characteristics of the blade, and can prevent the contact between the first blade and the second blade. It is an object of the present invention to provide a fluid actuator that can be reliably suppressed and that can also prevent displacement of the swing center position of a cylinder.

  In order to achieve the above object, a fluid actuator according to an aspect of the present invention is configured such that a first moving blade on the front side and a second moving blade on the rear side are arranged side by side along the longitudinal direction of the wing of an aircraft. A fluid actuator that is installed in the blade and operates by supplying and discharging a fluid and driving the first blade to swing with respect to the blade, wherein the fluid is supplied and discharged A cylinder that partitions a pressure chamber into and from which fluid is supplied and discharged, and slides against an inner wall of the cylinder, and is provided integrally with or fixed to the piston. A rod which is displaced so as to expand and contract with respect to the rod, and is integrally provided or fixed to the rod and connected to the first rotor blade, and is displaced together with the rod. An output portion that drives the first moving blade, a stopper member that defines a movable range of the piston in the cylinder by contacting at least one of the piston and the rod in the cylinder; A stopper drive unit that is attached to the cylinder so as to be rotatable or swingable and that can be driven by urging the stopper member, and one or a plurality of link members, one end side of which is against the second moving blade A link mechanism that is swingably or rotatably connected, and an arm that has one end side connected to the other end side of the link mechanism to be swingable or rotatable, and the other end side fixed to the stopper driving unit. And a member. In the fluid actuator according to an aspect of the present invention, the link mechanism is displaced in accordance with the operation of the second moving blade, the arm member is displaced in accordance with the displacement of the link mechanism, The stopper driving unit rotates or swings with the displacement, and the stopper driving unit rotates or swings to change the position of the stopper member in the cylinder according to the displacement of the arm member. Further, the stopper member is driven.

  According to this configuration, when the second moving blade is driven, the link mechanism connected to the second moving blade is displaced. As the link mechanism is displaced, the arm member rotates or swings the stopper drive unit. At this time, the stopper driving unit changes the position of the stopper member in the cylinder according to the displacement of the arm member. And the movable range of the piston prescribed | regulated in a cylinder is changed. Along with this, the position of the rod and the output portion with respect to the cylinder when the rod is contracted with respect to the cylinder is also changed. By the above, a droop function can be achieved reliably. That is, when the second moving blade is driven so that the rear end portion of the second moving blade swings downward, the gap between the first moving blade and the second moving blade is reduced. The first moving blade can be driven in correspondence with the operation of the second moving blade so as not to become large. That is, the position of the rod and the output portion relative to the cylinder in a state where the rod is contracted with respect to the cylinder is displaced, and the rear end portion of the first moving blade swings downward along with the displacement of the output portion. The first moving blade is driven. And it adjusts so that the clearance gap between the rear-end part of a 1st moving blade and the front-end part of a 2nd moving blade may not become large.

  According to the above configuration, a simple mechanical structure including a stopper member, a stopper driving unit, a link mechanism, and an arm member is added to the basic configuration of the fluid actuator including the cylinder, the piston, the rod, and the output unit. Thus, the droop function can be realized. Further, according to the above configuration, the droop function is not realized by the electrical position control as in the prior art, but is realized by a simple mechanical structure. For this reason, contact between the first moving blade and the second moving blade does not occur in relation to the control intersection. In addition, the gap between the first moving blade and the second moving blade does not become large as a result of performing the control within a range having a sufficient margin for the control intersection. That is, it is possible to suppress the deterioration of the aerodynamic characteristics of the wing. Therefore, when realizing the droop function, it is possible to suppress a decrease in the aerodynamic characteristics of the blade and to reliably suppress the occurrence of contact between the first moving blade and the second moving blade.

  Further, according to the above configuration, the stopper driving unit that mechanically interlocks with the operation of the second moving blade via the link mechanism and the arm member changes the position of the stopper member in the cylinder. The movable range of the piston in the cylinder is changed. Thereby, the position with respect to the cylinder of the output part in the state which the rod contracted with respect to the cylinder is changed, and a droop function is implement | achieved. For this reason, the droop operation | movement of a 1st moving blade will be performed, without displacing the rocking | swiveling center position of a cylinder. Thereby, when the rod extends from the cylinder and the first moving blade stands up with respect to the blade, it is possible to prevent variation in the standing angle of the first moving blade. That is, it is possible to prevent variation in the steering angle of the first moving blade.

  Therefore, according to said structure, a droop function can be implement | achieved by simple mechanical structure, the fall of the aerodynamic characteristic of a blade can be suppressed, and generation | occurrence | production of a contact with a 1st moving blade and a 2nd moving blade is suppressed reliably. Further, it is possible to provide a fluid actuator that can prevent displacement of the center position of the swing of the cylinder.

  Moreover, it is preferable that the said stopper member is slidably installed along the axial direction of the said cylinder with respect to the inner wall of the said cylinder in the said cylinder.

  According to this configuration, the stopper member is provided as a member that slides in the axial direction within the cylinder. For this reason, the stopper member which drives in a cylinder by a stopper drive part and prescribes | regulates the movable range in the cylinder of a piston is realizable with a simple structure.

  The stopper member is disposed in the cylinder so that its axial direction extends along the axial direction of the cylinder, and the stopper member opens at both ends of the stopper member, and the stopper member It is preferable that a through-hole penetrating the member in the axial direction is provided, and the pressure of the fluid supplied to the pressure chamber acts on both ends of the stopper member through the through-hole in the cylinder.

  According to this configuration, since the through hole is provided in the stopper member, the pressure of the fluid supplied to the pressure chamber acts on both ends of the stopper member. For this reason, the stopper member is prevented from being strongly pressed to one side in the axial direction of the cylinder by the pressure of the fluid supplied to the pressure chamber. Thereby, when the stopper member is driven, the influence of the pressure of the fluid supplied to the pressure chamber can be canceled and suppressed in the axial direction. That is, the stopper member can be easily driven by the stopper driving unit.

  Moreover, it is preferable that the stopper member is provided as a cylindrical member, has a sliding surface that slides with respect to the inner wall of the cylinder on the outer peripheral surface thereof, and the through hole is provided on the inner side.

  According to this configuration, it is possible to realize a stopper member that can suppress the influence of the pressure of the fluid supplied to the pressure chamber and can easily drive the stopper member by the stopper driving unit with a simple structure.

  Further, the stopper member is provided with a circumferential groove portion which is recessed toward the inner side in the radial direction of the stopper member and extends in a groove shape in the circumferential direction on the outer peripheral surface at a midway position in the axial direction, In a state where the fluid supplied to the pressure chamber is restricted from flowing into an annular region defined as an annularly extending region between the circumferential groove and the inner periphery of the cylinder, the stopper member It is preferable that the outer peripheral surface and the inner peripheral surface of the cylinder slide.

  According to this configuration, the annular region in which the flow of the fluid supplied to the pressure chamber is restricted is defined between the circumferential groove on the outer peripheral surface of the stopper member and the inner periphery of the cylinder. For this reason, it is possible to dispose a part of the stopper driving part in the annular region where the inflow of the fluid supplied to the pressure chamber is restricted, and to bring the stopper driving part into contact with the stopper member. That is, the driving force from the stopper driving unit can be transmitted to the stopper member in the annular region outside the region where the pressure of the fluid supplied to the pressure chamber directly acts. Thereby, the structure for driving a stopper member by a stopper drive part is realizable with a simple structure. In the stopper member, a portion for partitioning a region where a part of the stopper driving portion is arranged is provided as a circumferential groove extending along the circumferential direction of the stopper member. For this reason, the stability of the sliding operation of the stopper member with respect to the cylinder can be further improved.

  In addition, a first seal member and a second seal member attached to the outer periphery of the stopper member are further provided, and the first seal member is located on one end side in the axial direction of the stopper member with respect to the circumferential groove portion. The second seal member is mounted in the axial direction of the stopper member with respect to the circumferential groove portion, and is attached to be disposed to seal inflow of the fluid supplied to the pressure chamber into the annular region. It is preferable to be attached so as to be arranged on the other end side to seal the inflow of the fluid supplied to the pressure chamber into the annular region.

  According to this configuration, the annular region is sealed by the first seal member and the second seal member on both sides in the axial direction of the stopper member. Therefore, the sealing performance between the region where the pressure of the fluid supplied to the pressure chamber acts and the annular region is improved by a simple configuration in which the first and second seal members are attached to the outer periphery of the stopper member. Can do.

  The stopper driving portion includes a shaft portion that is rotatably or swingably supported with respect to the cylinder, and a portion provided at a position eccentric to the rotation center or swing center of the shaft portion. And an eccentric portion that rotates or swings with the shaft portion, and the shaft portion rotates or swings with the displacement of the arm member, and the eccentric portion biases the stopper member. .

  According to this structure, the stopper drive part which urges | biases and drives a stopper member with the displacement of an arm member by the simple structure provided with the axial part and the eccentric part can be comprised.

  Moreover, it is preferable that the said eccentric part contains the crankshaft part or cam part provided in the position eccentric with respect to the said axial part.

  According to this configuration, the eccentric portion of the stopper driving portion can be easily formed with a simple structure including the crankshaft portion or the cam portion.

  Moreover, it is preferable that the stopper member is provided with a groove portion that can be engaged with the eccentric portion on an outer peripheral surface thereof.

  According to this configuration, the stopper member can be urged by the groove portion on the outer peripheral surface of the stopper member by the eccentric portion that rotates or swings together with the shaft portion. For this reason, the structure for driving a stopper member by an eccentric part is realizable with the simple structure which provided the groove part in the outer peripheral surface of the stopper member.

  The stopper driving portion includes a shaft portion that is rotatably or swingably supported with respect to the cylinder, and a portion provided at a position eccentric to the rotation center or swing center of the shaft portion. An eccentric portion that rotates or swings together with the shaft portion, and the eccentric portion is disposed so as to be engageable with the circumferential groove portion, and the shaft portion rotates in accordance with the displacement of the arm member. Or it is also preferable that the eccentric portion oscillates and biases the stopper member.

  According to this structure, the stopper drive part which urges | biases and drives a stopper member with the displacement of an arm member by the simple structure provided with the axial part and the eccentric part can be comprised. The eccentric portion biases the stopper member in the circumferential groove portion. For this reason, the driving force from the stopper driving portion can be transmitted to the stopper member in the annular region that is the region outside the region where the pressure of the fluid supplied to the pressure chamber directly acts.

  According to the present invention, a droop function can be realized by a simple mechanical structure, a decrease in aerodynamic characteristics of the blade can be suppressed, and the occurrence of contact between the first blade and the second blade can be reliably suppressed. In addition, it is possible to provide a fluid actuator that can prevent displacement of the swing center position of the cylinder.

It is a mimetic diagram illustrating the state where the fluid actuator concerning one embodiment of the present invention was installed in the wing of an airplane. It is a schematic diagram which shows the state by which the droop operation | movement of the 1st moving blade was performed by the action | operation of the fluid actuator shown in FIG. It is an enlarged view which expands and shows a part of FIG. It is sectional drawing about a part of fluid actuator of the state shown in FIG. It is an enlarged view which expands and shows a part of FIG. It is a figure which shows a part of fluid actuator in the AA arrow position shown in FIG. 5, Comprising: It is a figure containing the partial cross section which shows a stopper drive part and its vicinity. It is a figure which expands and shows some cross sections of the fluid actuator of the state shown in FIG. It is sectional drawing which shows the fluid actuator which concerns on a modification.

  Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings. The present invention is not limited to the embodiment exemplified in the following embodiment, and the first moving blade on the front side and the second moving blade on the rear side are installed side by side along the front-rear direction of the wing of the aircraft. The present invention can be widely applied to a fluid actuator that is installed in a blade, operates by supplying and discharging a fluid, and drives the first blade to swing relative to the blade.

[Installation form of fluid actuator]
FIG. 1 is a schematic view illustrating a state in which a fluid actuator 1 according to an embodiment of the invention is installed on a wing 101 of an aircraft. In FIG. 1, the main part of the aircraft is not shown. In FIG. 1, a part of the blade 101, the first moving blade 102, and the second moving blade 103 are schematically illustrated.

  In the present embodiment, the wing 101 is configured as a main wing of an aircraft. The first moving blade 102 is configured as a spoiler. The second moving blade 103 is configured as a flap. In the following description, the first moving blade 102 is also referred to as a spoiler 102. The second rotor blade 103 is also referred to as a flap 103. In FIG. 1, a cross section perpendicular to the left-right direction of the aircraft in a portion on the rear end side of the wing 101 is schematically illustrated. In FIG. 1, the wing 101 and the spoiler 102 are illustrated in a state including a partial cross section. On the other hand, only the outline of the flap 103 is schematically shown.

  The fluid actuator 1 of this embodiment is installed in a wing 101 in which a front spoiler 102 and a rear flap 103 are installed side by side along the front-rear direction of an aircraft wing 101. The fluid actuator 1 is provided as an actuator that operates by supplying and discharging a fluid, and drives the spoiler 102 to swing with respect to the blade 101.

  The fluid actuator 1 is connected to the wing 101 via a rotating shaft 104. The rotating shaft 104 is installed on the wing 101. The fluid actuator 1 is rotatably connected to the rotary shaft 104 at the end of the cylinder 11. Thereby, the fluid actuator 1 is supported with respect to the wing | blade 101 so that rocking | fluctuation centering | focusing on the rotating shaft 104 is possible.

  Further, the fluid actuator 1 is connected to the spoiler 102 via the swing shaft 105. The swing shaft 105 is installed on the spoiler 102. The fluid actuator 1 is rotatably connected to the swing shaft 105 at the output portion 14 thereof. The spoiler 102 is rotatably supported with respect to the fulcrum shaft 106. The fulcrum shaft 106 is installed on the wing 101. Thereby, the spoiler 102 is supported with respect to the wing | blade 101 so that rocking | fluctuation centering | focusing on the fulcrum shaft 106 is possible.

  In the fluid actuator 1, an output portion 14 and a rod 13 to which the output portion 14 is fixed are provided so as to protrude relative to the cylinder 11 and be relatively displaceable. That is, the output unit 14 and the rod 13 are configured to be able to extend from the cylinder 11 by protruding from the cylinder 11. Further, the output unit 14 and the rod 13 are configured to be capable of contracting with respect to the cylinder 11. The spoiler 102 is driven by operating the fluid actuator 1 and displacing the output unit 14 and the rod 13 with respect to the cylinder 11. The spoiler 102 is driven to swing with respect to the wing 101 about the fulcrum shaft 106.

  The fluid actuator 1 is connected to the flap 103 via a connecting shaft 107. The connecting shaft 107 is installed on the flap 103. The fluid actuator 1 is rotatably connected to the connecting shaft 107 in the link mechanism 15. Note that the flap 103 is rotatably supported with respect to the fulcrum shaft 108. The fulcrum shaft 108 is installed on the wing 101. As a result, the flap 103 is swingably supported with respect to the wing 101 about the fulcrum shaft 108.

  The spoiler 102 is driven by the fluid actuator 1. On the other hand, the flap 103 is an actuator different from the fluid actuator 1 and is driven by an actuator not shown. Similar to the fluid actuator 1, this actuator also operates by supplying and discharging fluid and drives the flap 103 to swing with respect to the blade 101.

[Configuration of fluid actuator]
As will be described later, the fluid actuator 1 is configured as an actuator capable of realizing a droop function by a mechanical structure. That is, the fluid actuator 1 is configured so that the gap between the spoiler 102 and the flap 103 does not become large when the flap 103 is driven so that the rear end portion of the flap 103 swings downward. In response to the operation of the flap 103, a droop operation for driving the spoiler 103 can be performed.

  FIG. 2 is a schematic diagram showing a state in which the fluid actuator 1 is installed on the blade 101 as in FIG. However, FIG. 1 illustrates a state in which the flap 103 is in an upward position and the spoiler 102 is in a neutral position. On the other hand, FIG. 2 shows a state where the drooping operation of the spoiler 102 is performed by the operation of the fluid actuator 1. That is, FIG. 2 illustrates a state in which the flap 103 is in a downward position and the spoiler 102 is in a droop position.

  FIG. 3 is an enlarged view showing a part of FIG. 4 is a cross-sectional view of a part of the fluid actuator 1 in the state shown in FIG. As shown in FIGS. 1 to 4, the fluid actuator 1 includes a cylinder 11, a piston 12, a rod 13, an output unit 14, a link mechanism 15, an arm member 16, a stopper member 17, a stopper driving unit 18, and a first seal member 19. The second seal member 20 and the position detector 21 are provided.

  In addition, in FIG. 4, the cross section about the cylinder 11, the piston 12, the rod 13, the stopper member 17, etc. is shown in figure. In FIG. 4, the relationship between the arm member 16 and its mounting position with respect to the cylinder 11 is schematically shown in an exploded perspective view. Specifically, in FIG. 4, the correspondence between the arm member 16 and its mounting position with respect to the cylinder 11 is illustrated by a one-dot chain line. Furthermore, in FIG. 4, only a part of the link mechanism 15 is shown.

[Cylinder]
The cylinder 11 is provided as a structure having a cylindrical portion through which fluid is supplied and discharged. The cylinder 11 includes a cylinder body 22, a cap member 23, and the like. The cylinder 11 is supplied with pressurized fluid as the fluid. The pressure fluid is supplied to the cylinder 11 from a fluid supply device (not shown) installed on the aircraft side of the aircraft. Examples of the pressure fluid supplied to the cylinder 11 include pressure oil, a pressure liquid other than the pressure oil, and compressed air. In the present embodiment, pressure oil is supplied to the cylinder 11 as the pressure fluid.

  The cylinder body 22 includes a cylindrical portion in which the piston 12 is disposed on the inside. The longitudinal direction in which the cylinder body 22 extends in a cylindrical shape is configured as the axial direction of the cylinder 11. The cylinder body 22 is open at one end in the axial direction of the cylinder 11 and is closed at the other end in the axial direction of the cylinder 11. A cap member 23 is attached to the opening at one end of the cylinder body 22.

  A connecting portion 22 a is provided at the closed end of the cylinder body 22. The connecting portion 22a is rotatably connected to the rotating shaft 104 via a bearing or a bush that is a cylindrical sliding member. Thereby, the cylinder 11 is rotatably installed with respect to the blade 101 via the rotating shaft 104.

  The cap member 23 is provided as a cylindrical member having a short length in the axial direction of the cylinder 11. The cap member 23 is fitted into and fixed to the opening at one end of the cylinder body 22. A male screw portion that is screwed into a female screw portion provided on the inner periphery of one end of the cylinder 11 is provided on the outer periphery of the cap member 23. The cap member 23 is attached to the cylinder body 22 by screwing. Note that a flange-like portion that is positioned with respect to the cylinder main body 22 by being in contact with the end of the cylinder main body 22 is provided at one end of the cap member 23.

  Further, a rod 13 described later is inserted inside the cap member 23 in a state where the rod 13 penetrates. The rod 13 is inserted inside the cap member 23 in a state where the rod 13 is slidable with respect to the inner periphery of the cap member 23 on the outer periphery thereof.

[piston]
The piston 12 is disposed in the cylinder 11 so as to be slidable along the axial direction of the cylinder 11 with respect to the inner wall of the cylinder body 22 of the cylinder 11. And the piston 12 is arrange | positioned in the cylinder 11 so that it may slide with respect to the inner periphery of the cylinder 11 in the outer periphery. The piston 12 is provided integrally with the rod 13 at the end of the rod 13. Thereby, when the piston 12 is displaced in the cylinder 11, the rod 13 is also displaced together with the piston 12.

  The piston 12 defines a pressure chamber (11a, 11b) in which pressure oil (pressure fluid) is supplied and discharged in the cylinder 11. More specifically, the piston 12 divides a region in the cylinder 11 into a pressure chamber 11 a on one side in the axial direction of the cylinder 11 and a pressure chamber 11 a on the other side in the axial direction of the cylinder 11. That is, the pressure chamber 11 a is disposed in the cylinder 11 on the side where the rod 13 together with the output portion 14 protrudes from the cylinder 11. And the pressure chamber 11b is arrange | positioned in the cylinder 11 at the connection part 22a side.

  Note that the pressure oil supplied from the fluid supply device installed on the aircraft body side is supplied to one of the pair of pressure chambers (11a, 11b). Then, at the same time as the supply timing, the pressure oil is discharged from the other of the pair of pressure chambers (11a, 11b). Thereby, the piston 12 is displaced with respect to the cylinder 11. The pressure oil discharged from the other of the pair of pressure chambers (11a, 11b) is returned to a reservoir circuit (not shown) installed on the aircraft body side. Then, the pressurized oil is pressurized by the fluid supply device and circulated for use. The pressure oil supply path and the discharge path for the pressure chambers (11a, 11b) are switched by a control valve (not shown). The piston 12 is displaced in the cylinder 11 by supplying and discharging the pressure oil to and from the pair of pressure chambers (11a, 11b).

[rod]
The rod 13 is provided as a member extending linearly, and is provided integrally with the piston 12 at an end thereof. For this reason, the rod 13 is displaced together with the piston 12. The rod 13 is displaced together with the piston 12 so as to expand and contract with respect to the cylinder 11. The rod 13 is installed so as to extend parallel to the cylinder 11 with respect to the cylinder 11. That is, the axial direction of the rod 13 configured as the longitudinal direction of the rod 13 is set parallel to the axial direction of the cylinder 11.

  Further, the rod 13 is disposed in the cylinder 11 on the end side where the piston 12 is integrally provided. The rod 13 is disposed in a state where the end opposite to the end where the piston 12 is integrally provided protrudes from the cap member 23 of the cylinder 11. An output portion 14 is fixed to an end portion of the rod 13 protruding from the cylinder 11. Note that an end of the rod 13 that protrudes from the cylinder 11 is provided with an attachment hole 13a that opens toward the end and to which the output portion 14 is attached. On the inner periphery of the mounting hole 13a, a female screw portion that is screwed into a male screw portion provided in the shaft portion 14a of the output portion 14 is provided.

  Further, the rod 13 is provided with a cylindrical portion 13b formed in a cylindrical shape opening toward the piston 12 side. In the space inside the cylindrical portion 13b, a part of a position detector 21 described later is disposed. A through hole is formed in the center of the piston 12, and this through hole communicates with the opening of the cylindrical portion 13b. And the position detector 21 is arrange | positioned in the state which penetrated the through-hole of the center of piston 12 in the cylinder 11. FIG.

[Output section]
The output unit 14 is provided as a member that is fixed to the rod 13 and connected to the spoiler 102. The output unit 14 is configured to be displaced together with the rod 13 with respect to the cylinder 11 to drive the spoiler 102.

  The output portion 14 is provided with a shaft portion 14 a that is screwed into the mounting hole 13 a of the rod 13 and a connecting portion 14 b that is connected to the spoiler 102. The shaft portion 14a and the connecting portion 14b are integrally provided. A nut member 24 is attached to the shaft portion 14a in a screwed state. The connecting portion 14b is provided as a ring-shaped portion, and is rotatably connected to the swing shaft 105 via a bearing or a bush that is a cylindrical sliding member.

  When the output portion 14 is attached to the rod 13 and fixed, first, the shaft portion 14a in a state where the nut member 24 is screwed is screwed into the attachment hole 13a of the rod 13 and attached. Then, the nut member 24 screwed into the shaft portion 14a is tightened toward the rod 13 in a state where the shaft portion 14a is sufficiently screwed into the mounting hole 13a. That is, the position where the nut member 24 is screwed to the shaft portion 14a is changed toward the rod 13 side, and the nut member 24 is brought into contact with the rod 13 and tightened. As a result, the shaft portion 14 a is prevented from loosening with respect to the mounting hole 13 a, and the output portion 14 is fixed to the rod 13.

[Position detector]
The position detector 21 shown in FIG. 4 includes a case 21a and a probe 21b that is displaced with respect to the case 21a. The position detector 21 is provided as a mechanism for detecting the relative position of the probe 21b with respect to the case 21a. In the position detector 21, the main part of the case 21 a and the probe 21 b are disposed inside the rod 13.

  The case 21a is installed in the cylinder body 22, and primary and secondary coils (not shown) are provided therein. The probe 21 b is attached to the rod 13 or the shaft portion 14 a of the output unit 14, and is provided so as to be displaced together with the rod 13 and the output unit 14. FIG. 4 illustrates a form in which the probe 21b is fixed to the shaft portion 14a of the output unit 14 at the end thereof. A seal member is installed between the outer periphery of the end of the probe 21 b and the inner periphery of the rod 13. Thereby, the space between the inner region of the rod 13 communicating with the pressure chamber 11b and the inner region of the mounting hole 13a are sealed.

  The probe 21b is provided with a movable iron core (not shown) that is displaced relative to the case 21a inside the coil of the case 21a. With the above configuration, the position detector 21 is configured to detect the positions of the rod 13 and the output unit 14 with respect to the cylinder 11. In the position detector 21, a signal based on an induced voltage generated in the secondary coil is generated by displacing the movable iron core with respect to the case 21 a while the primary coil is excited. Is output as The output position detection signal is transmitted to a controller (not shown). The controller that has received the position detection signal controls a control valve (not shown) that switches the supply path and the discharge path of the pressure oil to the pressure chambers (11a, 11b) based on the position detection signal. Thereby, supply and discharge of the pressure oil to and from the pair of pressure chambers (11a, 11b) are controlled, the piston 12 is displaced in the cylinder 11, and the operation of the spoiler 102 is controlled.

[Stopper member, first seal member, second seal member]
FIG. 5 is an enlarged view showing a part of FIG. As shown in FIGS. 4 and 5, the stopper member 17 is installed in the cylinder 11. The stopper member 17 is provided as a member that defines a movable range of the piston 12 in the cylinder 11 by contacting the piston 12 in the cylinder 11. The stopper member 17 defines the end position of the movable range on the connecting portion 22a side in the axial direction of the cylinder 11 as the movable range of the piston 12 within the cylinder 11.

  The position of the stopper member 17 in the cylinder 11 in the axial direction of the cylinder 11 is positioned by a stopper driving unit 18 described later. The stopper member 17 abuts against the end portion of the piston 12 on the connecting portion 22a side at the end portion on the pressure chamber 11b side, that is, the end portion on the opposite side of the connecting portion 22a side of the cylinder 11. Thereby, based on the position of the stopper member 17 positioned by the stopper driving unit 18, the movable range of the piston 12 that contacts the stopper member 17 is defined. That is, the range in which the piston 12 can move toward the connecting portion 22 a in the axial direction of the cylinder 11 is restricted to a position where it abuts against the stopper member 17. As described above, the stopper member 17 is provided as a member that defines a movable range of the piston 12 within the cylinder 11.

  Moreover, the stopper member 17 is arrange | positioned in the stopper arrangement | positioning area | region 11c which is an area | region divided in the connection part 22a side rather than the area | region where the piston 12 is arrange | positioned in the cylinder 11. FIG. In the cylinder 11, the stopper arrangement area 11c is configured as an area continuous with the area where the piston 12 is arranged, and is formed as an area formed by reducing the diameter with respect to the area where the piston 12 is arranged. Yes. The stopper member 17 is installed to be slidable along the axial direction of the cylinder 11 with respect to the inner wall of the cylinder 11 at a portion defining the stopper arrangement region 11 c in the cylinder 11. Further, the stopper member 17 is arranged in the stopper arrangement region 11 c in the cylinder 11 so that its axial direction extends along the axial direction of the cylinder 11.

  Further, the stopper member 17 is provided with through holes 17a that open at both ends of the stopper member 17 and penetrate the stopper member 17 in the axial direction. A through hole 17a penetrating the stopper member 17 in the axial direction communicates with the pressure chamber 11b. As a result, the fluid actuator 1 is configured such that the pressure of the pressure oil supplied to the pressure chamber 11b acts on both ends of the stopper member 17 through the through hole 17a in the cylinder 11. The case 21a of the position detector 21 is supported in a cantilevered manner with respect to the cylinder body 22, and is disposed in the cylinder 11 while penetrating the inside of the through hole 17a.

  The stopper member 17 is provided as a cylindrical member. The stopper member 17 has a sliding surface 17b that slides with respect to the inner wall of the cylinder 11 on the outer peripheral surface thereof, and a through hole 17a is provided on the inner side. And the stopper member 17 is provided with the circumferential groove part 17c in the outer peripheral surface of the halfway position in the axial direction. The circumferential groove portion 17c is provided so as to be recessed inward in the radial direction of the stopper member 17 and to extend in a groove shape in the circumferential direction.

  In the cylinder 11, an annular region 25 is defined as a region extending in an annular shape between the circumferential groove portion 17 c and the inner periphery of a portion that defines the stopper arrangement region 11 c in the cylinder 11. In the fluid actuator 1, the outer peripheral surface 17 b of the stopper member 17 and the inner peripheral surface of the cylinder 11 are slid in a state in which the pressure oil supplied to the pressure chamber 11 b flows into the annular region 25. It is configured to move. In the present embodiment, the first seal member 19 and the second seal member 20 are provided as a configuration that restricts the pressure oil supplied to the pressure chamber 11 b from flowing into the annular region 25.

  The first seal member 19 and the second seal member 20 are both provided as ring-shaped seal members. The first seal member 19 and the second seal member 20 are provided as O-ring seals, for example. The first seal member 19 and the second seal member 20 are attached to the outer periphery of the stopper member 17.

  The first seal member 19 is attached to the circumferential groove portion 17 c of the stopper member 17 so as to be disposed on one end side in the axial direction of the stopper member 17. More specifically, the first seal member 19 is fitted in a groove provided on the piston 12 side with respect to the circumferential groove portion 17 c on the outer periphery of the stopper member 17. This groove is provided as a groove formed on the outer peripheral surface 17 b of the stopper member 17 and extending in the circumferential direction of the stopper member 17. Further, the first seal member 19 has an inner peripheral side in contact with the outer periphery of the stopper member 17, and an outer peripheral side in contact with the inner periphery of the cylinder 11. Thereby, the 1st sealing member 19 is comprised so that the inflow to the cyclic | annular area | region 25 of the pressure oil supplied to the pressure chamber 11b may be sealed.

  The second seal member 20 is attached to the circumferential groove 17c of the stopper member 17 so as to be disposed on the other end side in the axial direction of the stopper member 17. More specifically, the second seal member 20 is fitted in a groove provided on the connecting portion 22a side with respect to the circumferential groove portion 17c on the outer periphery of the stopper member 17. This groove is provided as a groove formed on the outer peripheral surface 17 b of the stopper member 17 and extending in the circumferential direction of the stopper member 17. Furthermore, the inner peripheral side of the second seal member 20 is in contact with the outer periphery of the stopper member 17, and the outer peripheral side thereof is in contact with the inner periphery of the cylinder 11. Thus, the second seal member 20 is configured to seal the inflow of the pressure oil that is supplied to the pressure chamber 11b and also flows into the through hole 17c into the annular region 25.

[Stopper drive]
FIG. 6 is a view showing a part of the fluid actuator 1 at the position of the arrow AA shown in FIG. 5 and includes a partial cross section showing the stopper drive unit 18 and the vicinity thereof. In FIG. 6, the stopper drive unit 18 has an outer shape, not a cross section.

  The stopper driving unit 18 shown in FIGS. 4 to 6 is attached to the cylinder 11 so as to be rotatable or swingable, and is provided as a mechanism capable of driving by driving the stopper member 17. In the present embodiment, the stopper driving unit 18 is attached to the cylinder 11 so as to be rotatable. The stopper driving unit 18 includes a shaft part 26 and an eccentric part 27.

  The shaft portion 26 is supported so as to be rotatable or swingable with respect to the cylinder 11. In the present embodiment, the shaft portion 26 is supported so as to be rotatable with respect to the cylinder 11. The shaft portion 26 includes a first shaft portion 26a, a second shaft portion 26b, and an arm fixing portion 26c.

  The first shaft portion 26a and the second shaft portion 26b are each provided as a cylindrical portion, and are provided so as to sandwich the eccentric portion 27 from both sides. The first shaft portion 26 a and the second shaft portion 26 b are provided integrally with the eccentric portion 27.

  The first shaft portion 26a is rotatably supported with respect to the cylinder body 22 of the cylinder 11 via the bearing 28a. And the 2nd axial part 26b is rotatably supported with respect to the cylinder main body 22 of the cylinder 11 via the bearing 28b. Furthermore, the axial center of the first shaft portion 26a and the axial center of the second shaft portion 26b are arranged on the same straight line. Thereby, the 1st axial part 26a and the 2nd axial part 26b are provided so that it may rotate centering on the same rotation center which corresponds to those axial centers.

  The arm fixing portion 26 c is provided as a portion fixed to the arm member 16 described later in the shaft portion 26. The arm fixing part 26c is provided as a columnar part. The arm fixing portion 26c is provided integrally with the first shaft portion 26a in a state of being arranged in series with the first shaft portion 26a. Furthermore, the axial center of the arm fixing portion 26c and the axial center of the first shaft portion 26a are arranged on the same straight line. The arm fixing portion 26c is provided as a portion protruding from the cylinder 11 to the outside.

  The eccentric portion 27 includes a portion provided at a position eccentric with respect to the rotation center of the shaft portion 26, and is configured to rotate together with the shaft portion 26. The eccentric part 27 is provided integrally with the shaft part 26, and includes a first disk part 27a, a second disk part 27b, and a crank pin 27c. The first disk part 27a, the second disk part 27b, and the crank pin 27c are provided integrally. A crank pin 27c is provided between the first disk part 27a and the second disk part 27b.

  The first disk part 27a is provided as a disk-shaped part. The first disk portion 27a is provided integrally with the first shaft portion 26a on the side opposite to the arm fixing portion 26c with respect to the first shaft portion 26a in a state of being arranged in series with the first shaft portion 26a. It has been. Further, the axis of the first disk portion 27a and the axis of the first shaft portion 26a are arranged on the same straight line. Moreover, the diameter of the 1st disk part 27a is comprised larger than the diameter of the 1st axial part 26a. That is, the first disk portion 27a is provided with a diameter larger than that of the first shaft portion 26a.

  The second disk part 27b is provided as a disk-shaped part. The second disk portion 27b is provided integrally with the second shaft portion 26b on the first shaft portion 28a side with respect to the second shaft portion 26b in a state of being arranged in series with the second shaft portion 26a. Yes. Further, the axis of the second disk portion 27b and the axis of the second shaft portion 26b are arranged on the same straight line. Moreover, the diameter of the 2nd disc part 27b is comprised larger than the diameter of the 2nd axial part 26b. That is, the second disk portion 27b is provided with a diameter larger than that of the second shaft portion 26b.

  The crankpin 27 c is configured as a crankshaft portion provided at a position eccentric with respect to the shaft portion 26. The crankpin 27c has a portion extending in a columnar shape. And the crankpin 27c is provided so that the 1st disk part 27a and the 2nd disk part 27b may be connected integrally. That is, one end of the crank pin 27c is integrally connected to the first disk portion 27a. The other end of the crank pin 27c is integrally connected to the second disk portion 27b.

  The crank pin 27c is a portion on the outer peripheral side that is a radially outer portion from the rotation center of the first disc portion 27a and the second disc portion 27b with respect to the first disc portion 27a and the second disc portion 27b, respectively. Are connected together. The axial center of the crank pin 27c is arranged at a position shifted in parallel with respect to the axial centers of the first shaft portion 26a, the second shaft portion 26b, the first disk portion 27a, and the second disk portion 27b. Yes. As a result, the crank pin 27 c is provided at a position eccentric with respect to the shaft portion 26.

  Further, in the cylinder 11, the crank pin 27 c is disposed at a position where the crank pin 27 c can come into contact with the wall surface of the circumferential groove 17 c of the stopper member 17 at the outer peripheral portion thereof. Accordingly, the eccentric portion 27 is disposed in the cylinder 11 so as to be engageable with the circumferential groove portion 17c of the stopper member 17 at the crank pin 27c. That is, the stopper member 17 is provided with a circumferential groove portion 17c on the outer peripheral surface thereof as a groove portion that can be engaged with the eccentric portion 27. Then, the shaft portion 26 rotates in accordance with the displacement of the arm member 16 described later, and the eccentric portion 27 that engages with the circumferential groove portion 17c of the stopper member 17 rotates about the shaft center of the shaft portion 26. Thereby, the eccentric part 27 biases the stopper member 17 in the crankpin 27c.

[Linking mechanism]
The link mechanism 15 shown in FIGS. 1 to 4 includes one or a plurality of link members, and is provided as a mechanism for connecting the flap 103 and the arm member 16. In the present embodiment, the link mechanism 15 includes a single link member 15a.

  One end side of the link mechanism 15 is connected to the flap 103 so as to be swingable or rotatable. In the present embodiment, the link mechanism 15 is rotatably connected to the flap 103 via the connecting shaft 107 at the end 15b on one end side of the link member 15a. The end 15b of the link member 15a is rotatably connected to the connecting shaft 107 via a bearing or a bush that is a cylindrical sliding member.

  Further, the connecting shaft 107 to which the end 15b of the link member 15a is rotatably connected is fixed to the flap 103 at a position shifted upward from the fulcrum shaft 108 which is the swing center of the flap 108. For this reason, the end portion 15b of the link member 15a is displaced along an arc line centered on the fulcrum shaft 108 along with the swinging motion about the fulcrum shaft 108 of the flap 103. As a result, the link member 15a is displaced.

  The other end of the link mechanism 15 is connected to the arm member 16 so as to be swingable or rotatable. In the present embodiment, the link mechanism 15 is rotatably connected to the arm member 16 via the connecting shaft 15d at the end 15c on the other end side of the link member 15a. The connecting shaft 15d is fixed to the arm member 16. The end 15c of the link member 15a is rotatably connected to the connecting shaft 15d via a bearing or a bush that is a cylindrical sliding member.

[Arm member]
The arm member 16 shown in FIGS. 1 to 4 is provided as a member for connecting the link mechanism 15 and the stopper driving unit 18. In this embodiment, the arm member 16 is provided as an elongated plate-like member extending linearly.

  Further, the arm member 16 is connected so that one end side thereof can swing or rotate with respect to the other end side of the link mechanism 15. In this embodiment, the arm member 16 is rotatably connected to the end portion 15b on the other end side of the link member 15a via the connecting shaft 15d at the end portion 16a on the one end side.

  Further, the other end side of the arm member 16 is fixed to the stopper driving unit 18. In the present embodiment, the arm member 16 is fixed to the arm fixing portion 26c of the shaft portion 26 of the stopper driving portion 18 at the end portion 16b on the other end side.

  Here, the fixing structure between the arm member 16 and the stopper driving unit 18 will be described more specifically. As shown in FIG. 6, a fitting hole 16 c is formed through the end 16 b of the arm member 16. The fitting hole 16c penetrates the end 16b of the elongated plate-like arm member 16 in a direction perpendicular to both the longitudinal direction of the arm member 16 and the surface direction of the arm member 16 spreading in a plate shape. As formed. The direction in which the fitting hole 16c penetrates the arm member 16 is set parallel to the axial direction of the connecting shaft 15d.

  A fixing pin hole 16 d is also formed through the end 16 b of the arm member 16. The fixing pin hole 16d is provided as a hole into which a fixing pin 16e provided as a columnar member is inserted and fitted.

  The fixed pin hole 16d is formed as a hole that penetrates the end 16b of the arm member 16 in a direction perpendicular to the longitudinal direction of the arm member 16 and parallel to the surface direction of the arm member 16. ing. Furthermore, the fixing pin hole 16d is provided so as to communicate with the fitting hole 16c. Further, the central axis of the fixing pin hole 16d and the central axis of the fitting hole 16c are located at a twisted position. In the present embodiment, the fixing pin hole 16d is located at a position where it is seen to overlap with the fitting hole 16c when viewed in a perspective view from the longitudinal direction of the arm member 16. 16 is provided.

  The arm fixing portion 26c of the shaft portion 26 of the stopper driving portion 18 is inserted and fitted into the fitting hole 16c of the end portion 16b of the arm member 16. And the groove | channel 26d is provided in the part inserted in the fitting hole 16c in the arm fixing | fixed part 26c. The groove 26d is provided as a groove having a cross-sectional shape that is recessed in an arc shape. The shape of the groove 26d corresponds to the outer peripheral surface of the fixed pin 16e, and is formed in a shape in which the outer periphery of the fixed pin 16e is fitted.

  In a state where the arm fixing portion 26c is fitted in the fitting hole 16c, the groove 26d is disposed so as to face the fixing pin hole 16d. Then, the fixing pin 16e is inserted and fitted into the fixing pin hole 16d in a state where the arm fixing portion 26c is fitted into the fitting hole 16c and the groove 26d faces the fixing pin hole 16d. Thereby, the arm member 16 and the stopper drive part 18 are being fixed.

  The fixing structure between the arm member 16 and the stopper driving unit 18 described above is an example. The arm member 16 and the stopper driving unit 18 may be fixed by a fixing structure other than those described above.

[Operation of fluid actuator]
Next, the operation of the fluid actuator 1 will be described. When the spoiler 102 is driven by the fluid actuator 1, a control valve (not shown) is switched based on a command from a controller (not shown), and pressure oil is supplied to the cylinder 11 of the fluid actuator 1. Supply and discharge are performed. With the supply and discharge of the pressure oil, the piston 12 is displaced, and the rod 13 is displaced with the piston 12 so as to expand and contract with respect to the cylinder 11.

  As described above, the rod 13 is expanded and contracted with respect to the cylinder 11 so that the output unit 14 is displaced together with the rod 13. Then, the spoiler 102 is driven by the output unit 14. Accordingly, the spoiler 102 is driven so as to swing with respect to the blade 101 about the fulcrum shaft 106.

  In FIG. 1, the rod 13 is contracted with respect to the cylinder 11. From this state, when the rod 13 is displaced so as to extend relative to the cylinder 11, the spoiler 102 is driven to swing upward. On the other hand, when the spoiler 102 is driven so as to be in the state shown in FIG. 1 from the state where it rises upward, the rod 13 is controlled to be displaced so as to contract with respect to the cylinder 11. As a result, the spoiler 102 is driven to swing downward.

  Next, the operation of the fluid actuator 1 when the spoiler 103 is drooped and when the spoiler 103 is displaced from the droop position to the neutral position will be described. That is, the operation of the fluid actuator 1 accompanying the operation of the flap 103 will be described.

  The flap 103 is driven by an actuator for driving the flap 103 (not shown). When the flap 103 is driven, the link member 15 a that is rotatably connected to the flap 103 by the connecting shaft 107 is displaced with the operation of the flap 103. As the link member 15a is displaced, the arm member 16 is displaced.

  When the arm member 16 is displaced, with the displacement of the arm member 16, the stopper driving unit 18 that is rotatably supported at the shaft portion 26 with respect to the cylinder 11 rotates about the shaft portion 26. The stopper drive unit 18 rotates to drive the stopper member 17 so that the position of the stopper member 17 in the cylinder 11 is changed according to the displacement of the arm member 16.

  As described above, when the flap 103 is driven so that the rear end portion of the flap 103 swings downward, the drooping operation of the spoiler 103 is performed. That is, the fluid actuator 1 drives the spoiler 103 in accordance with the operation of the flap 103 so that the gap between the spoiler 102 and the flap 103 does not become large.

  In the state of FIG. 1, the flap 103 is in the upward position, and the spoiler 102 is in the neutral position. From this state, when the flap 103 is driven so that the rear end portion of the flap 103 swings downward, a droop operation is performed and the state shown in FIG. 2 is obtained. That is, the flap 103 is in the downward position and the spoiler 102 is in the droop position. FIG. 7 is an enlarged cross-sectional view of a part of the fluid actuator 1 in the state shown in FIG. 1, and is an enlarged cross-sectional view showing the stopper member 17 and the vicinity thereof. On the other hand, FIG. 5 is an enlarged cross-sectional view showing a part of the fluid actuator 1 in the state shown in FIG. 2, and is an enlarged cross-sectional view showing the stopper member 17 and the vicinity thereof.

  When the flap 103 is driven to swing downward, the link member 15a and the end portion 16a of the arm member 16 are displaced toward the flap 103 side. Then, the shaft portion 26 of the stopper driving portion 18 rotates counterclockwise in FIG. As a result, the crank pin 27c is displaced toward the connecting portion 22a, and the state of the fluid actuator 1 shifts from the state shown in FIG. 7 to the state shown in FIG. When the crank pin 27c engaged with the circumferential groove 17c of the stopper member 17 is displaced, the stopper member 17 is driven toward the connecting portion 22a along the axial direction of the cylinder 11. At this time, the stopper member 17 is driven not only by the crank pin 27c engaged with the circumferential groove 17c but also by an urging force acting from the piston 12. The urging force acting from the piston 12 is generated when pressure oil higher in pressure than the pressure chamber 11b is supplied to the pressure chamber 11a.

  As described above, when the stopper member 17 is driven toward the connecting portion 22a, the end position on the connecting portion 22a side in the movable range of the piston 12 in the cylinder 11 is further changed to the connecting portion 22a side. Will be. Thereby, the position of the rod 13 and the output portion 14 relative to the cylinder 11 in a state where the rod 13 is contracted with respect to the cylinder 11 is also changed to the connecting portion 22a side. With the displacement of the rod 13 and the output unit 14, the spoiler 102 is driven so that the rear end portion of the spoiler 102 swings downward. That is, the drooping operation of the spoiler 102 is performed. Thereby, it adjusts so that the clearance gap between the rear-end part of the spoiler 102 and the front-end part of the flap 103 may not become large.

  On the other hand, when the flap 103 is driven to swing upward, the spoiler 102 is displaced from the droop position to the neutral position. At this time, the link member 15 a and the end portion 16 a of the arm member 16 are displaced toward the opposite side of the flap 103 with the operation of the flap 103. Then, the shaft portion 26 of the stopper driving portion 18 rotates in the clockwise direction in FIG. As a result, the crank pin 27c is displaced toward the piston 12, and the state of the fluid actuator 1 shifts from the state shown in FIG. 5 to the state shown in FIG. The crank pin 27 c that engages with the circumferential groove 17 c of the stopper member 17 is displaced, so that the stopper member 17 is driven toward the piston 12 along the axial direction of the cylinder 11.

  As described above, when the stopper member 17 is driven toward the piston 12 side, the position of the end portion on the coupling portion 22a side in the movable range of the piston 12 within the cylinder 11 is changed to the piston 12 side. Become. Thereby, the position with respect to the cylinder 11 of the rod 13 and the output part 14 in the state which the rod 13 contracted with respect to the cylinder 11 is also changed to the piston 12 side. With the displacement of the rod 13 and the output unit 14, the spoiler 102 is driven so that the rear end portion of the spoiler 102 swings slightly upward. In other words, the spoiler 103 is moved from the droop position to the neutral position.

[effect]
As described above, according to the present embodiment, when the flap 103 is driven, the link mechanism 15 connected to the flap 103 is displaced. As the link mechanism 15 is displaced, the arm member 16 rotates the stopper driving unit 18. At this time, the stopper driving unit 18 changes the position of the stopper member 17 in the cylinder 11 according to the displacement of the arm member 16. And the movable range of the piston 12 prescribed | regulated in the cylinder 11 is changed. Accordingly, the positions of the rod 13 and the output unit 14 with respect to the cylinder 11 in a state where the rod 13 is contracted with respect to the cylinder 11 are also changed. By the above, a droop function can be achieved reliably. That is, when the flap 103 is driven so that the rear end portion of the flap 103 swings downward, the operation of the flap 103 is performed so that the gap between the spoiler 102 and the flap 103 does not become large. In response to this, the spoiler 102 can also be driven. That is, the position of the rod 13 and the output unit 14 with respect to the cylinder 11 in a state where the rod 13 is contracted with respect to the cylinder 11 is displaced, and the rear end portion of the spoiler 102 swings downward as the output unit 14 is displaced. Thus, the spoiler 102 is driven. And it adjusts so that the clearance gap between the rear-end part of the spoiler 102 and the front-end part of the flap 103 may not become large.

  And according to this embodiment, with respect to the basic composition of fluid actuator 1 provided with cylinder 11, piston 12, rod 13, and output part 14, it is provided with stopper member 17, stopper drive part 18, link mechanism 15, and arm member 16. By adding a simple mechanical structure, a droop function can be realized. Furthermore, according to the present embodiment, the droop function is not realized by electrical position control as in the prior art, but is realized by a simple mechanical structure. For this reason, contact between the spoiler 102 and the flap 103 does not occur due to the control intersection. In addition, the gap between the spoiler 102 and the flap 103 does not increase with the control within a range that has a sufficient margin for the control intersection. That is, it is possible to suppress the deterioration of the aerodynamic characteristics of the wing. Therefore, when realizing the droop function, it is possible to suppress a decrease in aerodynamic characteristics of the blade 101 and to reliably suppress the occurrence of contact between the spoiler 102 and the flap 103.

  Further, according to the present embodiment, the stopper driving unit 18 mechanically interlocked with the operation of the flap 103 via the link mechanism 15 and the arm member 16 changes the position of the stopper member 17 in the cylinder 11. Thus, the movable range of the piston 12 in the cylinder 11 is changed. Thereby, the position with respect to the cylinder 11 of the output part 14 in the state which the rod 13 contracted with respect to the cylinder 11 is changed, and a droop function is implement | achieved. For this reason, the drooping operation of the spoiler 102 is performed without the position of the rotating shaft 104 that is the swing center position of the cylinder 11 being displaced. Thereby, when the rod 13 extends from the cylinder 11 and the spoiler 102 stands up with respect to the blade 101, it is possible to prevent variation in the standing angle of the spoiler 102. That is, variation in the steering angle of the spoiler 102 can be prevented.

  Therefore, according to the present embodiment, the droop function can be realized by a simple mechanical structure, the deterioration of the aerodynamic characteristics of the blade 101 can be suppressed, and the occurrence of contact between the spoiler 102 and the flap 103 can be reliably suppressed. Thus, it is possible to provide the fluid actuator 1 that can prevent displacement of the swing center position of 11.

  According to the present embodiment, the stopper member 17 is provided as a member that slides in the axial direction in the cylinder 11. For this reason, the stopper member 17 which drives in the cylinder 11 by the stopper drive part 18 and prescribes | regulates the movable range in the cylinder 11 of the piston 12 is realizable by simple structure.

  Further, according to the present embodiment, since the stopper member 17 is provided with the through hole 17 a, the pressure of the pressure oil supplied to the pressure chamber 11 b acts on both ends of the stopper member 17. For this reason, the stopper member 17 is prevented from being strongly pressed against one of the cylinders 11 in the axial direction by the pressure of the fluid supplied to the pressure chamber 11 b in the cylinder 11. Thereby, when the stopper member 17 is driven, the influence of the action of the pressure of the fluid supplied to the pressure chamber 11b can be canceled and suppressed in the axial direction. In other words, the stopper member 17 can be easily driven by the stopper driving portion 18.

  Further, according to the present embodiment, the stopper member 17 that can easily drive the stopper member 17 by the stopper driving unit 18 while suppressing the influence of the pressure of the pressure oil supplied to the pressure chamber 11b is simplified. Can be realized with a structure.

  Further, according to the present embodiment, the annular region 25 where the inflow of the pressure oil supplied to the pressure chamber 11b is restricted between the circumferential groove 17c of the outer peripheral surface 17b of the stopper member 17 and the inner periphery of the cylinder 11 is provided. Partitioned. For this reason, a part of the stopper drive unit 18 can be disposed in the annular region 25 where the inflow of the pressure oil supplied to the pressure chamber 11 b is restricted, and the stopper drive unit 18 can be brought into contact with the stopper member 17. That is, the driving force from the stopper driving unit 18 can be transmitted to the stopper member 17 in the annular region 25 outside the region where the pressure of the pressure oil supplied to the pressure chamber 11 b directly acts. Thereby, the structure for driving the stopper member 17 by the stopper drive part 18 is realizable with a simple structure. Further, in the stopper member 17, a portion for partitioning a region where a part of the stopper driving portion 18 is arranged is provided as a circumferential groove portion 17 c extending along the circumferential direction of the stopper member 17. For this reason, the stability of the sliding operation of the stopper member 17 with respect to the cylinder 11 can be further improved.

  Further, according to the present embodiment, the annular region 25 is sealed by the first seal member 19 and the second seal member 20 on both sides in the axial direction of the stopper member 17. Therefore, with a simple configuration in which the first seal member 19 and the second seal member 20 are attached to the outer periphery of the stopper member 17, the region between the annular region 25 and the region where the pressure of the pressure oil supplied to the pressure chamber 11 b acts. The sealing performance can be improved.

  In addition, according to the present embodiment, the stopper drive unit 18 that biases and drives the stopper member 17 with the displacement of the arm member 16 is configured by a simple configuration in which the shaft portion 26 and the eccentric portion 27 are provided. Can do. And according to this embodiment, the eccentric part 27 of the stopper drive part 18 can be easily formed with a simple structure including the crank pin 27c which is a crankshaft part.

  Further, according to the present embodiment, the stopper member 17 can be biased by the groove portion (circumferential groove portion) 17 c of the outer peripheral surface 17 b of the stopper member 17 by the eccentric portion 27 that rotates together with the shaft portion 26. For this reason, the structure for driving the stopper member 17 by the eccentric part 27 can be realized with a simple structure in which the groove part (circumferential groove part) 17 c is provided on the outer peripheral surface 17 b of the stopper member 17.

[Modification]
The embodiments of the present invention have been described above. However, the present invention is not limited to the above-described embodiments, and various modifications can be made as long as they are described in the claims. For example, the following modifications may be made.

(1) In the above-described embodiment, the first moving blade is configured as a spoiler and the second moving blade is configured as a flap. However, this need not be the case. The present invention may be applied to a case where the combination of the first moving blade and the second moving blade is in a form other than the form in which the spoiler and the flap are used.

(2) In the above-described embodiment, the mode in which the rod is provided integrally with the piston has been described as an example, but this need not be the case. A form in which the rod is fixed to the piston may be implemented.

(3) In the above-described embodiment, an example in which the output unit is fixed to the rod has been described as an example, but this need not be the case. A form in which the output unit is provided integrally with the rod may be implemented.

(4) In the above-described embodiment, an example has been described in which the stopper member abuts on the piston in the cylinder to define the movable range of the piston in the cylinder. However, this need not be the case. A form in which the stopper member abuts on the rod may be implemented. Or the form which a stopper member contact | abuts to both a piston and a rod may be implemented. That is, the stopper member may be configured to define a movable range of the piston in the cylinder by contacting the piston and / or the rod in the cylinder.

(5) In the above-described embodiment, the eccentric portion of the stopper driving portion has been described by taking an example in which the eccentric portion rotates with the shaft portion including a portion provided at a position eccentric with respect to the rotation center of the shaft portion. It doesn't have to be on the street. A mode in which the eccentric portion of the stopper driving portion swings with the shaft portion including a portion provided at a position eccentric with respect to the swing center of the shaft portion may be implemented.

(6) In the above-described embodiment, the embodiment in which the position detector for detecting the position of the rod and the output unit with respect to the cylinder is described as an example, but this need not be the case. A fluid actuator without a position detector may be implemented.

(7) In the above-described embodiment, the form of the link mechanism having one link member has been described as an example, but this need not be the case. A fluid actuator including a link mechanism having a plurality of link members may be implemented.

(8) In the above-described embodiment, the form of the eccentric portion including the crankshaft portion provided at a position eccentric with respect to the shaft portion has been described as an example, but this need not be the case. The eccentric portion may be configured to rotate or swing together with the shaft portion including a portion provided at a position eccentric with respect to the rotation center or swing center of the shaft portion. For example, a fluid actuator including a stopper driving unit having an eccentric part including a cam portion provided at a position eccentric with respect to the shaft part may be implemented.

  FIG. 8 is a cross-sectional view showing a fluid actuator 1a according to the above modification. FIG. 8 is illustrated as a diagram corresponding to FIG. 4 in the above-described embodiment. The fluid actuator 1a according to the modification is configured in the same manner as the fluid actuator 1 of the above-described embodiment. However, the fluid actuator 1a according to the modified example is different from the fluid actuator 1 of the above-described embodiment in the configuration of the eccentric portion 30 of the stopper drive unit 29.

  Hereinafter, regarding the electric actuator 1a according to the modified example, a configuration different from the above-described embodiment will be described. In addition, in the modification shown in FIG. 8, elements that are configured in the same manner as in the above-described embodiment are denoted by the same reference numerals as those in the above-described embodiments, or the same reference numerals as in the above-described embodiments. The description is omitted by quoting.

  The stopper drive unit 29 in the fluid actuator 1a includes a shaft portion 26 and an eccentric portion 30. The shaft portion 26 of the stopper driving portion 29 is configured in the same manner as the shaft portion 26 of the stopper driving portion 18 of the above-described embodiment. On the other hand, the eccentric part 30 of the stopper driving part 29 is different from the eccentric part 27 of the stopper driving part 18 in that the crank pin 27c is not provided and the cam part 30a is included. FIG. 8 shows a cross section of the cam portion 30a.

  The cam portion 30a of the eccentric portion 30 is provided integrally with the shaft portion 26, for example. The cam portion 30 a is provided at a position eccentric with respect to the shaft portion 26. That is, the cam portion 30 a is disposed at a position that is shifted radially outward from the rotation center of the shaft portion 26. Further, the cam portion 30 a is disposed in the cylinder 11 at a position where it can abut against the wall surface of the circumferential groove 17 c of the stopper member 17. Thereby, the eccentric part 30 is arrange | positioned in the cylinder 11 so that engagement with the circumferential groove part 17c of the stopper member 17 in the cam part 30a is possible. Then, the shaft portion 26 rotates with the displacement of the arm member 16, and the eccentric portion 30 that engages with the circumferential groove portion 17 c of the stopper member 17 rotates about the shaft center of the shaft portion 26. Thereby, the eccentric part 30 biases the stopper member 17 in the cam part 30a.

  According to the above modification, the eccentric portion 30 of the stopper driving portion 29 can be easily formed with a simple structure including the cam portion 30a. Note that the cross-sectional shape of the cam portion 30a shown in FIG. 8 is an example, and the shape of the cam portion may be variously changed.

  The present invention is installed in a wing in which the first moving blade on the front side and the second moving blade on the rear side are installed side by side along the longitudinal direction of the wing of the aircraft, and fluid is supplied and discharged. The present invention can be widely applied to a fluid actuator that operates in order to drive the first moving blade with respect to the blade.

DESCRIPTION OF SYMBOLS 1 Fluid actuator 11 Cylinder 12 Piston 13 Rod 14 Output part 15 Link mechanism 16 Arm member 17 Stopper member 18 Stopper drive part

Claims (10)

The first moving blade on the front side and the second moving blade on the rear side are installed side by side along the front-rear direction of the wing of the aircraft, and operates by supplying and discharging fluid. A fluid actuator that drives the first blade to oscillate relative to the blade,
A cylinder to which fluid is supplied and discharged;
A piston that partitions a pressure chamber in which fluid is supplied and discharged in the cylinder and slides against an inner wall of the cylinder;
A rod that is integrally provided or fixed to the piston and that is displaced to expand and contract with respect to the cylinder;
An output unit that is integrally provided or fixed to the rod and connected to the first blade, and is displaced together with the rod to drive the first blade;
A stopper member for defining a movable range of the piston in the cylinder by contacting at least one of the piston and the rod in the cylinder;
A stopper drive unit that is attached to the cylinder so as to be rotatable or swingable, and that can be driven by urging the stopper member;
A link mechanism including one or a plurality of link members, one end side of which is swingably or rotatably connected to the second moving blade;
An arm member whose one end side is connected to the other end side of the link mechanism so as to be swingable or rotatable, and whose other end side is fixed to the stopper driving unit;
With
The link mechanism is displaced in accordance with the operation of the second moving blade,
The arm member is displaced with the displacement of the link mechanism,
The stopper driving part rotates or swings with the displacement of the arm member,
The stopper driving unit drives the stopper member so as to change the position of the stopper member in the cylinder according to the displacement of the arm member by rotating or swinging. Actuator. The fluid actuator according to claim 1,
The fluid actuator according to claim 1, wherein the stopper member is slidably installed along the axial direction of the cylinder with respect to the inner wall of the cylinder. The fluid actuator according to claim 2,
The stopper member is disposed in the cylinder such that its axial direction extends along the axial direction of the cylinder,
The stopper member is provided with through holes that open at both ends of the stopper member and penetrate the stopper member in the axial direction.
In the cylinder, the fluid pressure supplied to the pressure chamber acts on both ends of the stopper member via the through hole. The fluid actuator according to claim 3,
The stopper member is provided as a cylindrical member, and has a sliding surface that slides with respect to the inner wall of the cylinder on an outer peripheral surface thereof, and the through hole is provided on the inner side. Fluid actuator. The fluid actuator according to claim 4,
The stopper member is provided with a circumferential groove portion provided on the outer peripheral surface of the intermediate position in the axial direction so as to be recessed inward in the radial direction of the stopper member and to extend in a groove shape in the circumferential direction,
In a state where the fluid supplied to the pressure chamber is restricted from flowing into an annular region defined as an annularly extending region between the circumferential groove and the inner periphery of the cylinder, the stopper member A fluid actuator, wherein an outer peripheral surface slides with an inner peripheral surface of the cylinder. The fluid actuator according to claim 5,
A first seal member and a second seal member attached to the outer periphery of the stopper member;
The first seal member is attached to the circumferential groove portion so as to be disposed on one end side in the axial direction of the stopper member, and the fluid supplied to the pressure chamber is supplied to the annular region. Sealing the inflow,
The second seal member is attached to the circumferential groove portion so as to be disposed on the other end side in the axial direction of the stopper member, and the fluid supplied to the pressure chamber is supplied to the annular region. A fluid actuator characterized by sealing an inflow. The fluid actuator according to any one of claims 1 to 6,
The stopper driving portion includes a shaft portion that is rotatably or swingably supported with respect to the cylinder, and a portion provided at a position eccentric to the rotation center or swing center of the shaft portion. An eccentric part that rotates or swings with the shaft part,
The fluid actuator according to claim 1, wherein the shaft portion rotates or swings with the displacement of the arm member, and the eccentric portion biases the stopper member. The fluid actuator according to claim 7,
The fluid actuator according to claim 1, wherein the eccentric portion includes a crankshaft portion or a cam portion provided at a position eccentric with respect to the shaft portion. The fluid actuator according to claim 7 or 8,
The fluid actuator according to claim 1, wherein the stopper member is provided with a groove portion engageable with the eccentric portion on an outer peripheral surface thereof. The fluid actuator according to claim 5 or 6, wherein
The stopper driving portion includes a shaft portion that is rotatably or swingably supported with respect to the cylinder, and a portion provided at a position eccentric to the rotation center or swing center of the shaft portion. An eccentric part that rotates or swings with the shaft part,
The eccentric part is arranged to be engageable with the circumferential groove part,
The fluid actuator according to claim 1, wherein the shaft portion rotates or swings with the displacement of the arm member, and the eccentric portion biases the stopper member.

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