ACTUATOR

Abstract

A linear actuator comprising: an axially moveable member; a housing within which the axially moveable member is mounted for linear movement relative to the housing; drive means to move the axially moveable member between an extended axial position and a retracted axial position; and one or more springs provided to absorb impact from axial movement of the axially moveable member at the extended axial position and/or at the retracted axial position.

Claims

1. A linear actuator comprising: an axially moveable member; a housing within which the axially moveable member is mounted for linear movement relative to the housing; drive means to move the axially moveable member between an extended axial position and a retracted axial position; and one or more springs provided to absorb impact from axial movement of the axially moveable member at the extended axial position and/or at the retracted axial position.

2. The actuator of claim 1 wherein the drive means is one of mechanical, electrical or hydraulic.

3. The actuator of claim 1, wherein the axially moveable member is provided as a first axially moveable member mounted and axially moveable relative to a second axially moveable member.

4. The actuator of claim 1, wherein the one or more springs comprises a spring mounted at each end of the axially moveable member.

5. The actuator of claim 3, wherein the one or more springs comprises a spring at each end of each of the first and second axially moveable member.

6. The actuator of claim 1, wherein the one or more springs comprise friction springs.

7. The actuator of claim 6, wherein the friction springs comprise Ringfeder friction springs.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0015] FIG. 1 is a cross-sectional view of an actuator according to the disclosure.

[0016] FIG. 2 is a detail view of a damping arrangement of the disclosure with the actuator in a stowed/stowing position.

[0017] FIG. 3 is a detail view of a damping arrangement of the disclosure with the actuator in a deploy/deploying position.

[0018] FIG. 4 is a simplified view of an example spring.

[0019] FIG. 5 shows how the spring force of a spring such as in FIG. 4 varies on application of a load.

DETAILED DESCRIPTION

[0020] Referring first to FIG. 1, an electric actuator is shown comprising an axially moveable member 1 mounted within a cylinder 2. The axially moveable member is arranged to move axially or linearly with respect to the cylinder to extend from and retract into the open end 3 of the cylinder 2. The end of the axially moveable member at the open end of the cylinder is coupled to or arranged to be coupled to the component or surface to be moved, by connecting means e.g. an eye-bolt. In the example shown, the axially moveable member 1 comprises two rods, one 1 inside the other 1. A single rod could also be used.

[0021] Movement of the axially moveable member 1 is controlled by an electric motor input 5 controlled by a motor controller. The motor and motor controller can be of any known type and is mounted upstream of input 5. For a hydraulic actuator, the motor and motor controller would be replaced by any known hydraulic supply and control arrangement to cause movement of the axially moveable member by hydraulic fluid pressure. Gearing, such as ball screw gearing 7 may be provided to translate rotary motion of the rotor 5 to linear motion of the axially moveable member 1. Here, a right angle gear box 7a rotates screw 7 providing gearing to nut 7b transferring torque to linear motion of the axially moveable member 1.

[0022] The axially moveable member 1 moves between a deploy position and a stow position. These positions will vary depending on the application. As an example, such actuators may be used in a RAT or TRAS system of an aircraft, wherein, as shown, the retracted position of the axially moveable member is the deploy position and the extended position is the stow position. In other applications, the stow and deploy positions may be the retracted and extended positions respectively. In these respective positions, a stop or end surface prevents further axial movement in that direction.

[0023] As mentioned above, a high inertial mass can be created by the movement of the member, which can cause the member to crash against the stop with high impact. This can cause damage and/or wear to the assembly components.

[0024] To avoid or mitigate such impact, the actuator of the present disclosure incorporates one or more friction springs 8, 8 axially positioned with respect to the axially moveable member and positioned between the axially moveable member and the respective stops or ends to absorb the impact.

[0025] Preferably, a friction spring is provided at each of the deploy (8) and stow (8) positions, but advantages are obtained even with a spring at only one of those locations.

[0026] In the example shown, where the axially moveable member comprises an inner and an outer rod, it is also possible to provide four such springs at the two extremes of movement of each rod.

[0027] Whilst any springs would reduce impact, friction springs are preferred as a large amount of energy is generated by the friction caused by movement of the axially moveable member. The friction springs act to absorb a large amount of energy within a small volume.

[0028] The friction springs are preferably fully sealed within the actuator to ensure consistent lubrication and good protection against external foreign bodies. Further, the incorporation of springs into existing actuators e.g. TRAS, is simple and the springs can be tuned to meet the required energy absorption.

[0029] Most preferably, the system uses friction springs such as Ringfeder friction springs (also known as Feder rings). As shown in FIG. 4, such a spring consists of a series of separate inner 11 and outer 10 rings with mating taper faces. Under the application of an axial load, the wedge action of the taper faces expands the outer rings and contracts the inner rings radially allowing axial deflection.

[0030] Friction and hoop stresses between the rings allows the axial force to be elevated to the peak force and the subsequent rebound force is also lower, as shown in FIG. 5, thus the ringfeders are both springs and dampers.

[0031] The friction springs absorb drive motor kinetic energy to ensure excessive torque being experienced by internal gears of the system.

[0032] Such springs could also be incorporated in hydraulic actuators to supplement or replace existing damping.

[0033] The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the present disclosure. As used herein, the singular forms a, an and the are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms comprises and/or comprising, when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, element components, and/or groups thereof.

[0034] While the present disclosure has been described with reference to an exemplary embodiment or embodiments, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the present disclosure. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the present disclosure without departing from the essential scope thereof. Therefore, it is intended that the present disclosure not be limited to the particular embodiment disclosed as the best mode contemplated for carrying out this present disclosure, but that the present disclosure will include all embodiments falling within the scope of the claims.