Patent ID: 12240590

DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS

FIG.1shows an actuator assembly2in a schematic view. Here, the actuator assembly2comprises a geared rotary actuator4having a plurality of actuator slices6, which comprise a planetary gear. All actuator slices6are attached to one another along a central axis8. An input section10is provided for introducing an externally provided rotary motion into the actuator assembly2. As an example, then input section10is coupled to a drive unit12, which may comprise a redundant arrangement of two motors, a differential gear, and an output shaft. The drive unit12is connected to a first shaft14, which is connected to a first bevel gear16. In doing so, the drive unit12may be placed in a region lateral to the central axis8. The input section10comprises an input shaft18that extends along the central axis8from a first end20to a second end22. At the second end22a second bevel gear24is provided, which is connected to a second shaft26. Here, the brake28as well as a system position sensor30are arranged.

The actuator slices6are coupled with first lugs32couplable with a fixed component34, such as a wing box, which may comprise stiffening elements such as stringers, spars and skin portions. In this example, the actuator assembly2is arranged in a wing structure of an aircraft, which is described further below. Also, output gears (not shown) of the actuator slices6are coupled with second lugs36, which are coupled with a movable surface38. The surface38may be a wing tip portion, which is swivably arranged on the central axis8, which is thus also a swivel axis. By driving the geared rotary actuator4, the second lugs36swivel the surface38about the central axis8.

For reducing structural loads in certain conditions it is desirable to decouple the surface38from the fixed component34. For achieving this, it is decouplable from the input section10, such that it is freely swivable. In the exemplary embodiment shown inFIG.1a first clutch40and a second clutch42are provided. The first clutch40is arranged in the region of the first end20. The second clutch42is arranged in the region of the second end22. Both clutches40and42are adapted to selectively disengage the input shaft18from the actuator slices6. In this exemplary embodiment, the clutches40and42are arranged upstream of the geared rotary actuator4, i.e. between the input shaft18and the geared rotary actuator4.

The arrangement of elements shown inFIG.1, i.e. gears, gearboxes, brake, drive unit and shaft elements depends on the installation constraints and is not limiting the subject-matter of the invention. It may also be possible to use an arrangement without shafts and gearboxes, e.g. having drive units directly mounted on the geared rotary actuator.

FIG.2shows a detail of on actuator slice6, the input section10and the first clutch40. The input section10exemplarily comprises an input gear stage11, which is coupled to the input shaft18. The detailed setup of this input gear stage11is not crucial for the invention and it may be selected by a skilled person appropriately.

For transferring torque from the input shaft18to the first actuator slice6, the first clutch40comprises a first element in the form of a first clutch disc46and a second element in the form of a second clutch disc48. The second clutch disc48is coupled with a sun gear44through a hollow shaft45. A lever50is movable by a clutch actuator (not shown herein), which is designed to let the clutch discs46and48contact or to separate them from each other. The first clutch disc46comprises a first toothing52, while the second clutch disc48comprises a second toothing54. The toothings52and54are designed to complement each other, such that they mesh with in a torque-transferring manner when the clutch discs46and48contact each other. Hence, the first clutch40can selectively couple the actuator slice6with the input shaft18or decouple it therefrom.

For the sake of completeness, the actuator slice6comprises a ring gear56, which meshes with planet gears58. The planet gears58may be supported by a cage60, which is coupled to the fixed component34through the first lug32. The ring gear56constitutes the output gear and comprises the second lug36for driving the movable component38.

FIG.3shows simplified illustrations of the first clutch40and the second clutch42. Here, the first clutch40and the second clutch42comprise a first clutch disc46and a second clutch disc48. Both clutches40and42are shown in the disengaged state, where the toothings52and54are separated from each other. In each of the clutches40and42, a clutch actuator62is connected to the clutch lever50, which exemplarily moved the first clutch disc46along the central axis8. The clutch actuator62may be provided in the form of a hydraulic actuators, or an electrical or electromechanical actuators, e.g. in the form of a ball spindle drive with a low gear ratio.

FIG.4shows another actuator assembly64, which differs from the assembly2ofFIG.1. Here, clutches66are provided, which may be designed similarly to the first clutch40and the second clutch42. However, in this exemplary embodiment the clutches66are fully integrated into a geared rotary actuator68, i.e. directly in actuator slices70to selectively decouple the respective output gears56from the surface38. This is further explained in conjunction withFIG.5.

Here, the output gear56is arranged inside an output member57, which is coupled with two first clutch discs46at both axial sides. Two second clutch discs48can be brought into engagement or disengagement with the first clutch discs46for selectively coupling the output gear56with the output member57. For this, the second clutch discs48are movable through clutch actuators62, which are provided as hydraulic actuators and are selectively supplied with hydraulics fluid through a solenoid valve72. For providing a reversing force, springs73are provided. The valve72may comprise a very low reaction time in the region of 10 to 20 ms. Thus, upon request, both second clutch discs48can rapidly be disengaged from the first clutch discs46to disengage the associated output gear56. All actuators62may be attached to the output member57and coupled with a flexible hose74for receiving hydraulics fluid. Thus, if the output member57moves about the central axis8, the flexible hose74compensates a positional offset.

FIG.6shows a still further exemplary embodiment in the form of an actuator assembly76. Here, a geared rotary actuator78has several actuator slices80with integrated clutches82. Here, each output gear56comprises a first clutch disc46, which is engageable or disengageable from a second clutch disc48. However, different than inFIG.5, only one axial side of the output gear56comprises such an arrangement. This is further explained in conjunction withFIG.7.

It becomes apparent that by moving all output gears56along the central axis8towards the first end20, the first clutch discs46are disengaged from the second clutch discs48. To reverse this motion, a spring unit84is provided in the region of the first end20, which is compressed during said motion and which expands if an actuation force is removed. A clutch actuator86is arranged in the region of the second end22. As shown inFIG.7, sleeve bearings88are provided on the side of the output gear56facing away from the associated first clutch disc46.

A component position sensor90is directly coupled with the component38in addition to the system position sensor30. Thus, a control unit may gather the exact position of the movable component38after it has been decoupled from the input shaft18.

FIG.8shows an upper part of a sectional view of a further actuator assembly92, which is a modification of the assembly64shown inFIGS.4and5. Here, the ring gear56is separated from the second lugs36, which are indicated by an arrow onto a first clutch disc46of a clutch93. The first clutch disc46as well as the ring gear56comprise circumferential grooves94and96at the same axial position, which enclose a first set of rollers98for rotatably supporting the first clutch disc46on the ring gear56. The first toothing52is provided for receiving rollers100, which are rotatably supported on a second clutch disc48. Exemplarily, this is conducted by a needle bearing102held by a bolt104pressed or screwed into the second clutch disc48. The second clutch disc48is axially and concentrically supported by a second set of rollers106running in axial grooves108and110provided in the second clutch disc48and the ring gear56. A spring73is placed between a flange112of the ring gear56and the second clutch disc48and provides a reversing force to clutch actuators62. As shown inFIG.5, a hose74is coupled with the clutch actuators62to supply hydraulics fluid. In this exemplary embodiment, very short reaction times for engaging or disengaging the clutch93can be realized.

Lastly,FIG.9shows an aircraft114having a wing structure116comprising a fixed wing portion118, a hinge120and a movable wing tip portion122. For moving the wing tip portion122, and actuator assembly2is provided, wherein the central axis8of the actuator assembly2is parallel to a longitudinal axis x of the aircraft114as an example. However, it may also enclose an angle of up to 10 or 20° with the longitudinal axis. The other actuator assemblies64,76and92are also applicable to be integrated into the aircraft114.

In addition, it should be pointed out that “comprising” does not exclude other elements or steps, and “a” or “an” does not exclude a plural number. Furthermore, it should be pointed out that characteristics or steps which have been described with reference to one of the above exemplary embodiments may also be used in combination with other characteristics or steps of other exemplary embodiments described above. Reference characters in the claims are not to be interpreted as limitations.