BACKGROUND
Actuators are widely used throughout many industries to control the
movement of various components. Some actuators are configured to transfer
rotational energy between components to, ultimately, effectuate movement of a
surface or component. Similarly, some actuators are configured to transfer linear
energy between components to, ultimately, effectuate movement of a surface or
component. Still further, some actuators are configured to transfer both rotational and
linear energy between components to, ultimately, effectuate movement of a surface or
component.
Some actuator applications require reliable, fail-free or fails-safe mechanical
or electro-mechanical actuators. More specifically, many applications require
actuators which include mechanisms that limit an input force andlor release the
actuated load during fail situations, such as when one component of the actuation
system in which the actuator is installed fails or is otherwise compromised and
thereby limits or prevents movement of the actuated surface or component (i.e., the
load recipient). Such mechanisms limit or prevent damage to components during
overload situations and free the actuated load from a jam in the actuation system. For
example, some actuation systems employ torque limiters or overload clutches which
automatically limit torque throughput by slipping or shearing of components at a
certain predefined maximum torque. Similarly, some actuators employ mechanisms
which automatically limit axial force throughput by slipping or shearing of
components at a certain predefined maximum axial force. However, these
mechanisms are often unreliable, inaccurate, cannot be customized (as the "release"
parameter often cannot be changed after installation), are difficult to reset after
"release" and are difficult to scale. These mechanisms are also typically designed to
only limit force in a particular direction (e.g., only limit torque or only limit axial
force).
These types of mechanism are therefore not well suited for applications in
which prevention of overload situations and release of the actuated surface or
components during a jam is vital. For example, in the aviation industry, reliability of
actuators relied upon for control of flight control surfaces is paramount. Due to the
operating conditions of flight control surfaces, movement of flight control surfaces in
aircraft is effectuated by redundant actuators. When one of these actuators fails, such
as when a jam occurs, it is vitally important that the failed actuator does not prevent
movement of the flight control surface to which the actuator is coupled. Typically,
movement of a flight control surface directly results in movement of the components
of the actuators configured to effectuate movement of the surface. Thus, if an
actuator has failed in a manner such that the components of the actuator are locked
with one another or are otherwise incapable of movement, the failed actuator
effectively prevents movement of the control surface by the other properlyfunctioning
redundant actuators or other actuator control mechanisms.
As a result, a need exists for reliable, accurate and scalable actuators that are
capable of selectively coupling and decoupling components of the actuator in
response to a jam or other failure of the actuator to disengage components of the
actuator to free the actuated component or surface from the failed actuator. In such
situations, a particular need exits for actuators which are capable of selectively fixing
or locking components of the actuator (such as rotationally or angularly,
longitudinally or axially, or both rotationally and longitudinally) when the actuator is
properly functioning, and also reliably responsive to a failure of the actuator (e.g., a
jam in the actuator) to disengage components of the actuator with respect to one
another (such as rotationally, longitudinally, or both rotationally and longitudinally)
and, thereby, free the actuated component or surface (i.e., the load recipient).
SUMMARY
In accordance with one aspect of the present disclosure, an actuator decoupler
for selectively coupling and decoupling a driven part with a driving part of an
actuation system is disclosed. In some such embodiments, the actuator decoupler
includes a sleeve member, a housing member, at least one coupling pin, at least one
preloaded energy mechanism, and at least one engageable locking member.
In some such embodiments, the sleeve member defies a longitudinal axis and
includes a first portion configured to couple to the driven part, and a second portion
configured to couple to the driving part to receive at least one of a torque about the
longitudinal axis and a force along the longitudinal axis. In some such embodiments,
the housing member is rotationally and longitudinally fixed to the sleeve member.
[007] In some such embodiments, the at least one coupling pin is selectively
engaged with the second portion of the sleeve member and the driven part when the
driven part is coupled to the sleeve member such that the sleeve member and the
driven part are at least one of rotationally and longitudinally fixed to one another by
the at least one coupling pin. In some such embodiments, the at least one preloaded
energy mechanism is coupled to the housing member and the at least one coupling
pin.
In some such embodiments, the at least one engageable locking member is
movably coupled to the at least one preloaded energy mechanism. In some such
embodiments, the at least one engageable locking member is configured to selectively
retain preloaded energy of the at least one preloaded energy mechanism and maintain
the engagement of the at least one coupling pin with the sleeve member and the
driven part in a locking position. In some such embodiments, in an unlocking
position the at least one engageable locking member is configured to selectively
release the preloaded energy of the at least one preloaded energy mechanism to
disengage the at least one coupling pin from at least the' driven part such that the
driven part is free to translate at least one of rotationally and longitudinally with
respect to the sleeve member and the driving part.
In some embodiments, the at least one preloaded energy mechanism is a
preloaded resilient member coupled to a cam disc that is rotatably coupled about the
sleeve member. In some such embodiments, the resilient member is a torsion spring,
and wherein the preloaded energy of the torsion spring is a torque applied to the cam
disc that biases the cam disc in a first rotational direction.
In some such embodiments, when each coupling pin is selectively
engaged with the sleeve member and the driven part, each coupling pin is received
with an aperture of the sleeve member and an aperture of the driven part. In some
such embodiments, the cam disc includes two longitudinally spaced cam disc
members. In some such embodiments, the cam disc members include at least one pair
of substantially aligned cam slots corresponding to each coupling pin. In some such
embodiments, each pair of cam slots is movably coupled about a cam pin that is
engaged to a corresponding coupling pin that is positioned between the cam disc
members.
In some such embodiments, each cam slot defines a profile that
extends angularly and laterally about the longitudinal axis such that a first slot portion
of each cam slot is laterally proximate the longitudinal axis and a second slot portion
angularly spaced from the first portion and laterally distal the longitudinal axis. In
some such embodiments, each cam pin is positioned within the first slot portion of a
corresponding pair of cam slots when the at least one engageable locking member
retains the preloaded torque of the torsion spring and maintains the engagement of the
at least one coupling pin with the sleeve member and the driven part. In some such
embodiments, each cam pin is positioned within the second slot portion of a
corresponding pair of cam slots when the preloaded torque of the torsion spring is
released to disengage the at least one coupling pin from at least the driven part.
In some such embodiments, each cam slot is configured such that when
the at least one engageable locking member releases the preload torque of the torsion
spring the cam disc rotates in the first direction and each cam pin is translated from
the first slot portion to the second slot portion in a corresponding pair of cam slots.
In some such embodiments, the lateral distance between the first slot portion and the
second slot portion of each cam slot is greater than the lateral distance of each pin in
the aperture of the driven part when each cam pin is selectively engaged with the
driven part. In some such embodiments, each cam slot is configured such that the
first slot portion extends for predetermined degree of angulation about the
longitudinal axis, and wherein the lateral location of the first slot portion of the each
cam slot is constant. In some embodiments, the at least one engageable locking
member is configured to interact with a secondary actuator that is responsive to a jam
in the actuation system. In some such embodiments, the at least one engageable
locking member includes a first arm configured to selectively engage the cam disc in
a locking position to selectively rotationally fix the cam disc to selectively retain the
preloaded torque of the torsion spring and to maintain the engagement of the at least
one coupling pin with the sleeve member and the driven part.
In some such embodiments, the at least one engageable locking
member includes second and third longitudinally spaced arms configured to receive a
portion of the secondary actuator therebetween, and translation of the portion of the
secondary actuator in a first longitudinal direction results in the portion interacting
with the second arm and thereby repositioning the at least one engageable locking
member from the locking position to the unlocking position to selectively disengage
the first arm from the cam disc to release the preloaded torque of the torsion spring to
disengage the at least one coupling pin from at least the driven.
In some such embodiments, when the portion of the secondary actuator
is positioned between the second and third arms of the at least one engageable locking
member and the at least one engageable locking member is in the locking position, the
third arm is positioned on an opposing longitudinal side of the portion of the
secondary actuator as compared to the second arm to prevent the at least one
engageable locking member from repositioning from the locking position to the
unlocking position without translation of the at least one engageable locking member.
In some embodiments, the at least one preloaded energy mechanism
includes at least one preloaded cantilever member extending from the housing
member and defining a free end. In some such embodiments, the at least one
coupling pin is provided on a portion of the at least one cantilever member adjacent
the free end, and the at least one cantilever member is deformed to preload the at least
one cantilever member and position the at least one coupling pin within an aperture of
the second portion of the sleeve member and an aperture of the driven part when each
coupling pin is selectively engaged with the sleeve member and the driven part.
In some embodiments, the second portion of the sleeve member is
configured to couple to the driving part to receive at least a torque from the driving
part, and thereby rotate about the longitudinal axis. In some such embodiments, the
sleeve member and the driven part are at least rotationally fixed to one another by the
at least one coupling pin when the driven part is coupled to the sleeve member. In
some such embodiments, the driven part is free to translate at least rotationally with
respect to the sleeve member and the driving part when the at least one coupling pin is
disengaged from the driven part of the sleeve member. In some such embodiments,
the sleeve member and the driven part are also longitudinally fixed to one another by
the at least one coupling pin when the driven part is coupled to the sleeve member. In
some such embodiments, the driven part is also free to translate longitudinally with
respect to the sleeve member and the driving part when the at least one coupling pin is
disengaged from the driven part of the sleeve member.
In some embodiments, the second portion of the sleeve member is
configured to couple to the driving part to receive at least a force along the
longitudinal axis from the driving part, and thereby translate along the longitudinal
axis. In some such embodiments, the sleeve member and the driven part are at least
longitudinally fixed to one another by the at least one coupling pin when the driven
part is coupled to the sleeve member. In some such embodiments, the driven part is
free to translate at least longitudinally with respect to the sleeve member and the
driving part when the at least one coupling pin is disengaged from the driven part of
the sleeve member.
In accordance with another aspect of the present disclosure, an actuator
decoupler for selectively coupling and decoupling a driven part including an aperture
with a driving part of an actuation system such that when selectively coupled the
driven part is at least rotationally fixed to the driving part and when selectively
decoupled the driven part is at least one of rotationally and longitudinally free to with
respect to the driving part is disclosed. In some such embodiments, the actuator
decoupler includes a sleeve member, a cam disc, at least one coupling pin, a housing
member, and no more than one energy mechanism.
In some such embodiments, the sleeve member defines a longitudinal
axis and an aperture, and is configured to receive at least a torque via the driving part
and, upon receipt thereof, to rotate about the longitudinal axis. In some such
embodiments, the cam disc is rotationally coupled about the sleeve member and
includes two longitudinally spaced cam members. In some such embodiments, the
cam members including at least one pair of substantially aligned cam slots defining a
cam profile.
In some such embodiments, the at least one coupling pin is carried
within the aperture of the sleeve member, and a pair of cam slots of the cam disc and
positioned at least partially between the cam members of the cam disc. In some such
embodiments, the housing member is rotationally and longitudinally fixed to the
sleeve member and includes at least one movable locking member for selectively
rotationally locking the cam disc to the housing member and, thereby, the sleeve
member.
In some such embodiments, no more than one energy mechanism is
coupled to the housing member and the cam disc. In some such embodiments, the
energy mechanism is configured to deform and thereby produce a preload torque to
the cam disc in a first direction upon rotation of the cam disc about the sleeve member
in a second direction that substantially opposes the first direction.
In some such embodiments, the cam profile is configured such that at a
second angular position of the cam disc each cam slot, and thereby each coupling pin
carried therein, is spaced laterally further from the longitudinal axis as compared to a
first angular position. In some such embodiments, when the aperture of the sleeve
member is aligned with the aperture of the driven part, the cam disc can be rotated
about the sleeve member in the second direction to the first angular position and
selectively locked thereat by the locking mechanism to preload the torsion spring and
bias the cam disc in the first direction, and to position each coupling pin at least
partially within the aperture of the driven part to selectively couple the driven part
with the driving part via the decoupler. In some such embodiments, the locking
member is configured to be translatable by a secondary actuator to disengage from the
cam disc and release the preload torque of the energy mechanism to thereby rotate the
cam disc in the first direction to the second angular position to laterally translate each
coupling pin away from the longitudinal axis such that each coupling pin is removed
from the aperture of the driven part to selectively decouple the driven part with the
driving part via the actuator decoupler.
In some such embodiments, the at least one coupling pin includes at
least one cam pin member, and the at least one cam pin member is carried within a
pair of cam slots. In some other such embodiments, the cam members include an
even number of pairs of substantially aligned cam slots symmetrically disposed about
the longitudinal axis. In some such embodiments, a coupling pin is carried within
each pair of cam slots and the aperture of the sleeve member, and the housing member
includes at least two locking members symmetrically disposed about the longitudinal
axis.In some embodiments, the cam disc includes slots about the periphery of at least
one cam member, and the at least one locking member includes a first arm including a
protrusion configured to engage a slot of the cam disc. In some such embodiments,
the at least one locking member further includes second and third arms longitudinally
spaced from one another and configured to receive a secondary actuator therebetween.
In some embodiments, when the driving part and the driven part are
selectively decoupled, the driven part is at least rotationally and longitudinally free to
translate with respect to the driving part.
In accordance with another aspect of the present disclosure, an actuator
decoupler for selectively coupling to an actuation system such that at least a first
component of the actuation system is at least rotationally fixed to the actuator
decoupler when the actuation system is functioning properly, and for selectively
decoupling from at least the first component when a jam occurs in the actuation
system such that the first component is capable of rotationally and longitudinally
translating with respect to the actuator decoupler is disclosed. In some such
embodiments, the actuator decoupler includes a sleeve member, at least one coupling
pin, a biasing member, and a locking member.
In some such embodiments, the sleeve member is configured to engage
the first component of the actuation system such that at least one aperture of the
sleeve member is aligned with at least one aperture of the first component. In some
such embodiments, the at least one coupling pin is configured to translate into, and
out of, engagement within the at least one aperture of the sleeve member and the at
least one aperture of the first component when the first component is engaged with the
sleeve member to selectively couple the actuator decoupler to the first component to
at least rotationally fix at least the first component of the actuation system to the
actuator decoupler.
In some such embodiments, the biasing member is configured to bias
the at least one coupling pin out of engagement within the at least one aperture of the
first component when the actuator decoupler is selectively coupled to the actuation
system. In some such embodiments, the locking member is configured to selectively
prevent the biasing member from translating the at least one coupling pin out of
engagement within the at least one aperture af the first component when the actuator
decoupler is coupled to the actuation system and the actuation system is properly
functioning, and selectively allow the biasing member to translate the at least one
coupling pin out of engagement within the at least one aperture of the first component
when the actuator decoupler is coupled to the actuation system and a jam occurs in the
actuation system to decouple the first component from the actuator decoupler such
that at least the first component is capable of rotationally and longitudinally
translating with respect to the actuator decoupler.
In some such embodiments, the locking member is configured to be
responsive to longitudinal movement of a secondary actuator to translate between a
first orientation in which the locking member prevents the biasing member from
translating the at least one coupling pin and a second orientation in which the biasing
member biases the at least one coupling pin and, in response thereto, translates the at
least one coupling pin, and wherein the locking member is configured such that
translation of the locking member between the first orientation and the second
orientation is prevented in any manner other than longitudinal translation of the
secondary actuator.
Other objects, aspects and advantages of the actuator decoupler and
coupling and decoupling methods of the present invention, andlor of the currently
preferred embodiments thereof, will become more readily apparent in view of the
following detailed description of the currently preferred embodiments and the
accompanying drawings.
BRIEF DESCRIPTION OF THE FIGURES
FIG. 1 is a front side elevational perspective view of a first exemplary
embodiment of an actuator decoupler;
FIG. 2 is a top view of the actuator decoupler implant of FIG. 1;
FIG. 3 is a front side view of the actuator decoupler of FIG. 1;
FIG. 4 is a front side elevational perspective view of an exemplary
sleeve member of the actuator decoupler of FIG. 1 ;
FIG. 5 is a front side cross-sectional view of an exemplary sleeve
member of the actuator decoupler of FIG. 1 taken along a plane defined by the
longitudinal and lateral axes of the sleeve member;
FIG. 6 is a front side cross-sectional view of an exemplary sleeve
member of the actuator decoupler of FIG. 1 engaged with an exemplary driving part
and an exemplary driven part taken along a plane defined the longitudinal and lateral
axes of the sleeve member and the driven part;
FIG. 7 is a partial front side cross-sectional view of the exemplary
sleeve member of the actuator decoupler of FIG. 1 selectively fixed with an
exemplary driven part by exemplary coupling pins taken along a plane defined by the
longitudinal and lateral axes of the sleeve member and the driven part;
FIG. 8 is a partial front side cross-sectional view of an exemplary
sleeve member of the actuator decoupler of FIG. 1 selectively decoupled with an
exemplary driven part by exemplary coupling pins taken along a plane defined by the
longitudinal and lateral axes of the sleeve member and an exemplary driven part;
FIG. 9 is a front side elevational perspective view of an exemplary
sleeve member, an exemplary housing member and an exemplary energy mechanism
of the actuator decoupler of FIG. 1;
FIG. 10 is a partial rear side elevational perspective view of an
exemplary sleeve member, an exemplary housing member and an exemplary energy
mechanism of the actuator decoupler of FIG. 1 ;
FIG. 11 is a front side elevational perspective view of an exemplary
sleeve member, an exemplary housing member, an exemplary energy mechanism and
an exemplary cam disc of the actuator decoupler of FIG. 1 ;
FIG. 12 is a front side view of an exemplary sleeve member, an
exemplary housing member, an exemplary energy mechanism and an exemplary cam
disc of the actuator decoupler of FIG. 1 ;
FIG. 13 is a front side cross-sectional view of an exemplary sleeve
member, an exemplary housing member, an exemplary energy mechanism and an
exemplary cam disc of the actuator decoupler of FIG. 1 taken along a plane defined
by the longitudinal and lateral axes of the sleeve member and a driven part;
FIG. 14 is a partial front side elevational perspective view of an
exemplary housing member and an exemplary cam disc of the actuator decoupler of
FIG. 1 in the selectively locked state;
FIG. 15 is a partial front side cross-sectional view of an exemplary
housing member and an exemplary cam disc of the actuator decoupler of FIG. 1 in the
selectively locked state and interacting with an exemplary secondary actuator;
FIG. 16 is a partial front side elevational perspective view of an
exemplary housing member and an exemplary cam disc of the actuator decoupler of
FIG. 1 in the selectively unlocked state;
FIG. 17 is a front side elevational perspective view of an exemplary
housing member, an exemplary cam disc and an exemplary coupling pins of the
actuator decoupler of FIG. 1 ;
FIG. 18 is a front side elevational perspective view of the actuator
decoupler of FIG. 1 ;
FIG. 19 is an illustration of exemplary cam slots of an exemplary cam
disc and an exemplary cam disc cover of the actuator decoupler of FIG. 1;
FIG. 20 is an illustration of alternative cam slot embodiments;
FIG. 21 is a partial front side cross-sectional view of the exemplary
actuator decoupler of FIG. 1 selectively coupled to an exemplary driven part and
interacting with an exemplary secondary actuator taken along a plane defined by the
longitudinal and lateral axes of an exemplary sleeve member and an exemplary driven
part;
FIG. 22 is a front side cross-sectional view of the exemplary actuator
decoupler of FIG. 1 selectively decoupled from an exemplary driven part taken along
a plane defined by the longitudinal and lateral axes of an exemplary sleeve member
and the driven part; and
FIG. 23 is a partial front side cross-sectional view of a second
exemplary embodiment of an actuator decoupler of the present disclosure coupled to
an exemplary driving part and selectively coupled to an exemplary driven part.
DETAILED DESCRIPTION
In FIGS. 1-3, an actuator decoupler embodying a first embodiment is
indicated generally by the reference numeral 10. As shown in FIGS. 1-3, the
exemplary actuator decoupler 10 includes an exemplary sleeve member 12, an
exemplary housing member 14, an exemplary cam disc 16, an exemplary cam disc
cover 18 and exemplary coupling pins 20. The exemplary actuator decoupler 10 is
configured to selectively couple, at least in part, a power source (not shown) and a
load recipient (not shown), as explained further below. In this way, in a coupled state
the actuator decoupler 10 acts to engage a driving part 30A (i.e., the power source and
associated components) with a driven part 30B (see FIGS. 6 and 22) such that they are
at least one of rotationally or angularly and longitudinally or axially fixed with respect
to one another, and in an uncoupled state the actuator decoupler 10 acts to decouple
the driven part 30B from the driving part 30A such that the driven part 30B is free to
translate at least both rotationally and longitudinally wiih respect to the driving part
30A and the actuator decoupler 10. In some embodiments, the actuator decoupler 10
is configured such that in an uncoupled state the driven part 30B is free to translate at
least one of rotationally (i.e., angularly) and longitudinally (i.e., axially) with respect
to the driving part 30A and the actuator decoupler 10. Thereby, the actuator
decoupler 10 can be responsive to a jam in an actuation system in which it is installed
to decouple the driven part 30B of the system (and thereby the load recipient) from
the actuator decoupler 10 and the driving part 30A to thereby allow the load recipient
to properly function, at least in part, in spite of a jam or other malhnction, as
explained fbrther below.
The exemplary actuator decoupler 10 utilizes in part the sleeve
member 12 to selectively couple the driving mechanism (driving part 30A) and the
exemplary actuator decoupler 10 itself to the driven part 30B, and therefore to the
load recipient. The configuration of the sleeve member 12 may thereby depend upon
the configuration of a particular driving part or mechanism 30A, a particular load
application, and a particular driven part 30B and load recipient. For example, the
driving part or mechanism 30A, which provides and applies the energy or force that is
applied to the actuator decoupler 10, the driven part 30B and, ultimately, the load
recipient in the coupled state, may be any drive mechanism known in the art. For
example, the actuator decoupler 10 may be used with one or motor or other electric
system, hydraulic system, mechanical system, human powered system and
combinations thereof as the power source. The driving part or mechanism 30A may
also include components that manipulate the output force of the power source. For
example, the drive mechanism may include components that alter the magnitude of
the output force (e.g., gearing), the direction or type of the output force (e.g.,
rotational to linear), the timing of the output force (e.g., a switch or clutch), and the
like. The driving part 30A may also likely include a mechanism to transfer the output
force to the sleeve member 12. For example, the driving part 30A may include one or
more gear, belt, pulley, chain or the like to apply the output force of the driving part
30A to the sleeve member 12. As a result, a drive portion or portions 22 of the sleeve
member 12 may be configured in any known manner to couple the sleeve member 12
to a driving part or mechanism 30A such that the output force of the driving part or
mechanism 30A is transferred, at least partially, to the sleeve member 12. Such a
configuration may be achieved through conventional methods commonly and
commercially used in the art and may be determined on a routine basis.
As stated above, the directions or type of the output force of the
driving part 30A, and thereby applied to the sleeve 12, may vary. As such, the
actuator decoupler 10 may be configured to be used in differing types of actuation
systems. For example, the actuator decoupler 10 may be used in a liner actuation
system in which linear forces are applied to the sleeve 12 by the driving part 30A
along the longitudinal axis X-X to "push" and "pull" the sleeve 12 substantially
linearly. These longitudinal or axial forces, and resulting motions, may ultimately act
to apply longitudinal or axial forces via the actuator decoupler 10 to move a force
recipient. Similarly, the actuator decoupler 10 may be used in a rotational actuation
system in which torques are applied to the sleeve 12 about the longitudinal axis X-X
to rotate the sleeve 12 in clockwise and/or counterclockwise directions. These
rotational or angular forces, and resulting motions, may ultimately act to apply
rotational or angular forces (i.e., torque) via the actuator decoupler 10 to move a force
recipient. As yet another example, the actuator decoupler 10 may be used in actuation
systems in which a combination of forces are applied and/or result from actuation.
For example, a rotational force (i.e., torque) may be applied to sleeve 12, and such
rotation may result in longitudinal forces ultimately acting on the load recipient (and
the actuator decoupler 10 via reaction), such as with a power screw. As another
example, at least one of rotational forces (i.e., torques) and longitudinal forces may be
applied to sleeve 12, and such forces (and resulting movement) may result in at least
one of rotational and longitudinal forces ultimately acting on the load recipient (and
the actuator decoupler 10 via reaction). Still hrther, other forces besides rotational
and longitudinal forces may be applied to the actuator decoupler by the driving part
and/or to the load recipient (and the driven portion or portions 26 of the sleeve 12).
Therefore, the driven 22 and driving 26 portions of the sleeve 12 of the actuator
decoupler 10 may be configured to receive and transmit any of such forces.
As best shown in FIGS. 4-6, the illustrated exemplary sleeve member
12 of the actuator decoupler 10 defines an elongate cylindrical-like shape defining a
longitudinal axis X-X. The exemplary sleeve member 12 is configured to rotate about
the longitudinal axis X-X, and is therefore formed substantially symmetrically about
the longitudinal axis X-X to reduce wobble, vibration or the like during rotation. As a
result, the drive portion 22 of the sleeve member 12 is configured to receive a moment
or torque about the longitudinal axis X-X such that it rotates thereabout. The drive
portion 22 of the sleeve member 12 includes a first detent or flat 24 formed into the
outer surface. The first detent or flat 24 can be used to rotationally fix a gear, pulley,
sleeve member or other rotational mechanism to the drive portion 22. For example,
the first detent or flat 24 may be used in conjunction with a set screw or key and
keyway with a gear, pulley, sleeve member or other rotational mechanism that is
rotated, either directly or indirectly, from the power source. In such a configuration,
the set screw or key and keyway, the rotational mechanism, and the power source may
be considered the driving part or mechanism 30A. In this manner, a torque can be
applied to the sleeve member 12 via the first portion 22 by the driving part 30A to
rotate the sleeve member 12 about the longitudinal axis X-X. The sleeve member 12
may be supported such that the drive portion 22 remains engaged with the drive
mechanism during such rotation, such as being restricted from movement in
longitudinal or axial and lateral or radial directions. Further, the sleeve member 12
may be supported in such a manner that allows or aids in such rotational movement,
such as being supported by bearings about the periphery of the sleeve member 12.
However, as explained above, the drive portion 22 of the sleeve member 12 may be
alternatively configured depending upon the particular actuation system in which the
actuator decoupler 10 is installed, and such configuration may be determined on a
routine basis in the art. For example, rather than, or in addition to, a torque and
resulting rotational movement, the sleeve member 12 may be subjected to longitudinal
force by the driving part 30A that results in longitudinal movement of the sleeve
member 12. Thus, in such a configuration, the drive portion 22 of the sleeve member
12 may be configured to receive such longitudinal force and allow for resulting
longitudinal movement.
As the configuration of the driving portion or portions 22 of the sleeve
member 12 may depend upon, or at least be related to, the particular driving part or
mechanism 30A (or vice versa) as described above, the configuration of the driven
portion or portions 26 of the sleeve member 12 may depend upon, or at least be
related to, the particular driven part or mechanism 30B (or vice versa) of the actuator
system in which the actuator decoupler 10 is installed. For example, the driven part
30B may be a mechanism that transfers the force of the sleeve member 12 to the load
recipient. For example, the driven part 30B may include one or more shaft, linkage,
gear, belt, pulley, chain or any other known mechanism or configuration to receive the
output force of the sleeve member 12 (via the driving part 30A) and apply it, at least
partially, to the load recipient. As a result, the drive portion or portions 22 of the
sleeve member 12 may be configured in any known manner to couple the sleeve
member 12 to the driven part or mechanism 30B such that the output force of the
sleeve member 12 (via the driving part 30A) is transferred, at least partially, to the
driven part or mechanism 30B and, ultimately, to the load recipient. Such
configuration may be achieved through conventional methods commonly and
commercially used in the art and may be determined on a routine basis.
As the illustrated exemplary sleeve member 12 is configured to receive
a moment or torque via the driving portion 22 such that it rotates about the
longitudinal axis X-X, the driven portion or portions 26 islare configured to transfer
such a torque to the driven part or mechanism 30B, as shown in FIGS. 4-6. The
exemplary driven portion 26 of the sleeve member 12 includes an interior aperture 28
extending longitudinally from an end of the sleeve member 12 about the longitudinal
axis X-X such that the axis of the aperture 28 is aligned with the longitudinal axis XX
of the sleeve member 12. The longitudinally extending aperture 28 of the driven
portion 26 of the sleeve member 12 defines substantially smooth walls and a circular
profile to accept a similarly shaped driven part 30B therein, as shown in FIG. 6. As
the sleeve member 12 is configured to receive and translate a torque or moment (via
rotation of the sleeve member 12) to the driven part 30B, the longitudinally extending
aperture 28 is configured with respect to the to the driven part 30B (or vice versa)
such that the driven part 30B can be received and supported within the longitudinally
extending aperture 28 and a longitudinal axis Xl-XI of the driven part 30B is aligned
with the longitudinal axis X-X of the sleeve member 12. In the illustrated
embodiment, the longitudinally extending aperture 28 and the driven part 30B are also
configured with respect to one another such that the driven part 30B is able to
relatively freely rotate about, and translate along, the longitudinal axes X-X, XI-X1
of the longitudinally extending aperture 28 and the driven part 30B when in an
uncoupled state with the actuator decoupler 10, as shown in FIG. 6. As such, the
relative diameter, longitudinal length, surface finish and other pertinent characteristics
of the longitudinally extending aperture 28 of the driven portion 26 and the driven
part 30B are dependent upon, or at least related to, each other such that rotation and
longitudinal translation between the two components is achieved in the uncoupled
state of the actuator decoupler 10. Such configurations are known in the art and may
be achieved through conventional methods commonly and commercially used in the
art and may be determined on a routine basis.
The driven portion 26 of the sleeve member 12 may also be configured
to allow the sleeve member 12 to be selectively coupled to the driven part 30B. In the
illustrated embodiment, as shown in FIGS. 4-7, the driven portion 26 may include at
least one laterally or radially extending aperture 32 that extends entirely through the
thickness of the portion of the sleeve member 12 about the longitudinally extending
aperture 28. As best shown in FIGS. 4 and 5, the exemplary at least one aperture 32
of the illustrated sleeve member 12 extends entirely through the sleeve member 12
and thereby provides two opening s fiom the exterior of the sleeve member 12 to the
interior of the longitudinally extending aperture 28. The at least one aperture 32 of
the driven portion 26 of the sleeve member 12 is preferably configured to mate with at
least one corresponding laterally or radially extending aperture 34 of the driven part
30B when the driven part is received with the longitudinally extending aperture 28.
As such, the configuration, such as the position, orientation, size, shape and quantity,
of the at least one aperture 32 of the driven portion 26 of the sleeve member 12 is
dependent upon, or at least related to, the corresponding characteristics of the at least
one aperture 34 of the driven part 30B (or vice versa).
In the illustrated embodiment, as best shown in FIGS. 6 and 7, the at
least one laterally extending aperture 32 of the driven portion 26 of the sleeve member
12 extends through the entire thickness of the sleeve member 12 (i.e., the at least one
laterally extending aperture 32 intersects the longitudinal axis X-X of the sleeve
member 12). Similarly, in the illustrated embodiment the at least one laterally or
radially extending aperture 34 of the driven part 30B extends through the entire
thickness of the driven part 30B (i.e., the at least one laterally extending aperture 34
intersects the longitudinal axis XI-X1 of the driven part 30B). Further, as shown in
FIGS. 5- 7, the at least one aperture 32 of the driven portion 26 and the at least one
aperture 34 of the driven part 30B are circular, linear (constant diameter) and define
respective axes Y-Y, Yl-Y1 that extend substantially perpendicular to the
longitudinal axis X-X of the sleeve member 12 and the longitudinal axis XI-X1 of the
driven part 30B, respectively. It is noted however, that the particular shape,
orientation, position, quantity and the like of the at least one aperture 32 of the driven
portion 26 and the at least one aperture 34 of the driven part 30B may vary and be of
any configuration that allows the sleeve member 12 and the driven part 30B to be at
least rotationally and longitudinally coupled to one another by at least one coupling
pin 20 positioned within the apertures 32,34, as shown in FIG. 7.
As illustrated in FIG. 7, the driven portion 26 of the sleeve member 12
may include a single laterally or radially extending aperture 32 that passes through the
sleeve member 12, the longitudinal axis X-X and the longitudinally extending
aperture 28 such that two opposing openings are formed in the outer surface of the
driven portion 26 of the sleeve member 12. Similarly, the poition of the driven part
configured to be positioned within the longitudinally extending aperture 28 of the
sleeve member 12 may include a single laterally extending aperture 34 that passes
through the driven part 30B and the longitudinal axis X1-XI such that two opposing
openings are formed in the outer surface of the driven portion 26. In such a
configuration, as shown in FIG. 7 the axes Y-Y, Y 1-Y 1 of the apertures 32,34 can be
aligned and a coupling pin 20 can be inserted into the each opening and ultimately,
into engagement with the aperture 32 of the driven portion 26 of the sleeve member
12 and the aperture 34 of the driven part 30B. Thereby, each coupling pin 20
selectively rotationally and longitudinally locks the sleeve member 12 and the dnven
part 30B to each other (discounting any negligible rotational or longitudinal
movement allowed by tolerances between each coupling pin 20 and the apertures 32,
34 of the driven portion 26 of the sleeve member 12 and the driven part 30B).
Further, as discussed above, the interaction between the interior surface of the sleeve
member 12 that forms the longitudinally extending aperture 28 and the outer surface
of the portion of the driven part 30B that is positioned within the longitudinally
extending aperture 28 laterally locks the sleeve member 12 and the driven part 30B to
one another such that alignment of the longitudinal axes X-X, XI-X1 is maintained.
As such, in the illustrated configuration or state of the sleeve member 12, driven part
30B and pins 20 shown in FIG. 7, the sleeve member 12 is selectively coupled to the
driven part 30B.
In the illustrated exemplary embodiment, each coupling pin 20 is sized,
shaped oriented and otherwise configured to substantially correspond to
characteristics of the apertures 32, 34 of the sleeve member 12 and driven part 30B
(or vice versa) such that each pin defines a laterally or radially extending axis Y2-Y2.
As such, the axis Y2-Y2 of each coupling pin 20 is aligned with the laterally
extending axes Y-Y, Y I-Y 1 of the apertures 32, 34 of the sleeve member 12 and the
driven part 30B, respectively, at least in the coupled state (see FIG. 7).
In some alternative embodiments (not shown), the actuator decoupler
10 is configured to transmit only one of rotational and longitudinal forces to the
driven part 30B. Alternatively, in some embodiments, such as in the illustrated
embodiment, the actuator decoupler 10 is configured to be capable of transmitting
both rotational and longitudinal forces to the driven part 30B as the actuator decoupler
10 is both rotational and longitudinal fixed or locked to the driven part 30B in the
coupled state (FIG. 7). In use, even if the actuator decoupler 10 is configured to
transmit both rotationally and longitudinally forces (andlor any other forces) to the
driven part 30B, the actuation system in which the actuator decoupler 10 is installed
may only transmit one such force to the driven part 30B. In such embodiments,
however, the actuation system may alter the direction of the transmitted force, and
thereby exert a reaction force that is of different directions or type, such as when the
driving part 30A applies a torque to the sleeve 12 and the sleeve 12 and the at least
one coupling pin 20 receive a longitudinal reaction force from the driven part 30B
when the driven part 30B is a component of, or coupled to, a power screw (i.e.,
reactionary longitudinal and rotational forces verse transmitted rotational forces).In
contrast to the selectively coupled or locked state or configuration of the illustrated
sleeve member 12 and driven part 30B shown in FIG. 7, FIG. 8 illustrates a
selectively decoupled or unlocked state or configuration of the actuator decoupler 10.
As shown in FIG. 8, each coupling pin 20 may be laterally translated such that the
each coupling pin 20 is drawn out of engagement with the aperture 34 of the driven
part 30B. In such a configuration, the driven part 30B is free to translate both
rotationally about, and longitudinally along, the longitudinal axis XI-XI. In
alternative embodiments (not shown), the driven part 30B may be free to translate
only rotationally, only longitudinally, or in a combination of rotational, longitudinal
and other directions.
As explained above, in the uncoupled state of the exemplary illustrated
actuator decoupler 10, as shown in FIG. 8, the driven part 30B is supported by the
longitudinally extending aperture 28 of the sleeve member 12 and is free to rotate
about the longitudinal axis XI-XI. Further, as illustrated in FIGS. 6-8 the
longitudinally extending aperture 28 of the sleeve member 12, the pin aperture 32 of
the sleeve member 12, and the pin aperture of the driven part 30B may be configured
such that in an uncoupled state the driven part 30B is capable of translating
longitudinally in either longitudinal direction along the longitudinal axis XI-X1. As
indicated in FIG 8., the pin apertures 32, 34 of the driven portion 26 of the sleeve
member 12 and the driven part 30B may be positioned such that when the driven part
30B is positioned within the longitudinally extending aperture 28 of the sleeve
member 12 such that the axes Y-Y, Yl-Yl are aligned, a spacing or gap of a
predetermined longitudinal length L1 is provided between the ends of the driven part
30B and the longitudinally extending aperture 28. The predetermined length Ll of
the spacing between the ends of the driven part 30B and longitudinally extending
aperture 28 of the sleeve member 12 will depend upon the particular application (i.e.,
will depend upon how much longitudinal translation is required based on the
particular actuation system in which the actuator decoupler is installed). In such an
arrangement, when the actuator decoupler 10 translates or drives each pin 20 from the
coupled state with the driven part 30B (FIG. 7) to the uncoupled state (FIG. 8), the
driven part 30B (or the sleeve member 12) can translate a distance L1 in a direction
such that the driven part 30B is positioned deeper within the longitudinally extending
aperture 28 of the driven portion 26 of the sleeve member 12. The arrangement of the
components thereby prevents the driven part 30B from "bottoming out" in the
longitudinally extending aperture 28 during longitudinal translation. Further, due to
the overall length of the internal longitudinally extending aperture 28 of the sleeve
member 12, the driven part 30B can translate to a position where the driven part 30B
is more shallow while remaining in the longitudinally extending aperture 28 and,
therefore, supported thereby. Stated differently, the sleeve member 12 and the driven
part 30B can be configured such that a predetermined degree of longitudinal
translation of the driven part 30B (or the sleeve member 12) is provided, within the
longitudinally extending aperture 28 for example, when the actuator decoupler 10
decouples the driven part 30B from the sleeve member 12 (and thus the driving part
30A). However, in alternative embodiments (not shown), the actuator decoupler 10
may be configured to not allow longitudinal movement in the uncoupled state.
As also shown in FIG. 8, in a decoupled state each coupling pin 20
may be withdrawn from the driven part 30B and the longitudinally extending aperture
28 of the sleeve member 12, but a portion thereof may remain in the thickness of the
sleeve member 12. The complete removal of each coupling pin 20 from the
longitudinally extending aperture 28 may be advantageous as the driven part 30B can
freely rotationally and longitudinally translate within the longitudinally extending
aperture 28 without interacting with each coupling pin 20. As such, each coupling
pin 20 and the driven part 30B are prevented from scratching, deforming, rubbing or
otherwise damaging each other, and each coupling pin 20 is prevented from catching
or otherwise interacting with the aperture 34 of the driven part 30B and, thereby,
inhibiting movement of the driven part 30B in any manner. Further, by remaining
within the aperture 32 of the sleeve member 12, each coupling pin 20 can be easily
inserted, or reinserted, into the coupling pin aperture 34 of the driven part 30B when
the aperture 34 is aligned with each coupling pin 20 and the aperture 32 of the sleeve
member 12 to couple the sleeve member 12 (and therefore the actuator decoupler 10)
and the driven part 30B. Stated differently, to move from an uncoupled state to a
coupled state, each coupling pin 20 of the actuator decoupler 10 need only to be
aligned with the pin aperture 34 of the driven part 30B and then translated into
engagement therein (i.e., each coupling pin 20 does not need to be aligned with the
aperture 32 of the sleeve member 12).
The thickness of the sleeve member 12 extending between the surface
of the longitudinally extending aperture 28 and the outer surface of the portion 38 of
the driven portion 26 of the sleeve member 12 about the laterally or radially extending
coupling pin aperture 32 may depend upon the load requirements of the particular
application of the actuator system in which the actuator decoupler 10 is installed. For
example, in order to drive or translate the driven part 30B (and ultimately the load
recipient), a load must be transferred from the sleeve member 12 (via the driving part
30A) to the driven part 30B. Similarly, in some applications, the load recipient may
apply a relatively large load to the driven part 30B, and thereby to the sleeve member
12. In the illustrated embodiment, these forces are translated from the sleeve member
12 to the driven part 30B, or vice versa, through the interaction of each coupling pin
20 and the interior surfaces of the lateral aperture 32 of the sleeve member 12. As
such, the relative dimensions of the sleeve member 12 (as well as the driven part 30B)
and each coupling pin 20, including the thickness of the interior surfaces of the lateral
aperture 32 and the number of coupling pins 20, may depend, at least in part, upon the
load characteristics of the particular actuation system in which the actuator decoupler
10 is installed. In the illustrated embodiment, as shown in FIGS. 4-8, the thickness of
the driven portion 26 of the sleeve member 12 about the aperture 32 is increased as
compared to adjacent portions of the sleeve member 12 to provide a collar or raised
portion 38 about the aperture 32, and therefore larger interior surface area of the
aperture 32, to interact with each coupling pin 20. Further, two coupling pins 20 are
provided so that the forces or load acting on each coupling pin 20 and each portion of
the sleeve member 12 of the lateral or radial aperture 32 interacting with the coupling
pins 20 formed by the collar 38, is reduced by half as compared to the forces or load
that would be present if one coupling pin 20, instead of two coupling pins 20, was
provided.
To further account for the forces exerted on each coupling pin 20 and
the sleeve member 12, the portion of the sleeve member 12 about the aperture 32 (i.e.,
the collar 38) may be configured such that the outer surface of the sleeve member 12
are flat or "squared-off', as opposed to radiused, as shown best in FIG 4. In such a
configuration, the surface area of the interior surfaces of the lateral or radial coupling
pin aperture 32 of the sleeve member 12 at the exterior of the sleeve member 12 that
engage each coupling pin 20 when each coupling pin 20 is inserted within the lateral
coupling pin aperture 32 in the coupled state or condition of the actuator decoupler 10
is constant about all sides of the pin. Stated differently, because the openings of the
coupling pin aperture 32 are flat and oriented such that a plane defined by the
openings is normal to the lateral or radial axis Y-Y of the aperture 32 (and therefore
the lateral axis Y2-Y2 of each coupling pin 20), the outer edge of the joint between
the outer surfaces of each coupling pin 20 and the interior surfaces of each opening of
the lateral coupling pin aperture 32 extends about the same lateral location of each
coupling pin 20. In comparison to a configuration where the portion of the sleeve
member 12 that forms the openings of the coupling pin aperture 32 is cylindrical, and
therefore defines a radiused or curved shape about the longitudinal axis X-X, the
longitudinal or axial sides of the 32 would extend further from the longitudinal axis
X-X as compared to the lateral or radial sides. As such, each coupling pin 32 and the
lateral coupling pin aperture 32 of the sleeve member 12 would tend to wear nonuniformly
and be more prone to failure (e.g., deformation or breakage of a coupling
pin 20, deformation or breakage of the sleeve member 12 bout the coupling pin
aperture 32 or a scenario such that a coupling pin 20 is "stuck" in engagement with
the coupling pin aperture 32). Further, if each coupling pin 20 is configured such that
the bottom of each coupling pin 20 is planar and oriented normal to the axis Y2-Y2 of
each coupling pin 20, as each coupling pin 20 is removed from the coupling pin
aperture 32 each coupling pin 20 would gradually disengage from the coupling pin
aperture 32, and thereby cause portions of the aperture 32 and pin to experience
greater loads and resulting wear, deformation or otherwise interfere with the removal
of each coupling pin 20. In contrast, in the illustrated configuration, because the
portion 38 of the sleeve member 12 about the coupling pin aperture 32 is planar and
oriented such that a plane defined by the openings is normal to the lateral or radial
axes Y-Y, Y2-Y2 of the lateral pin aperture 32 and each coupling pin 20, and the
bottom surface of each coupling pin 20 is planar and oriented normal to the axis Y2-
Y2 of each coupling pin 20, all surface areas or sides of each coupling pin 20
disengage from the coupling pin aperture 32 at the same time as the coupling pin 20 is
translated out of engagement with the lateral coupling pin aperture 32 coupling pin
20. Further, such a configuration may aid in initially translating each coupling pin 20
into engagement with the lateral coupling pin aperture 32 of the sleeve member 12
through the openings of the lateral coupling pin aperture 32.
The configuration or characteristics of the sleeve member 12, lateral or
radial coupling pin aperture 32 and coupling pins 20 may further depend upon other
variables, such as the material properties of the components, as known in the art. As
such, the configuration or characteristics of the sleeve member 12, lateral coupling pin
aperture 32 and coupling pins 20 may be determined through conventional methods
commonly and commercially used in the art and may be determined on a routine
basis. It is noted, however, that as the number of coupling pins 20 the actuator
decoupler 10 includes decreases, the reliable of the actuator decoupler 10 increases,
but the load applied to each coupling pin 20 and the associated structures of the
actuator decoupler 10 increases, such as the portion 38 of the driven portion 26 of the
sleeve member 12 about each pin aperture 32. As such, in applications which require
a high level of reliability, such as in aviation applications, it is advantageous for the
actuator decoupler 10 to include relatively few coupling pins 20, and such coupling
pins 20 and the associated structures of the actuator decoupler 10 to be configured to
withstand the relatively large forces or loads applied thereto. Further, such an
actuator decoupler 10 must be configured to overcome such large forces or loads to
translate each lateral coupling pin aperture 32 out from the lateral coupling pin
aperture 34 of the driven part 30B to decouple the driven part 30B from the actuator
decoupler 10 and the driving part 30A. To this end, the illustrated actuator decoupler
10 includes two pins 26, the portion of the driven part 26 of the sleeve member 12
about the aperture 32 is enlarged and the actuator decoupler 10 is otherwise
configured to overcome the relatively large forces or loads applied to the coupling
pins 20 to translate each lateral coupling pin 20 out of engagement with the lateral
coupling pin aperture 32 of the driven part 30B, as described Wher below.
In the illustrated embodiment, the actuator decoupler 10 is particularly
well suited for rotation about the longitudinal axis X-X as described above, and
therefore is particularly well suited for use with a power screw. For example, as
shown in FIG. 6 the exterior of the driven part 30B may include external threading for
interaction with internal threading of a complimentary component (or vice versa). As
such, in some embodiments, the driven part 30B may be a first component of a power
screw. In other embodiments, the driven portion 30B may be a first component of an
actuation system that does not include a power screw. In actuation systems including
a power screw and the driven part 30B is a first component of the power screw, the
torque and resulting rotational movement of the driven part 30B applied by each
coupling pin 20 via the sleeve member 12 can be converted into liner force and
movement. As a result, when the actuator decoupler 10 is in the coupled state shown
in FIG. 7 and a torque is applied to the driving portion 22 of the sleeve member 12,
the sleeve member 12 rotates about the longitudinal axis X-X and the interior surfaces
of the lateral coupling pin aperture 32 of the driven portion 26 of the sleeve member
12 proportionally apply the torque to each coupling pin 20. In such a state, each
coupling pin 20 transfers the force (torque) to the interior surfaces of the lateral
coupling pin aperture 34 of driven part 30B to rotate the driven part 30B about the
longitudinal axis Xl-XI. If the driven part 30B is configured as a component of a
power screw, the rotational energy (i.e., torque) of the driven part 30B is transferred
into linear energy and, ultimately, applied to a load recipient. In such an arrangement,
for example, the load recipient may be a flight control surface of an aircraft. As is
known in the art, if the driven part 30B is part of, or at least downstream from, a
power screw or other rotational-to-axial motion or energy converting mechanism,
axial forces acting generally in the direction of the longitudinal axis Xl-X1 will be
applied to the driven part 30B. Further, external forces applied to the load recipient
will result in additional axial forces acting generally in the direction of the
longitudinal axis X1-X1 to the driven part 30B. For example, if the load recipient is a
flight control surface of an aircraft, air pressure acting on the control surface will be
transferred through a rotational-to-axial motion or energy converting mechanism (e.g.,
a power screw) and, ultimately, to the driven part 30B.
In scenarios where the actuator decoupler 10 is coupled to a driven part
30B as part of an actuation system that produces both rotational or angular and
longitudinal or axial forces, as described above for example, the coupling pins 20 will
be subjecting to such forces. Specifically, in such a configuration each coupling pin
20 will be subjected to a shear stress resulting from the forces of the interior surface
of the lateral coupling pin aperture 32 of the sleeve member 12 acting on the outer
surface of each coupling pin 20 due to the torque of the sleeve member 12, and
reaction forces of the interior surface of the pin aperture 34 of the driven part 30B
acting on an opposing outer surface of each coupling pin 20 as compared to the forces
exerted by surfaces of the lateral coupling aperture 32 of the sleeve member 12.
Similarly, each coupling pin 20 will be subjected to a shear stress resulting from the
forces of the interior surface of the lateral coupling pin aperture 34 of the driven part
30B acting on the outer surface of each coupling pin 20 due to linear forces of the
driven part 30B, and reaction forces of the interior surface of the coupling pin
aperture 32 of the sleeve member 12 acting on an opposing outer surface of each
coupling pin 20 as compared to the forces exerted by surfaces of the pin aperture 34
of the driven part 12. As such longitudinal or axial forces act generally along the
longitudinal axes X-X, XI-XI of the sleeve member 12 and the driven part 30B, and
such rotational forces (i.e., torque) about the longitudinal axes X-X, XI-XI, the forces
of the lateral coupling pin aperture 32 of the sleeve member 12 act on adjacent
surfaces of each coupling pin 20, and the forces of the lateral coupling pin aperture 34
of the driven part 30B act on opposing adjacent surfaces of each coupling pin 20. As
a result, a relatively large surface area about the periphery of each coupling pin 20 is
subjected to forces. As is known in the art, such forces acting on the outer surface of
each coupling pin 20 by the sleeve member 12 and driven part 30B increase any
frictional forces between each coupling pin 20 and the sleeve member 12 and the
driven part 30B. To overcome such frictional forces and translate each coupling pin
20 from engagement within the lateral coupling pin aperture 32 of the driven part 30B
(the coupled state or position shown in FIG. 7) to a configuration where each coupling
pin 20 is removed from within the lateral coupling pin aperture 34 of the driven part
30B and the longitudinally extending internal aperture 28 of the sleeve member 12
(the uncoupled state or position shown in FIG. 8), and thereby allow the driven part
30B to translate both rotationally and longitudinally independent of the actuator
decoupler 10 and the driven part 30B, the illustrated exemplary actuator decoupler 10
includes a single (i.e., no more than one) preloaded energy mechanism or resilient
member 40. However, in alternative embodiments (not shown) the actuation
decoupler includes more than one preloaded energy mechanism 40 (or more than one
energy mechanism 40 that can be preloaded).
As shown in FIGS. 1-3, the illustrated exemplary actuator decoupler 10
includes an exemplary housing member 14. The exemplary housing member 14 may
be a component or part of the preloaded energy mechanism 40 which drives each
coupling pin 20 out of engagement with the driven part 30B to decouple the driven
part 30B from the actuator decoupler 10 and the driving part 30A. In reference to
FIGS. 9 and 10, the exemplary housing member 14 may be coupled, connected or
otherwise attached with, or part of, the sleeve member 12 such that it rotates with the
sleeve member 12 about the longitudinal axis X-X in unison with the sleeve member
12 itself. For example, the exemplary housing member 14 (and/or the sleeve member
12) may be configured to engage with the outer surface of the sleeve member 12 such
that the housing member 14 is rotationally or angularly locked with respect to the
sleeve member 12. As such, the housing member 14 andlor sleeve member 12 may
be configured in any known manner such they are either monolithic or coupled,
attached, connected or otherwise rotationally locked with respect to one another. In
the illustrated embodiment, as best shown in FIG. 10, the sleeve member 12 and the
housing member 14 are rotationally locked to one another via a key joint. More
specifically, a collar portion 38 of the sleeve member 12 adjacent the lateral or radial
coupling pin aperture 32 includes a second detent or flat 42 formed into the outer
surface, the housing member 14 includes a keyway 48 in the interior portion of the
housing member 14 adjacent the second detent 42, and a key 44 is positioned within
the second detent 42 and keyway 48. The second detent 42 of the sleeve member 12,
the keyway 48 of the housing member 14 and the key 44 extend generally
longitudinal in the direction of the longitudinal axis X-X, and include substantially
planar surfaces. In the securely fixedly coupled configuration of the sleeve member
12 and housing member 14 shown in FIGS. 10 and 11, the bottom and longitudinal
side surfaces of the key 44 interact with corresponding surfaces of the second detent
42 of the sleeve member 12, and the top and longitudinal side surfaces of key 44
interact with the keyway 48 of the housing member 14. In this manner, a torque can
be applied to the sleeve member 12 via the first portion 22 by the driving part 30A to
rotate the sleeve member 12 and the housing member 14 via the key 44 about the
longitudinal axis X-X.
The actuator decoupler 10 may also be configured such that the
housing member 14 is securely prevented from longitudinal translation along the
sleeve member 12 (e.g., translation along the longitudinal axis X-X). For example,
the sleeve member 12 andlor housing member 14 may be configured such that the
housing member 14 is longitudinally locked with respect to the sleeve member 12.
The housing member 13 and/or sleeve member 12 may be configured in any known
manner such they couple to one another and are longitudinally or axially locked with
respect to one another. In the illustrated embodiment, as shown best in FIG. 10, a
washer 46 may be coupled to the sleeve member 12 and extend about the sleeve
member 12 and the second detents 42. As best seen in FIGS. 4-6, the sleeve member
12 may include a groove or channel 47 in which the washer 46 can be partially
inserted (see FIG. 10). In such an arrangement, the washer 46 is longitudinally fixed
to the sleeve member 12. The longitudinal positioning of the groove 47 and washer
46 is configured such that the key 44 is secured between the washer 46 and a
longitudinal side surface of the second detent 42, thereby restricting longitudinal
movement of the key 44 towards the driving portion 22. Further, as the washer 46
extends about the periphery of the sleeve member 12 and not only about the second
detents 42, the washer 46 abuts the housing member 14 and thereby restricts
longitudinal movement of the housing member 14 towards the driving portion 22. As
explained further below, a cam disc 16 can be coupled to the housing member 14 on
the side of the housing member 14 that opposes the washer 46. The housing member
14 and the cam disc 16 can be configured such that the side of the cam disc 16 that
faces the driven portion 26 abuts the collar or raised portion 38 about the lateral
coupling pin aperture 32 of the sleeve member 12. In this way, the housing member
14 (and the cam disc 16) is positioned between the washer 46 and the collar 38 such
that longitudinal movement of the housing member 14 (and the cam disc 16) along the
sleeve member 12 (i.e., along the longitudinal axis X-X) is restricted or substantially
prevented. Stated differently, the sleeve member 12 and housing member 14 may be
configured such that the housing member 14 is longitudinally fixed to the sleeve
member 12. Thereby, in the illustrated embodiment, the housing member 14 is
rotationally fixed to the sleeve member 12 via the second detent 42, key 44 and
keyway 44, and longitudinally fixed to the sleeve member 12 via the groove 47,
washer 46, collar 38 and cam disc 16.
As shown in FIG. 9, the housing member 14 may be configured to
support, at least partially, an energy mechanism 40 used to decouple the sleeve
member 12, and thereby the actuator decoupler 10, from the driven part 30B by
removal of each coupling pin 20 from the lateral coupling pin aperture 34 of the
driven part 30B. The energy mechanism 40 may be any known energy mechanism,
such as any mechanism known for providing energy, storing energy, releasing energy,
being preloaded and combinations thereof. For example, the energy mechanism 40
may be an energy mechanism capable of being coupled to the housing member 14 and
resiliently deformed or otherwise preloaded to store energy that can be released upon
actuation at least partially, by the actuator decoupler 10. Further, the quantity of the
members or elements comprising the energy mechanism 40 may vary. The amount of
energy capable of being stored and provided by the mechanism making up the energy
mechanism 40 may be determinative of the quantity of such mechanisms 40. For
example, a particular application of the actuator decoupler 10 may dictate the
necessary quantity of energy needed to remove each coupling pin 20 from the pin
aperture 34 of the driven part 30, and therefore the amount of energy elements
required such that the energy mechanism 40 is capable of providing the necessary
preloaded energy to remove each coupling pin 20 from the coupling pin aperture 34.
It is noted however, that the fewer the energy elements making up the energy
mechanism 40, the more reliable the energy mechanism 40 and, thereby, the actuator
decoupler 10. To this end, the illustrated energy mechanism 40 is comprised on a
single helical resilient spring (i.e., a single energy element) capable of providing an
amount of stored energy that is sufficient to translate each coupling pin 20 out of
engagement within the lateral coupling pin aperture 34 of the driven part 30B when
the driven part 30B is a component of a power screw and the actuator decoupler 10 is
installed in an actuation system of a flight control surface of an aircraft.
The illustrated housing member includes a longitudinally extending
inner portion about the sleeve member 12, and the energy mechanism or resilient
member 40 is provided thereabout, as shown best in FIG. 9. The energy mechanism
40, such as the illustrated exemplary resilient torsion spring, may be configured such
that a first portion or end of the energy mechanism 40 can be fixed to the housing
member 14, and a second portion or end can be deformed to preload the energy
mechanism 40. As shown in FIGS. 9 and 10, the illustrated energy mechanism or
torsion spring 40 is configured to mate with a bolt, pin, screw or other known
fastening mechanism at both the first and second end or portion of the energy
mechanism 40, and the housing member 14 includes a series of energy mechanism
apertures 32 at different radial or lateral andlor rotational or angular positions about
the longitudinal axis X-X for mating with the fastening mechanism. In such a
configuration, the housing member 14 is configured to accept energy mechanisms 40
of differing sizes (and thus differing energy potentials) and orientations of the energy
mechanism 40, and is thereby customizable based on the load requirements of a
particular actuation system in which the actuator decoupler 10 is installed. The
fastening of the first end of the energy mechanism 40 to the housing member 14 may
rotationally and longitudinally lock the energy mechanism 40 with respect to the
sleeve member 12 (except for any rotationally and longitudinally movement caused
by deformation of the spring). As explained further below, the second end or portion
of the torsion spring, torsion bar or like energy mechanism 40 can be deformed such
that it is twisted (e.g., partially unwound or wound) to store mechanical energy in the
form of a preloaded torque proportional to the amount it is twisted. It is noted that
bending stresses in the torsion spring, torsion bar or like energy mechanism 40 caused
by the twisting may result in the preloaded torque or moment force. As also
explained further below, because the first portion or end of the energy mechanism 40
is fixedly coupled to the housing member 14, which is at least rotationally and
longitudinally fixedly coupled to the sleeve member 12, after twisting the second end
of the energy mechanism 40 the second end will rotationally return, at least partially,
to its pre-deformed position if the resistance of the mechanism coupled to the second
end or portion provides less resistance than the resistance applied to the first end or
portion (i.e., the resistance applied by the sleeve member 12 by the driving part 30A
and the driven part 30B (in the coupled state)) and the reactionary preloaded torque
of the energy mechanism 40 is sufficient to overcome the resistance provided by the
mechanism coupled to the second end or portion.
As shown in FIGS. 1 1-13 and briefly discussed above, a cam disc 16
may be positioned about the sleeve member 12 and adjacent the housing member 14
between the housing member 14 and the collar 38 of the sleeve member 12 such that
longitudinal translation of the housing member 14 and the cam disc 16 is substantially
prevented by the collar 38 and the washer 46. The cam disc 16 may be disc shaped
and configured to substantially symmetrically surround the sleeve member 12. In
such a configuration, the cam disc 26 may be particularly well suited for rotation with,
and about, the longitudinal axis X-X the sleeve member 12. To aid in rotational or
angular translation about the sleeve member 12 (and therefore the longitudinal axis XX),
the cam disc 16 may include a bearing mechanism 62 between the inner surface of
the cam disc 16 and the outer surface of the sleeve member 12. In such a
configuration, as shown in the illustrated embodiment in FIGS. 11 and 13, the friction
between the cam disc 16 and sleeve member 12 is reduced as compared to a
configuration where the inner surface of the cam disc was in direct contact with the
outer surface of the sleeve member 12. Thereby, as further discussed below, the
resistance encountered to rotate the cam disc 16 to translate each pin 20 out of the
lateral coupling pin aperture 34 of the driven part 30B to decouple the driving part
30A from the actuator decoupler 10 and the driven part 30B is kept to a minimum.
The second end or portion of the energy mechanism 40 may be
coupled to the cam disc 16, as shown in FIGS. 12 and 13. In the illustrated
embodiment, the cam disc 16 includes a series of energy mechanism apertures 64 at
different radial or lateral andlor angular or rotational positions about the longitudinal
axis X-X for mating with the fastening mechanism and the second end or portion of
the energy mechanism 40. In such a configuration, the housing member 14 is
configured to accept energy mechanisms 40 of differing sizes (and thus differing
energy potentials) and orientations of the energy mechanism 40 (the position of the
second end or portion of the energy mechanism 40 as compared to the position or
orientation of the first end for example), and is thereby customizable based on the
load requirements of a particular actuation system in which the actuator decoupler 10
is installed.
The configuration of the housing member 14, energy mechanism 40
and cam disc 16 illustrated in FIGS. 1 1 - 13 allows the cam disc 16 to be rotated about
the sleeve member 12 and longitudinal axis X-X, and therefore rotated with respect to
the housing member 14, to twist or otherwise deform the second end or portion of the
energy mechanism 40 with respect to the first end or portion to pre-load the energy
mechanism 40. To aid in preloading the actuator decoupler 10 (i.e., deforming the
energy mechanism 40), the cam disc 16 may include an engageable mechanism 66 to
rotate the cam disc 16 about the sleeve member 12 and longitudinal axis X-X to
deform the energy mechanism 40. In the illustrated embodiment, as best shown in
FIGS. 11 and 12, the cam disc 12 includes apertures 66 extending from the outer
surface of the cam disc 16 toward the longitudinal axis X-X. The apertures 66 in the
outer surface of the cam disc 16 may be engaged with a lever arm, for example, to
assist a user in rotating the cam disc 12 to twist or otherwise deform the energy
mechanism 40 to apply the preload force or bias of the actuator decoupler 10.
The actuator decoupler 10 is preferably configured to selectively retain
or lock the preloaded condition of the energy mechanism 40 such that a secondary
actuator can selectively retain or release the preload to couple or decouple,
respectively, the actuator decoupler 10 and the driving part 30A from the driven part
30B, as explained further below. The mechanism or configuration of the actuator
decoupler 10 that achieves such selectively retaining and releasing of the preloaded
energy of the energy mechanism 40 may take any form know in the art capable of
interacting with a secondary actuator. For example, a secondary actuator may be
capable of detecting a jam in an actuation system in which the actuator decoupler 10
is installed in the driving part 30A, in the load recipient or otherwise upstream fiom
the actuator decoupler 10, and in reaction to such a jam, release the preloaded energy
of the energy mechanism 40 to translate each coupling pin 20 out of engagement
within the coupling pin aperture 34 of the driven part 30B to disengage the actuator
decoupler 10 and the driving part 30A from the driven part 30B and the rest of the
actuation system that is positioned upstream from the actuator decoupler 10. In such
a configuration, the driven part 30B may be capable of both rotational or angular
translation about, and longitudinal or axial translation along, the longitudinal axis XX
of the sleeve member 12. As is known in the art, when the driven part 30B is
decoupled and free to translate (e.g., at least one of angularly and axially)
independent of the driving part 30A and a jam is present between the load recipient
and the actuator decoupler 10, the load recipient may none-the-less be capable of
functioning, at least partially. For example, if the driven part 30B is a component of a
power screw, and the load recipient is a flight control surface of an aircraft and is
coupled to the power screw, a jam or other malfunction in the power screw
mechanism would tend to lockup the actuation system such that movement of the
flight control surface would be prevented by the jammed actuation system. Further,
the jammed actuation system would prevent other actuation systems coupled to the
flight control surface from actuating the flight control surface. However, if the
actuator decoupler 10 was installed in the jammed actuation system, the secondary
actuator may be capable of detecting the jam and in response thereto trigger the
actuator decoupler 10 to disengage the jammed power screw mechanism from the
driven part 30B to thereby allow the power screw to longitudinally andlor rotationally
translate. Such longitudinal or axial and rotational or angular translation of the power
screw would free-up the jam and allow other non-jammed actuation systems coupled
to the flight control surface to, at least partially, actuate (e.g., move) the flight control
surface. Further, decoupling the driving part 30A from the jammed power screw
would prevent the driving part 30A from applying additional destructive loads to the
jammed system that would tend to enhance or expand the jam andlor damage other
components of the actuation system.
Selective retention and release of the preload of the energy mechanism
40 is achieved in the illustrated embodiment through the use of slots 68 in the outer
surface of the cam disc 16 interacting with a protrusion of a locking member or lever
arm 50 provided on an outer portion of the housing member 14 that is positioned
adjacent to the outer surface of the cam disc 16, as best shown in FIGS. 11, 12 and
14-16. The locking member 50 of the housing member 14 and the slots 68 of the cam
disc 16 thereby prevent the cam disc 16 from rotating about the sleeve member 12 and
longitudinal axis X-X, and thereby prevent any preloaded torque of the energy
mechanism 40 from being released. Thus, the energy mechanism 40 must be
preloaded (i.e., deformed) before the cam disc 16 is selectively rotationally fixed to
the housing member 14 (and thereby the sleeve member 12) via the locking member
50.
As best shown in FIGS. 14-16, the locking member 50 of the
illustrated embodiment may be hinged to the housing member 14 via a hinge pin 52
that extends through a portion of the housing member 14 and the locking member 50.
The hinge pin 52 thereby represents an axis about which the locking member 50 is
capable of pivoting or rotating. The illustrated locking member 50 also includes a
first arm 54 that is configured to extend from the portion of the locking member 50
engaging the pin 52 (i.e., the axis of rotation). The lever arm may include a
protrusion 56 extending from the first arm 54 configured to mate with the slots 68
provided about the outer surface of cam disc 16. Thereby, the locking member 50 is
configured to rotate about the pin 52 into a first orientation such that the protrusion 56
in engaged within a slot 68 of the cam disc 16 as shown in FIGS. 14 and 15, and into
a second orientation such that the protrusion 56 is spaced from the slot 68 of the cam
disc 16 as shown in FIG. 15. In the first orientation, the cam disc 16 is prevented
from rotating with respect to the housing member 14, and therefore the sleeve
member 12, because the protrusion 56 of the first arm 54 of the locking member 50
engages the cam disc 16 via a slot 68. The engagement of the protrusion 56 of the
first arm 54 of the locking member 50 with a slot 68 of the cam disc 16 can be best
seen by the cross-sectional view of FIG. 15 of the illustrated embodiment. In this
way, the cam disc 16 of the actuator decoupler 10 can be rotated about the sleeve
member 12 such that the energy mechanism 40 is preloaded, and the locking member
50 rotated about the pin 52 to engage the protrusion 56 of the first arm 54 with a slot
68 of the cam disc 16 to lock, fix, retain or otherwise prevent the cam disc 16 from
rotating about the sleeve member 12, as shown in FIGS. 14 and 15. To release the
preload of the energy mechanism and allow the cam disc to rotate about the sleeve
member 12, the locking member 50 can be rotated about the pin 52 to disengage the
protrusion 56 of the first arm 54 from the slot 68 to allow the preloaded torque of the
energy mechanism 40 to act on the cam disc 16 and rotate the cam disc 16 about the
sleeve member 12 and longitudinal axis X-X, as shown in FIG. 16.
As also shown in FIGS, 14 and 16, the cam disc 16 may include
numerous slots 68 about the outer surface of the cam disc 16 to provide numerous
locations along the outer surface of the cam disc 16 for the locking member 50 to
engage, and thereby allow the cam disc 16 to be coupled to the housing member 14 in
differing rotational or angular orientations. In such a configuration, the cam disc 16 is
configured to function with energy mechanisms 40 of differing sizes (and thus
differing energy potentials) and differing orientations of the energy mechanism 40
(and thus differing amounts of preloads), and is thereby customizable based on the
load requirements of a particular actuation system in which the actuator decoupler 10
is installed. For example, the more the cam disc 16 is rotated about the sleeve
member 12, the more the energy mechanism 40 is deflected and the greater the
preload. The angular amount the cam disc 16 is rotated, and therefore the amount of
preload achieved, can be customized by engaging the locking member 50 with
differing slots 68 about the cam disc 16.
The above-described configuration of the locking member 50 and the
cam disc 16 such that the locking member 50 includes the protrusion 56 and the cam
disc includes a slot 68 is advantageous over a configuration wherein the locking
member 50 includes the slot 68 and the cam disc 16 includes the protrusion 56. For
example, machining or otherwise forming the protrusion 56 tends to be more costly
and time consuming than machining or otherwise forming the slots 68. As a result,
forming only one protrusion 56 on the locking member 50 and multiple slots 68 of the
cam disc 16 is cost and time efficient. Further, the preload torque of the energy
mechanism 40 will exert a shear stress on the protrusion 56, and therefore the
protrusion 56 may develop fatigue and deterioration or other damage over time.
Replacement of the illustrated locking member 50 is less expensive and simpler than
replacement of the cam disc 16. Thus, providing the protrusion 56 on the locking
member 50 as opposed to the cam disc 16 is further cost and time efficient.
The locking member 50 may also include a second arm 58 and a third
arm 60 for interaction with a secondary actuator 71 to retain and release, respectively,
the first lever arm 54 in engagement with the cam disc, as shown in the illustrated
embodiment in FIG. 15. The exemplary locking member 50 includes a second arm 58
and a third arm 60 configured in a "V" shape such that a secondary actuator 71 can be
positioned between the second 58 and the third arm 60. In such a configuration, the
secondary actuator 71 can act to retain the locking member 50 in the coupled state
with the cam disc 16 by preventing the second arm 60 of the locking member 50 from
rotating in a direction such that the protrusion 56 of the first arm 54 is disengaged
from a slot 68 of the cam disc 16. As shown in FIG. 15, when a secondary actuator
71 is maintained in a positioned located between the second arm 58 and a third arm 60
of the locking member 50 when the locking member 50 is engaged with the cam disc
16, the locking member 50 is prevented from rotation about the pin 52 by the
interaction of the third arm 60 and the secondary actuator 71. Thereby, the
configuration of the locking member 50 and the secondary actuator 71 prevents
accidental or erroneous uncoupling of the cam disc 16 such that the cam disc 16 is
able to rotate due to the torque provided by the. energy mechanism 40 being
accidentally released. In this manner, the actuator decoupler 10 can utilize a
secondary actuator 71 to monitor for a jam in the actuation system in which the
actuator decoupler is installed, and only release the preload energy of the energy
mechanism 40 when a jam is detected. Release of the preload energy due to
accidental movement of the lever arm 50, such as from shock or vibration for
example, is prevented by the third lever arm 60 and the secondary actuator 7 1.
If the secondary actuator 71 does detect a jam in the actuation system
in which the actuator decoupler 10 is installed, the secondary actuator 71 can be
responsive and triggered to translate longitudinally to rotate the locking member 50
about the pin 52 such that the first arm 54 is translated away from the cam disc 16 and
the protrusion 56 of the first arm 54 is disengaged from a slot 68 of the cam disc 16,
as shown in FIG. 16. More specifically, from the coupled state where the secondary
actuator 71 is positioned between the second arm 58 and third arm 60 and the locking
member 50 is engaged with a slot 68 of the cam disc 16 (FIG. 15), the secondary
actuator 71 can be translated longitudinally to interact with the second arm 58 to
rotate the locking member 50 about the pin 52 to translate the protrusion 56 of the
first arm 54 out from a slot 68 of the cam disc 16 to rotationally release the cam disc
16 (FIG. 16). In this way, the secondary actuator 71 can actuate the actuator
decoupler 10 to release the preload energy (i.e., torque) of the energy mechanism 40
to allow the cam disc 16 to rotate about the sleeve member 12 and, ultimately,
translate each coupling pin 20 from the lateral coupling pin aperture 34 of driven
portion 30B, as explained further below.
As shown in FIGS. 1, 3, 9 and 1 1-1 3, the actuator decoupler 10 may
include multiple mechanisms to selectively couple and uncouple the cam disc 16 and
the housing member 14 to selectively lock the cam disc 16 from rotation via the
preloaded torque of the energy mechanism 40. In the illustrated embodiment, the
actuator decoupler 10 includes two diametrically opposed locking members 50 for
engagement with slots 68 about the outer surface of the cam disc 16. In such a
configuration, the secondary actuator 71 for actuation of the locking members 50,
such as the secondary actuator 71 depicted in the cross-sectional view of FIG. 15, may
include a ring-shaped member that extends about the actuator decoupler 10 and
through the second 58 and third 60 arms of the locking members 50, as described
above. The ring-shaped member of the secondary actuator 71 may be coupled to a
mechanism that is capable of longitudinally or axially translating the ring member to
engage the second arm 58 of the locking member 50 to decouple the cam disc 16 and
housing member 14 (and thereby ultimately decouple the actuator decoupler 10 and
the driving part 30A from the driven part 30B). For example, the actuator decoupler
10 may include a ring-shaped member for interaction with multiple lever arms 50
coupled to a hydraulic system for longitudinally translating the ring-shaped member
to actuate the locking members 50 via the second lever arm 58. In this way, the
actuator decoupler 10 can rotate about the longitudinally axis X-X and within the
ring-shaped member of the secondary actuator 71. As stated above, however, any
known secondary actuation mechanism or system may be used to decouple the cam
disc 16 from the housing member 14 and/or sleeve member 12 such that the preloaded
torque of the energy mechanism rotates the cam disc 16 to, ultimately, translate each
coupling pin 20 from within the lateral coupling pin aperture 34 of the driven part
30B.
The cam disc 16 may also include one or more cam inserts 70 defining
a cam slot 72 therethrough, as depicted in FIGS. 1 1, 13, 17, 2 1 and 22. The cam disc
26 and each cam insert 70 may be configured such that each cam insert 70 can be
selectively secured to the cam disc 16. For example, the cam disc 16 and each cam
insert 70 may be configured such that each cam insert 70 can be bolted, pinned or
otherwise removably secured to the cam disc 16. In such an arrangement, the cam
disc 16 can be customized with differing cam inserts 70 for a particular coupling pin
20, sleeve member 12, driving part 30A, actuation system in which the actuator is
installed and combinations thereof, for example. In the illustrated embodiment as
shown in FIGS. 1 1 and 17, the actuator decoupler 10 includes two coupling pins 20
(see FIGS. 3, 7 and 8) and therefore includes two removable can inserts 70. As best
shown in' FIG. 17, a cam pin 74 may be inserted in each cam slot 72 and through an
aperture 76 of the head of each pin 20. In this way, each coupling pin 20 is coupled in
the aperture 32 of the sleeve member 12 and to a cam slot 72 via a cam pin 74.
Each cam pin 74 and cam slot 72 may be configured such that a first
end of the cam pin 74 is slidably and/or rotatably received within a corresponding
cam slot 72. As such, the relative dimensions of each cam pin 74 and cam slot 72
may be dependent upon, or at least related to, each other. Further, each cam pin 74
and cam slot 72 can be configured such that each cam pin 74 is carried within a
corresponding cam slot 74, and each cam pin 74 is capable of moving along the
corresponding cam slot 74 according to the profile of the cam slot 72. As best shown
in FIG. 11, each cam slot 72 defines a particular profile that extends angularly or
rotationally and laterally or radially about the cam disc 16 and longitudinal axis X-X
such that a first side or portion of the profile of each cam slot 72 is laterally or radial
positioned proximate to the sleeve member 12 and longitudinal axis X-X and the
opposing angularly or rotationally spaced second side or portion of the cam slot 72 is
laterally or radially distal the sleeve member 12 and longitudinal axis X-X as
compared to first side (i.e., the first side or portion is relatively laterally or radially
closer to the longitudinal axis X-X as compared to the second side or portion).
In some embodiments, one end of each cam pin 74 is carried within a
corresponding cam slot 72 in the cam disc 16, passes through an aperture 76 of a
coupling pin 20, and the second end of each cam pin 74 is carried within a
corresponding cam slot 76 in a cam disc cover 18 coupled to the cam disc 16, as
shown in FIGS. 13,20 and 21. In such embodiments, the cam disk cover 18 and cam
disc 16 may be configured such that each pin 20 is positioned between the disc cover
18 and the cam disc 16, and each corresponding cam pin 74 spans from a cam slot 72
of the cam disc 16 to a corresponding cam slot 76 of the cam disc cover 18. The cam
disc cover 18 may define the cam slot 72, or may include a cam slot insert as like with
the illustrated cam disc 16. By supporting both end portions of each cam pin 74, the
cam disc 16 and cam disc cover 18 may be particularly effective in translating each
cam pin 74 without rocking, bending or otherwise unevenly or smoothly translating
each cam pin 74 smoothly along corresponding cam slots 72, 76. The cam disc 16
and the cam disc cover 18 may thereby form two longitudinally spaced cam members
or cam disc members including substantially aligned cam slots 72, 76, or a pair of
substantially aligned cam slots 72, 76, defining a cam profile.
The cam disc 16 and the cam disc cover 18 may include any number of
pairs of cam slots 72, 76 (and associated structure). For example, the cam disc 16 and
the cam disc cover 18 may include one pair of cam slots 72, 76 (and thereby one
corresponding coupling pin 20) (not shown). As another example, as shown in the
illustrated embodiment in FIGS. 1 7 and 1 8, the cam disc 16 and the cam disc cover 18
may include two pair of cam slots 72, 76 diametrically opposed from one another
about the longitudinal axis X-X of the sleeve 12 (and associated structure). In such an
embodiment, the actuator decoupler 10 is substantially symmetrical about the
longitudinal axis X-X and thereby is advantageously configured for rotation about the
longitudinal axis X-X. In other embodiments (not shown), the cam disc 16 and the
cam disc cover 18 of the actuator decoupler 10 may include more than two pairs of
cam slots 72, 76. For example, the cam disc 16 and the cam disc cover 18 may
include an even number of pairs of substantially aligned cam slots 72, 76
symmetrically disposed about the longitudinal axis X-X (and associated structure).
In another embodiment (not shown), the cam disc 16 and the cam disc cover 18 of the
actuator decoupler 10 may include an odd number of pairs of cam slots 72, 76 (and
associated structure). In yet another alternative embodiment, only one of the cam
disc 16 and the cam disc cover 18 may be provided, and thereby each pin 20 may be
received in only one cam slot 72 or 76.
The configuration of the exemplary cam slots 72, 76 of the illustrated
cam disc 16 and the cam disc cover 18 is depicted in FIG. 19. For brevity purposes,
the cam disc 16 and the cam disc cover 18 are represented by a circle, and many of
the other components and aspects of the actuator decoupler 10 are not included. As
shown in the illustration of FIG. 19, the cam disc 16 and cam disc cover 18 may be
configured to rotate about the longitudinal axis X-X of the sleeve member 12 in a
substantially counterclockwise direction of rotation R by the torque of the torsion
spring 40. In such a configuration, the torsion spring 40 would have been preloaded
by twisting the torsion spring 40 in a substantially clockwise direction of rotation,
such as by rotating the cam disc 16 in a clockwise direction of rotation about the
sleeve member 12. It is noted, however, that the cam disc 16 and cam disc cover 18
may alternatively be configured to rotate in a substantially clockwise direction of
rotation R, and the torsion spring 40 thereby preloaded by twisting the torsion spring
40 in a substantially counterclockwise direction of rotation.
As can be seen from FIG. 10, the profile of the cam slots 72, 76 of the
cam disc 16 and the cam disc cover 18 may be configured such that a first end 80 of
the cam slots 72, 76 is laterally or radially positioned a first distance Dl from the
longitudinal axis X-X (the axis of rotation of the cam disc 16 and the cam disc cover
18). Further, the cam slots 72, 76 may angularly and radially extend such that a
second end 82 of the cam slots 72, 76 is radially positioned a second distance D2 from
the longitudinal axis X-X and angularly spaced in a direction opposite the direction of
rotation R a predefined degree of angulation or rotation 81. As the second lateral or
radial distance D2 of the second side 82 of the cam slots 72,76 is greater than the first
lateral or radial distance Dl of the first side 80 of the cam slots 72, 76, the cam pin 74
carried within the cam slots 72, 76 travels along the cam slots 72, 76, the cam pin 74
is laterally or radially translated away from the sleeve member 12 and longitudinal
axis X-X. For example, as shown in FIG. 19, a cam pin 74 may be positioned
adjacent the first end 80 of a pair of cam slots 72, 76 when the actuator decoupler 10
is selectively coupled to a driven part 30B of an actuation system, and the actuator
decoupler 10 is activated to release the preload torque of the torsion spring 40 to
rotate the cam disc 16 and the cam disc cover 18, and thereby the cam slots 72, 76,
about the sleeve member 12 and longitudinal axis X-X in the counterclockwise
direction of rotation R. As the cam slots 72, 76 are rotated about the sleeve member
12 and longitudinal axis X-X, each cam pin 74 is kept from rotating about the
longitudinal axis X-X by the interaction of the coupling pin with at least the lateral
coupling pin aperture 32 of the sleeve member 12. Thereby, as the cam slots 72, 76
rotate in the direction of rotation R, the cam pin 74 is carried along the cam slots 72,
76 in a direction from the first end 80 to the second end 82, as indicated by the arrow
in FIG. 19. Since, as described above, the second end 82 of the cam slots 72, 76 is
positioned laterally or radially further from the longitudinal axis X-X than the first
end 80, each cam pin 74, and the coupling pin 20 coupled thereto, is translated
laterally or radially away from the sleeve member 12 and the longitudinal axis X-X.
The size of the cam slots 72, 76, the size of the cam pin 74, the first and second lateral
or radial distances Dl, D2 of the cam slots 72, 76, and the angular degree to which the
cam disc 16 and the cam disc cover 18 rotate all effect the total lateral or radial
distance each cam pin 74, and therefore the coupling pins 20 coupled thereto,
translate.
As shown in FIG. 19, the profile of the cam slots 72, 76 may be
configured such that a passive portion 84 of the cam slots 72, 76 adjacent the first end
80 includes a lesser degree of lateral or radial slope, incline or translation rate as
compared to that of an aggressive portion 86 of the cam slots 72, 76 adjacent the
second end 82. In such an arrangement, the cam slots 72, 76 will likely experience a
smaller degree of forces resulting from the interaction of the surfaces of the cam pin
74 that tend to resist movement of the slots 72, 76 about the cam pin 74 in the passive
portion 84 of the cam slots 72, 76 as opposed to the aggressive portion 86. The less
resistive or destructive nature of the passive portion 84 of the cam slots 72, 76 may
therefore be advantageous to initiate rotational movement of the cam disc 16 and the
cam disc cover 18, and thereby lateral or radial translation of the cam pin 74 and the
coupling pin 20 coupled thereto, via the torque applied by the torsion spring 40. Once
the cam disc 16 and the cam disc cover 18 have gained kinetic energy andlor
momentum, movement of the aggressive portion 86 of the cam slots 72, 76 about the
cam pin 74 can be accomplished with use of the combination of at least the torque
applied by the torsion spring 40 and the kinetic energy andlor momentum of the cam
disc 16 and the cam disc cover 18. In this way, the arrangement of the passive portion
84 and the aggressive portion 86 of the cam slots 72, 76 may require less torque force
as compared to other arrangements or configurations of the cam slots 72, 76 to
laterally translate the cam pins 74, and therefore the coupling pins 20 coupled thereto.
Exemplary alternative embodiments of the cam slots 72, 76 of the cam
disc 16 and the cam disc cover 18 are shown in FIG. 20 and generally indicated by
reference numerals 172 and 176, respectively. The cam slots 172, 176 are similar to
cam slots 72, 76 described above with reference to FIG. 19, and therefore like
reference numerals preceded by the numeral "1" are used to indicate like elements.
Exemplary cam slots 172, 176 include a first end 180 and a passive portion 184
adjacent the first end 180. The first end 180 and passive portion 184 define the
portions of the cam slots 172, 176 that are positioned laterally or radially closest to the
sleeve member 12 and longitudinal axis X-X. As a result, the cam pin 74 of the
actuator decoupler 10 may initially be positioned at the first end 180 within the
passive portion 184 in the selectively coupled state of the actuator decoupler 10.
The exemplary passive portion 184 of the cam slots 172, 176 is
configured such that the lateral or radial distance between the passive portion 184 and
the sleeve member 12 and longitudinal axis X-X is constant over the degree of
angulation or rotation 02 of the passive portion 184 (i.e., constant over the entire angle
formed between the side edges of the passive portion 184). Stated differently, the
passive portion 184 is configured as an arcuate shape of a single radius formed about
the longitudinal axis X-X. As the passive portion 184 does not include a lateral or
radial slope or translation, the cam disc 16 and the cam disc cover 18 will encounter a
relatively small amount of forces by the cam pin 74 acting in a manner that opposes
rotation of the cam disc 16 and the cam disc cover 18 about the sleeve member 12 and
longitudinal axis X-X in the direction of rotation R. Thereby, the torque applied to
the cam disc 16 and the cam disc cover 18 by the torsion spring 40 in the decoupled
state of the actuator to rotate the cam disc 16 and the cam disc cover 18 about the
longitudinal axis X-X while the cam pin 74 travels within the passive portion 184
over the degree of angulation or rotation 82 of the passive portion 184 may be
relatively small. However, because the passive portion 184 produces a relatively
small level of resistance to the cam slots 172, 176 via the cam pin 74, the cam disc 16
and the cam disc cover 18 may quickly and easily rotate about the sleeve member 12
and longitudinal axis X-X in the direction of rotgtion R a degree of rotation equal to
the degree of angulation or rotation 02 of the passive portion 184 such that the cam
pin 74 passes through the passive portion 184 and to an adjacent aggressive portion
186A-C.
As the cam disc 16 and the cam disc cover 18 rotate about the sleeve
member 12 and longitudinal axis X-X in the direction of rotation R such that the
passive portion 1 18 of the cam slots 172, 176 is translated over the cam pin 74, the
cam disc 16 and the cam disc cover 18 gain kinetic energy and/or momentum. Once
the cam disc 16 and the cam disc cover 18 rotate through the angulation 02 of the
passive portion 184, further rotation of the cam disc 16 and the cam disc cover 18
abuts an aggressive portion 186A-C against the cam pin 75 because the aggressive
portion 186A-C includes a lateral or radial slope or dimension, as shown in FIG. 19.
FIG. 19 shows three differencing aggressive portions 186A-C - a first aggressive
portion 186A, a second aggressive portion 186B and a third aggressive portion 186C.
Only one of the first, second and third aggressive portions 186A-C can be used at a
time to pair with a passive portion 184 to form a cam slot 172, 176. Stated
differently, FIG. 19 illustrates a first aggressive portion 186A, a second aggressive
portion 186B and a third aggressive portion 186C that are not meant to be used in
combination, as depicted, but rather only one of the aggressive portions 186A-C used
per cam slot 172, 176.
As the cam disc 16 and the cam disc cover 18 rotate through the
passive portion 184, they thereby include gain kinetic energy andlor momentum when
the cam slots 172, 176 first laterally or radial interact with the cam pin 17 in the
aggressive portion 186A-C. In such a configuration, the aggressive portion 186A-C
of the cam slots 172, 176 applies a shock or impact force to the cam pins 74 (i.e., a
sudden lateral or radial acceleration caused by the impact of the aggressive portion
186A-C on the cam pins 74). The application of a shock or impact force on the cam
pins 74 may be advantageous because such a force or acceleration typically has a
greater effect than a lower force applied over a proportionally longer period of time
due to the force being applied to the cam pin 74 before the cam pin 74 is able to
disperse such forces. In this way, the cam slots 172, 176 may be configured such that
the passive portion 184 is configured to allow the cam slots 172, 176 to achieve a
velocity/acceleration, and the aggressive portion 186A-C of the cam slots 172, 176 is
configured to apply a shock or impact force to the cam pin 74 in a lateral or radial
direction to overcome the resistive forces applied to the cam pin 74, such as static
friction, to laterally or radially translate each cam pin 74 and each coupling pin 20
coupled thereto.
The particular configuration of the aggressive portion 186A-C may
depend upon the particular actuation system in which the actuator decoupler 10 is
installed and the particular configuration of the actuator decoupler 10. For example,
the configuration of the aggressive portion 186A-C of the cam slots 172, 176 may
depend, or at least be related to, the amount of each coupling pin 20 engaged within a
lateral coupling pin aperture 34 of the driven part 30B, the amount of torque applied
by the torsion spring 40, the amount of kinetic energy and momentum the cam disc 16
and the cam disc cover 18 achieve during the passive portion 1 18, and the amount of
lateral or radial shock or impact force needed to overcome the resistance forces of a
particular cam pin 74 to laterally or radially translate the cam pin 74 and the coupling
pin 20 coupled thereto.
FIG. 20 illustrates three exemplary aggressive portions 186A-C of the
cam slots 172, 176. A first aggressive portion 186A includes a relatively steep lateral
or radial slope, a relatively large lateral or radial translation or extension, and extends
for relatively short angular distance. As shown in FIG. 20, the lateral or radial slope
of the first aggressive portion 186A increases as the first aggressive portion 186A
angularly extends from the passive portion 184 to the second end 186A. The first
aggressive portion 186A may thereby require a relatively large rotational torque of the
torsion spring 40, a relatively large shock or impact force or a combination thereof for
the first aggressive portion 186A to laterally or radially translate the cam pin 74 to the
second end 182A. However, the first aggressive portion 186A requires a relatively
small amount or degree of angular rotation of the cam slots 172, 176, and therefore
the cam disc 16 and the cam disc cover 18. Further, the relatively large lateral or
radial translation or extension of the first aggressive portion 186A allows the coupling
pins 20 to be positioned relatively deep in the coupling pin aperture 34 of the driven
portion 30B.
As can be seen from FIG. 20, in contrast to the exemplary first
aggressive portion 186A, the exemplary second aggressive portion 186B includes a
relatively shallow lateral or radial slope, a relatively short lateral or radial translation
or extension, and extends for relatively large angular distance. The second aggressive
portion 186B may thereby require a relatively small rotational torque of the torsion
spring 40, a relatively small shock or impact force or a combination thereof for the
second aggressive portion 186B to laterally or radially translate the cam pin 74 to the
second end 182B. However, the second aggressive portion 186B requires a relatively
large amount or degree of angular rotation of the cam slots 172, 176 and therefore the
cam disc 16 and the cam disc cover 18.
As can also be seen from FIG. 20, in contrast to the exemplary first
aggressive portion 186A and the exemplary second aggressive portion 186B, the
exemplary third aggressive portion 186C includes a relatively shallow lateral or radial
slope, a relatively short lateral or radial translation or extension, and extends for
relatively large angular distance. The third aggressive portion 186C may thereby
require a relatively small rotational torque of the torsion spring 40, a relatively small
shock or impact force or a combination thereof for the second aggressive portion
186B to laterally or radially translate the cam pin 74 to the second end 182B.
However, the second aggressive portion 186B requires a relatively large amount or
degree of angular rotation of the cam slots 172, 176 and therefore the cam disc 16 and
the cam disc cover 1 8.
The third aggressive portion 186C is further configured such that the
furthest lateral or radial translation or extension of the third aggressive portion 186C
is positioned adjacent to the second end 182C of the third aggressive portion 186C, as
shown in FIG. 20. Stated differently, the lateral or radial position of the second end
182C of the third aggressive portion 186C is laterally or radially positioned closer to
the longitudinal axis X-X than the portion of the third aggressive portion 186C
adjacent the second end 182C. In such a configuration, as can be seen from FIG. 20,
the third aggressive portion 186C force the cam pin 74 and the coupling pin 20
coupled thereto to initially laterally or radially translate away from the longitudinal
axis X-X as the cam disc 16 and the cam disc cover 18 are rotated in the direction of
rotation R, and then laterally or radially translate partially back toward the
longitudinal axis X-X until the cam pin 74 abuts the second end 182C of the cam slots
172, 176 such that the maximum amount or degree of angulation of the cam disc 16
and cam disc cover 18 is exhausted.
The actuator decoupler 10 of FIGS. 1-3, and the components of the
actuator decoupler 10 illustrated in FIGS. 4-18, is shown in use in the cross-sectional
views of FIGS. 21 and 22. Specifically, FIG. 21 illustrates the actuator decoupler 10
in the coupled state wherein the actuator decoupler 10 couples the driving part 30A
and driven part 30B (and therefore the load recipient as discussed above), such that
the driving part 30A and driven part 30B are rotationally and longitudinally fixed to
one another via the coupling pins 20, and FIG. 22 illustrates the actuator decoupler 10
in the decoupled state wherein the actuator decoupler 10 has decoupled the driving
part 30A and the driven part 30B (and therefore the load recipient as discussed above)
such that the driven part 30B is capable of rotationally and longitudinally translating
independent of the driving part 30A and the actuator decoupler 10.
As shown in the cross-sectional view of FIG. 21, when the actuator
decoupler 10 is installed in an actuation system and configured in a selectively
coupled state, the driving part 30A of the sleeve member 12 can be coupled to a
driving part 30A (not shown), the driven part 30B can be positioned within the
longitudinally extending aperture 28 of the driven portion 26 of the sleeve member
12, and each coupling pin 20 can be engaged with the lateral coupling pin aperture 34
of the driven part 30B and the lateral coupling pin aperture 32 of the sleeve member
12. The driven part 30B and sleeve member 12 may be configured such that the
longitudinal axes X-X, XI -XI of the sleeve member 12 and driven part 30B are
substantially aligned. As each coupling pin 20 is laterally translatable via the cam
slots 72, 76 of the cam disc 16 and the cam disc cover 178, each coupling pin 20
thereby may selectively rotationally and longitudinally lock or fix the driven part 30B
(and therefore the load recipient coupled thereto) to the actuator decoupler 10 and the
driving part 30A (assuming the driving part 30A is rotationally and longitudinally
locked or fixed to the sleeve member).
Each coupling pin 20 may be positioned between the cam disc 16 and a
cam disc cover 16 (i.e., longitudinally spaced cam members or cam disc members)
and coupled to a corresponding cam pin 74. Each end of each cam pin 74 can be
carried within a corresponding pair of cam slots 72, 76 of the cam disc 16 and a cam
disc cover 18. The cam disc 16 and cam disc cover 18 can be rotatably coupled to the
sleeve member 12 via a bearing mechanism. Each cam slot 72, 76 of the pairs of cam
slots 72, 76 of the cam disc 16 and the cam disc cover 18 may be substantially the
same profile and they may be substantially aligned. The profile of each cam slot 72,
76 of the pairs of cam slots 72, 76 may be configured such that each cam slot 72, 76
extends laterally away from the longitudinal axes X-X, XI-XI of the sleeve member
12 and driven part 30B as each slot 72, 76 extends angularly or rotationally in a first
direction. In the coupled state of the actuator decoupler 110 and the driven part 30B,
each cam pin 74 is positioned in the portion of the corresponding pair of cam slots 72,
76 that is laterally closest to the longitudinal axes X-X, XI-XI, thereby laterally
positioning each coupling pin 20 within the lateral coupling pin aperture 34 of the
driven part 30B.
The rotational position of the cam slots 72, 76 with respect to the cam
pins 74 (and therefore the lateral position of the coupling pins 20 in the sleeve
member 12 and driven part 30) can be locked or maintained via the locking members
50, to retain the torque biasing the cam disc 16 and the cam disc cover 18 in the first
direction. Specifically, the locking members 50 may be coupled to the housing
member 14, which is rotationally and longitudinally locked to the sleeve member 12.
In such a configuration, a protrusion of a first arm of the locking member 50 may
selectively engaged with a slot 68 of the can disc 16. In this way, the locking member
50 prevents the biasing torque of the energy mechanism 40 from rotating the cam disc
16 and the cam disc cover 18 by locking the angular or rotational position of the cam
slots 72, 76, and therefore the lateral positioning of the coupling pins 20.
The locking member 50 may also include a second arm 58 and a third
arm 60 configured such that a secondary actuator 71 can be positioned between the
second 58 and third arm 60, as shown in FIG. 21. The second arm 58 may be
engaged and translated by the secondary actuator 71 to release the preload of the
energy mechanism 40 and decouple the driven part 30B from the actuator decoupler
10 and the driving part 30A, as explained above and further below. The configuration
of the third arm 60 and the secondary actuator 71 may retain the locking member 50
in the coupled state with the cam disc 16 by preventing first arm 54 from translating
in a longitudinal direction such that the protrusion 56 of the first arm 54 disengages
from the slot 68 of the cam disc 16. Thereby, the configuration of the locking
member 50 and the secondary actuator 71 prevents accidental or erroneous
uncoupling of the cam disc 16 such that the cam disc 16 is able to rotate due to the
torque provided by the energy mechanism 40. In this manner, the actuator decoupler
10 can utilize a secondary actuator 71 to monitor for a jam in the actuation system in
which the actuator decoupler 10 is installed, and only release the preload energy of
the energy mechanism 40 when a jam is detected.
In contrast to the coupled state of the actuator decoupler 10, FIG. 22
shows the actuator decoupler 10 in a decoupled state. The decoupled state may have
been responsive to a jam in the actuation system in which the actuator decoupler 10 is
installed. For example, if the driven part 30B is a component of a power screw that
controls, ultimately, a load recipient, a secondary actuator 71 may be configured to
detect a jam in the power screw and interact with the second arm 58 of the locking
member 50 (see FIGS. 15 and 21) to rotate the locking member 50 about the pivot
point 52 to disengage the protrusion 56 of the first arm 54 from a slot 68 of the cam
disc 18, as shown in FIG. 22. In such an embodiment, the preload torque of the
torsion spring 40 is no longer prevented from acting on the cam disc 16.
As such, as shown in FIG. 22, the torsion spring 40 can act of the cam
disc 16 and thereby rotate the cam disc 16 and cam disc cover 18 about the sleeve
member 12 and, as a result, rotate the cam slot 72 of the cam disc 16 and the
corresponding cam slot 76 of the cam disc cover 18 about the longitudinal axis X-X.
As also shown in FIG. 22, rotation of the pairs of cam slots 72, 76 will force the cam
pins 74 from a first angular side or portion of the cam slots 72, 76 that is positioned
laterally closer to the sleeve member 12 and the longitudinal axis X-X to a second
angular side or portion of the cam slots 72, 76 that is positioned laterally further from
the sleeve member 12 and the longitudinal axis X-X. As the coupling pins 20 are held
within at least the lateral coupling pin aperture 32 of the sleeve member 12, the
coupling pins 20 are prevented from rotation about the sleeve member 12 and the
longitudinal axis X-X, but are substantially free to translate laterally or radially within
the lateral pin aperture 32 except for friction between the exterior of the coupling pins
20 and the interior surfaces of the aperture 32 and the interior surfaces of the lateral
coupling pin aperture 34 of the driven part 30B when the coupling pins 20 are
positioned with the pin aperture 34 of the driven part 30B, as shown in FIGS. 7 and 8.
Thereby, each coupling pin 20 prevents the corresponding cam pin 74 coupled thereto
from rotation about the sleeve member 12 and the longitudinal axis X-X. The
resulting effect is that as the cam slots 72, 76 of the cam disc 16 and cam disc cover
18, respectively, rotate about the sleeve member 12 and the longitudinal axis X-X, the
cam pins 74 resist any forces tending to translate the cam pins 74 about the sleeve
member 12 and longitudinal axis X-X and force the cam slots 72, 76 to translate about
the cam pins 74, as shown in FIG. 22.
As described above, as the cam slots 72, 76 include a profile that
increases in lateral distance in the angular direction of the rotation of the cam disc 16
and cam disc cover 18 via the torsion spring 40, the cam pins 74 are forced, carried or
"ride" the cam slots 72, 76 in the lateral direction defined by the axis Y-Y of the
coupling pin aperture 32 of the sleeve member 12 andlor the axis Yl-Y1 of the
coupling pin aperture 34 of the driven part 30B only in the lateral direction. Stated
differently, as the cam slots 72, 76 rotate about the sleeve member 12 and longitudinal
axis X-X, the cam pins 74 only laterally translate in a direction dictated by the lateral
coupling pin aperture 32 of the sleeve member 12 andlor the lateral coupling pin
aperture 34 of the driven part 30B. In this way, the cam pins 74 pull the coupling
pins 20 in the lateral direction along the lateral axis Y2-Y2 of the coupling pin 20 to
translate the coupling pin 20 along the lateral axes Y-Y, Y 1-Y1 of the lateral coupling
pin apertures 32, 34 of the sleeve member 12 and the driven part 30B to a predefined
degree such that the coupling pin 20 are translated out of engagement within the
lateral coupling pin aperture 34 of the driving part 30A, as shown in the comparison
between the position of the coupling pins 20 in FIGS. 7 and 2 1 to FIGS. 8 and 22.
As noted above the, the coupling pin 20 are likely to experience loads
or forces that increase the friction between the outer surfaces of the coupling pin 20
and the inner surfaces of the lateral coupling pin apertures 32, 34 of the sleeve
member 12 and the driven part 30B. Further, as also described above, the cam pins
74 are subjected to frictional resistance while they travel within the cam slots 72, 76,
and the cam disc 16 encounters resistance as is rotated about the sleeve member 12.
These force, and any other forces on the components of the actuator decoupler 10
during decoupling of the driven part 30B, act to provide resistance to the lateral
translation of the coupling pins 20 from within the lateral coupling pin aperture 34 of
the driven part 30B by the actuator decoupler 10. The amount of preload torque of
the torsion spring 40 must therefore be sufficient to overcome such resistance to
decouple the actuator decoupler 10, and thereby the driving part 30A, from the driven
part 30B. Sufficient torque may be achieved, for example, through the characteristics
of the torsion spring itself, the amount of preload applied to the torsion spring, the
profile of the cam slots 72, 76 or a combination thereof.
Once the coupling pin 20 are translated out of engagement within the
lateral coupling pin aperture 34 of the driven part 30B, as shown in FIGS. 8 and 22,
the driven part 30B is free to translate both rotationally and longitudinally with
respect to the actuator decoupler 10. Further, if the actuator decoupler 10 is
rotationally and longitudinally fixed to the driving part 30A, the once the coupling
pins 20 are translated out of engagement within the lateral coupling pin aperture 34 of
the driven part 30B, the driven part 30B is free to translate both rotationally and
longitudinally with respect to the driving part 30A. Such longitudinal, and potentially
rotational, translation may be particularly advantageous for an actuation system in
which the driven part 30B is a component of a power screw, such as actuation system
in which the driven part 30B is a component of a power screw that provides
longitudinal forces, ultimately, to a load control surface, such as flight control surface.
More specifically, in such a configuration, if the flight control surface includes
multiple actuation systems supplying a cumulative load to translate the flight control
surface, and an actuation system in which the actuator decouple 10 is installed
experiences a jam in the power screw for example, the flight control surface is
prevented from moving (i.e., the flight control surface is "frozen" by the jammed
actuation system). In response to such a jam, the actuator decoupler 10 can disengage
the driven part 30B from the actuator decoupler 10 and the driving part 30A to allow
the power screw to freely rotate or longitudinally translate. Such free rotation and/or
longitudinally translation of the power screw, provided by the actuator decouple 10,
acts to remove the jam from the flight control surface and allows the other nonjammed
actuation systems to translate the flight control surface, and thereby
longitudinally and/or rotationally translate the power screw with respect to the
actuator decoupler 10 and the driving part 30A.
FIG. 23 shows an exemplary alternative embodiment of the actuator
decoupler generally indicated by reference numeral 210. Exemplary actuator
decoupler 2 10 is similar to the exemplary actuator decoupler 10 described above and
illustrated in FIGS. 1-1 9 and 20-22, and therefore like reference numerals preceded by
the numeral "2" are used to indicate like elements. The exemplary actuator decoupler
2 10 includes a sleeve member 2 12, an energy mechanism 240, coupling pins 220 and
locking members 250.
As shown in FIG. 23, the exemplary actuator decoupler 210 includes a
sleeve member 2 12 defining a longitudinal axis X2-X2 and configured to couple to a
driving part 230A at a driving portion 222 such that the driving part 30A applies a
torque to the sleeve member 212 to rotate the sleeve member 212 about the
longitudinal axis X2-X2. The driving part 230A may be coupled to the sleeve
member 212 such that the sleeve member 212 and the actuator decoupler 210 are
rotationally and longitudinally fixed to the driven part 30B.
The sleeve member 212 may also configured to include a driven
portion 226 configured to transfer a torque and/or longitudinal or axial force of the
driving part 230A to a driven part or mechanism 230B. In embodiments wherein the
driven part 230B is configured to rotate upon receipt of the torque of the driving part
230A, such as when the driven part 230 is a component of a power screw, the driven
part 230B may define a longitudinal axis of rotation X3-X3 that substantially aligns
with the longitudinal axis X2-X2 of the sleeve member 2 12.
As also shown in FIG. 23, the exemplar sleeve member 212 includes a
longitudinally extending aperture 228 extending from an end of the sleeve member
2 12 at the driven portion 228 of the sleeve member 2 12. The sleeve member 2 12 also
includes a laterally extending coupling pin aperture 232 defining a lateral or radial
axis Y3-Y3 extending entirely though the sleeve member 212 and the longitudinal or
axial axis X2-X2 such that the pin aperture 232 forms two diametrically opposed
openings in the outer surface of the sleeve member 2 12. The driven part 230B may
also include a laterally extending coupling pin aperture 234 defining a lateral or radial
axis Y4-Y4 extending entirely though the driven part 230 and the longitudinal or axial
axis of rotation X3-X3 such that the pin aperture 234 forms two diametrically
opposed openings in the outer surface of the driven part 230B. In such a
configuration, the driven part 230B may be received within the longitudinally
extending of aperture 228 of the driven portion 226 of the sleeve member 212 such
that the openings of the pin aperture 232 of the sleeve member 212 are aligned with
the openings of the pin aperture 234 of the driven part 230B (i.e., the apertures 232,
234 are aligned). The coupling pin aperture or apertures 234 may be alternatively
configured in any known manner without departing from the spirit and scope of the
disclosure.
In such a configuration of the sleeve member 212 and the driven part
230B, the coupling pins 220 may be translated into engagement with the pin aperture
232 of the sleeve member 212 and the pin aperture 234 of the driven part 230B such
that the driven part 230B is rotationally and longitudinally fixed or locked with
respect to the sleeve member 212 (and therefore the actuator decoupler 210) and the
driving part 230A if the driving part 230A is rotationally and longitudinally fixed or
locked with respect to the sleeve member 212, as shown in FIG. 23. The lateral
coupling pin apertures 232,234 of the sleeve member 212 and driven part 230B may
be configured such that a longitudinally extending gap of length L2 extends between
the end of the longitudinally extending aperture 228 of the driven portion 226 of the
sleeve member 212 and the end of the driven part 230B, as shown in FIG. 23. As
explained further below, such a longitudinally extending gap will allow the driven
part 230B to longitudinally translate with respect to the actuator decoupler 210 in a
selectively decoupled state. As also shown in FIG. 23, each coupling pin 220 may be
coupled to an energy mechanism 40 that is coupled to, and extends from, the housing
member 2 14 of the sleeve member 2 12.
In the illustrated embodiments of FIG. 23, the energy mechanism 240
is a cantilever member 240 extending from a housing member portion 214 of the
sleeve member 2 12, and includes a coupling pin 220 extending from a portion of the
cantilever member 240 adjacent the free end thereof. The cantilever member 240 may
be configured such that in a free or non-defected position, the coupling pin 220 is
spaced from the opening of the pin aperture 234 of the driven part 230B. The
cantilever member 240 may also be configured such that when the cantilever member
240 is deformed in a manner that the free end is translated toward the longitudinal
axis X2-X2, the coupling pin 220 is aligned and translated to a position at least
partially within the lateral pin aperture 232 of the sleeve member 212 and the lateral
pin aperture 234 of the driven part 230B to selectively couple the actuator decoupler
2 10 and the driven part 230B such that they are rotationally and longitudinally locked
or fixed with respect to one another, as depicted in FIG. 23. Further, in such a
selectively coupled state, if the driving part 230A is rotationally and longitudinally
locked or fixed with respect to the actuator decoupler 210, the driven part 230B will
also be rotationally and longitudinally locked or fixed with respect to driving part
230A.
When in the coupled state, the deformation of the cantilever member
240 such that the coupling pin 220 coupled thereto is laterally translated into
engagement within the lateral pin apertures 232, 234 of the sleeve member 212 and
driven part 230B creates a preload force in the cantilever member 240. The preload
force in the cantilever member 240 is directed in a direction substantially opposing
the direction of the deformation of the cantilever member 240. In this way, in the
selectively coupled state of the actuator decoupler 210 each cantilever member 240
includes a preload force that biases the coupling pin 220 coupled thereto in a direction
that laterally translates the coupling pin 220 out of engagement within the lateral pin
apertures 232,234 of the sleeve member 21 2 and the driven part 230B.
To selectively retain and release the preload force of each cantilever
member 240, and thereby the positioning of each coupling pin 220 within the pin
aperture 234 of the driven part 230B, the exemplary actuator decoupler 210 includes a
locking member 250 corresponding to each cantilever member 240, as illustrated in
FIG. 23. The locking member 250 may be translatably or movably coupled to the
sleeve member 212 andfor the driven part 230B. For example, in the illustrated
embodiment, each locking member 250 is longitudinally movably coupled to the
driven part 230B along the longitudinal axis X3-X3 of the driven part 230.
Each locking member 250 may include a first arm 254 extending from
the locking member 250 configured to engage a bearing member 290 positioned on
the cantilever member 240, to thereby engage the cantilever member 240. The first
arm 254 of the locking member 250 and the bearing member 290 can be configured
such that the deformed lateral position of the cantilever member 240, and therefore
the lateral position of the coupling pin 220 coupled thereto, is maintained by the
bearing member 290 and the first arm 254, as shown in FIG. 23. Specifically, in the
illustrated embodiment the preload of the cantilever member 240 is translated through
the bearing member 290 and to the first arm 254 which is configured to resist such
load. As such, each locking member 250 is configured to selectively retain the
preloaded energy of each cantilever member 240 and maintain engagement of the
coupling pin 220 coupled thereto within the pin aperture 232 of the sleeve member
212 and the pin aperture 234 of the driven part 230B in a selectively coupled state of
the actuator decoupler 210. In the illustrated embodiment, as each locking member
250 is configured to longitudinally translate, the bearing member 290 is preferably
configured to reduce or substantially eliminate the friction or other resistance between
the cantilever member 240 and the first arm 254 when the first arm 254 is laterally
translated with respect to the cantilever member 240.
To selectively decouple the driven part 230B from the actuator
decoupler 210 and, potentially, the driving part 230A, the actuator decoupler 210 can
be actuated by a secondary actuator (not shown) to release the preload of each
cantilever member 240 and laterally translate each coupling pin 220 out of
engagement within at least the pin aperture 234 of the driven part 230B. Specifically,
the secondary actuator can be responsive to a jam in the actuation system in which the
actuator decoupler 210 is installed to longitudinally translate each locking member
250, and thereby the first arm 254 of each locking member 250, a longitudinal
distance such that each first arm 254 is disengaged fiom each cantilever member 240.
When each first arm 254 is disengaged from each cantilever member
240, each cantilever member 240 is free to release its preload and thereby return to its
pre-deformed orientation. As described above, in the free or non-deflected position of
each cantilever member 240 the coupling pin 220 coupled thereto is spaced from the
pin aperture 234 of the driven part 230B. As such, each locking member 250 is
configured to translate to an unlocking position to selectively release the preloaded
energy of each cantilever member 240 to disengage the coupling pin 220 coupled
thereto from within the aperture 234 of the driven part 230B (and potentially the pin
aperture 232 of the sleeve member 212) such that the driven part 230B is free to
translate both rotationally and longitudinally with respect to the sleeve member 212
(and therefore the actuator decoupler 210) and the driving part 230A. In the
illustrated embodiment, in the decoupled state the driven part 230B is capable of
longitudinally translating away from the actuator decoupler 2 10 by translating within
the longitudinally extending aperture 228 of the driven portion 226 of the sleeve
member 212, longitudinally translating toward the actuator decoupler 210 by
translating within the longitudinally extending aperture 228 of the driven portion 226
of the sleeve member 212 a distance L2 (the longitudinal distance of the gap between
the end of the driven part 230 and the end of the longitudinally extending aperture
228), and rotating about the axis X3-X3 within the longitudinally extending aperture
228.
It is noted that that the actuator decoupler 210 may include multiple
coupling pins 220, multiple lateral pin apertures 232 in the sleeve member 212 and in
the driven part 230B, multiple energy mechanisms, and multiple locking mechanisms
250 about the longitudinal axis X2-X2. In such a configuration, the load or forces
applied to the coupling pins 220 via the driving part 230A and lor the driven part
230B through the sleeve member 212 will be proportionally shared by the coupling
pins 220. Thereby, the more couplings pins 220 (and associated components)
included in the actuator decoupler 210, the less the load or forces applied to each
coupling pin 220. However, the more couplings pins 220 (and associated
components) included in the actuator decoupler 2 10, the actuator decoupler 2 10
becomes less reliable as opportunities for failure is increased also increased.
It is to be understood that the above description is intended to be
illustrative, and not restrictive. For example, the above-described embodiments
(andlor aspects thereof) may be used in combination with each other. In addition,
many modifications may be made to adapt a particular situation or material to the
teachings of the various embodiments without departing from their scope. While the
dimensions and types of materials described herein are intended to define the
parameters of the various embodiments, they are by no means limiting and are merely
exemplary. Many other embodiments will be apparent to those of skill in the art upon
reviewing the above description. The scope of the various embodiments should,
therefore, be determined with reference to the appended claims, along with the full
scope of equivalents to which such claims are entitled. In the appended claims, the
terms "including" and "in which are used as the plain-English equivalents of the
respective terms "comprising" and "wherein." Moreover, in the following claims, the
terms "first," "second," and "third," etc. are used merely as labels, and are not
intended to impose numerical requirements on their objects. Further, the limitations
of the following claims are not written in means-plus-function format and are not
intended to be interpreted based on 35 U.S.C. 5 1 12, sixth paragraph, unless and until
such claim limitations expressly use the phrase "means for" followed by a statement
of function void of further structure. It is to be understood that not necessarily all
such objects or advantages described above may be achieved in accordance with any
particular embodiment. Thus, for example, those skilled in the art will recognize that
the systems and techniques described herein may be embodied or carried out in a
manner that achieves or optimizes one advantage or group of advantages as taught
herein without necessarily achieving other objects or advantages as may be taught or
suggested herein.
While the invention has been described in detail in connection with
only a limited number of embodiments, it should be readily understood that the
invention is not limited to such disclosed embodiments. Rather, the invention can be
modified to incorporate any number of variations, alterations, substitutions or
equivalent arrangements not heretofore described, but which are commensurate with
the spirit and scope of the invention. Additionally, while various embodiments of the
invention have been described, it is to be understood that aspects of the disclosure
may include only some of the described embodiments. Accordingly, the invention is
not to be seen as limited by the foregoing description, but is only limited by the scope
of the appended claims.
This written description uses examples to disclose the invention,
including the best mode, and also to enable any person skilled in the art to practice the
invention, including making and using any devices or systems and performing any
incorporated methods. The patentable scope of the invention is defined by the claims,
and may include other examples that occur to those skilled in the art. Such other
examples are intended to be within the scope of the claims if they have structural
elements that do not differ from the literal language of the claims, or if they include
equivalent structural elements with insubstantial differences from the literal language
of the claims.

We Claim :
1. An actuator decoupler for selectively coupling and decoupling a driven part
with a driving part of an actuation system, the actuator decoupler comprising:
a sleeve member defining a longitudinal axis and including a first portion
configured to couple to the driven part, and a second portion configured to couple to
the driving part to receive at least one of a torque about the longitudinal axis and a
force along the longitudinal axis from the driving part;
a housing member rotationally and longitudinally fixed to the sleeve member;
at least one coupling pin selectively engaged with the second portion of the
sleeve member and the driven part when the driven part is coupled to the sleeve
member such that the sleeve member and the driven part are at least one of
rotationally and longitudinally fixed to one another by the at least one coupling pin;
at least one preloaded energy mechanism coupled to the housing member and
the at least one coupling pin; and
at least one engageable locking member movably coupled to the at least one
preloaded energy mechanism and, in a locking position, selectively retaining a
preloaded energy of the at least one preloaded energy mechanism and maintaining the
engagement of the at least one coupling pin with the sleeve member and the driven
part, and, in an unlocking position, selectively releasing the preloaded energy of the at
least one preloaded energy mechanism and thereby disengaging the at least one
coupling pin from at least the driven part such that the driven part is fi-ee to translate
at least one of rotationally and longitudinally with respect to the sleeve member and
the driving part.
2. The actuator decoupler of claim 1, wherein the at least one preloaded energy
mechanism is a preloaded resilient member coupled to a cam disc that is rotatably
coupled about the sleeve member.
60
3. The actuator decoupler of claim 2, wherein the preloaded resilient member is a
preloaded torsion spring, and wherein the preloaded energy of the torsion spring is a
torque applied to the cam disc that biases the cam disc in a first rotational direction.
4. The actuator decoupler of claim 3, wherein when each coupling pin is
selectively engaged with the sleeve member and the driven part, each coupling pin is
received within an aperture of the sleeve member and an aperture of the driven part.
5. The actuator decoupler of claim 4, wherein the cam disc includes two
longitudinally spaced cam disc members, and wherein the cam disc members include
at least one pair of substantially aligned cam slots corresponding to each coupling pin,
and wherein each pair of cam slots is movably coupled about a cam pin that is
engaged to the corresponding coupling pin that is positioned between the cam disc
members.
6. The actuator decoupler of claim 5, wherein each cam slot defines a profile
that extends angularly and laterally about the longitudinal axis such that a first slot
portion of each cam slot is laterally proximate the longitudinal axis and a second slot
portion angularly spaced from the first portion and laterally distal the longitudinal
axis.
7. The actuator decoupler of claim 6, wherein each cam pin is positioned within
the first slot portion of a corresponding pair of cam slots when the at least one
engageable locking member retains the preloaded torque of the torsion spring and
maintains the engagement of the at least one coupling pin with the sleeve member and
the driven part, and wherein each cam pin is positioned within the second slot portion
of a corresponding pair of cam slots to disengage the at least one coupling pin from at
least the driven part.
8. The actuator decoupler of claim 7, wherein each cam slot is configured such
that when the at least one engageable locking member releases the preload torque of
the torsion spring the cam disc rotates in a first direction about the longitudinal axis
and such that the position of each cam pin moves with a corresponding pair of cam
slots from the first slot portion to the second slot portion.
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9. The actuator decoupler of claim 8, wherein the lateral distance between the
first slot portion and the second slot portion of each cam slot is greater than the lateral
distance of each pin in the aperture of the driven part when each cam pin is selectively
engaged with the driven part.
10. The actuator decoupler of claim 9, wherein each cam slot is configured such
that the first slot portion extends for predetermined degree of angulation about the
longitudinal axis, and wherein the lateral location of the first slot portion of the each
cam slot is constant to allow the cam disc to gain kinetic energy as it rotates in the
first direction. 11. The actuator decoupler of claim 1, wherein the at least one
engageable locking member is configured to interact with a secondary actuator that is
responsive to a jam in the actuation system, and wherein the at least one engageable
locking member includes a first arm configured to selectively engage the cam disc in
a locking position to selectively rotationally fix the cam disc to selectively retain the
preloaded torque of the torsion spring and to maintain the engagement of the at least
one coupling pin with the sleeve member and the driven part.
12. The actuator decoupler of claim 11, wherein the at least one engageable
locking member includes second and third longitudinally spaced arms configured to
receive a portion of the secondary actuator therebetween, and wherein translation of
the portion of the secondary actuator in a first longitudinal direction results in the
portion interacting with the second arm and thereby repositioning the at least one
engageable locking member from the locking position to the unlocking position to
selectively disengage the first arm from the cam disc to release the preloaded torque
of the torsion spring to disengage the at least one coupling pin from at least the driven
part.
13. The actuator decoupler of claim 12, wherein when the portion of the
secondary actuator is positioned between the second and third arms of the at least one
engageable locking member and the at least one engageable locking member is in the
locking position, the third arm is positioned on an opposing longitudinal side of the
portion of the secondary actuator as compared to the second arm to prevent the at
least one engageable locking member from repositioning from the locking position to
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the unlocking position without translation of the at least one engageable locking
member.
14. The actuator decoupler of claim 1, wherein the at least one preloaded energy
mechanism includes at least one preloaded cantilever member extending from the
housing member and defining a free end, wherein the at least one coupling pin is
provided on a portion of the at least one cantilever member adjacent the free end, and
wherein the at least one cantilever member is deformed to preload the at least one
cantilever member and position the at least one coupling pin within an aperture of the
second portion of the sleeve member and an aperture of the driven part when each
coupling pin is selectively engaged with the sleeve member and the driven part.
15. The actuator decoupler of claim 1, wherein the second portion of the sleeve
member is configured to couple to the driving part to receive at least a torque from the
driving part, and thereby rotate about the longitudinal axis, wherein the sleeve
member and the driven part are at least rotationally fixed to one another by the at least
one coupling pin when the driven part is coupled to the sleeve member, and wherein
the driven part is free to translate at least rotationally with respect to the sleeve
member and the driving part when the at least one coupling pin is disengaged from
the driven part of the sleeve member.
16. The actuator decoupler of claim 15, wherein the sleeve member and the driven
part are longitudinally fixed to one another by the at least one coupling pin when the
driven part is coupled to the sleeve member, and wherein the driven part is free to
translate longitudinally with respect to the sleeve member and the driving part when
the at least one coupling pin is disengaged from the driven part of the sleeve member.
17. The actuator decoupler of claim 1, wherein the second portion of the sleeve
member is configured to couple to the driving part to receive at least a force along the
longitudinal axis from the driving part, and thereby translate along the longitudinal
axis, wherein the sleeve member and the driven part are at least longitudinally fixed to
one another by the at least one coupling pin when the driven part is coupled to the
sleeve member, and wherein the driven part is free to translate at least longitudinally
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with respect to the sleeve member and the driving part when the at least one coupling
pin is disengaged from the driven part of the sleeve member.
18. An actuator decoupler for selectively coupling and decoupling a driven part
including an aperture with a driving part of an actuation system such that when
selectively coupled the driven part is at least rotationally fixed to the driving part and
when selectively decoupled the driven part is at least one of rotationally and
longitudinally free with respect to the driving part, the actuator decoupler including:
a sleeve member defining a longitudinal axis and an aperture and configured
to receive at least a torque via the driving part and, upon receipt thereof, to rotate
about the longitudinal axis;
a cam disc rotationally coupled about the sleeve member and including two
longitudinally spaced cam members, the cam members including at least one pair of
substantially aligned cam slots defining a cam profile;
at least one coupling pin carried within the aperture of the sleeve member, and
a pair of cam slots of the cam disc and positioned at least partially between the cam
members of the cam disc;
a housing member rotationally and longitudinally fixed to the sleeve member
and including at least one movable locking member for selectively rotationally
locking the cam disc to the housing member and, thereby, the sleeve member; and
no more than one energy mechanism coupled to the housing member and the
cam disc and configured to deform and thereby produce a preload torque to the cam
disc in a first direction upon rotation of the cam disc about the sleeve member in a
second direction that substantially opposes the first direction,
wherein the cam profile is configured such that at a second angular position of
the cam disc each cam slot, and thereby each coupling pin carried therein, is spaced
laterally further from the longitudinal axis as compared to a first angular position,
wherein when the aperture of the sleeve member is aligned with the aperture
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of the driven part, the cam disc can be rotated about the sleeve member in the second
direction to the first angular position and selectively locked by the locking mechanism
to preload the torsion spring and bias the cam disc in the first direction, and to
position each coupling pin at least partially within the aperture of the driven part to
selectively couple the driven part with the driving part via the actuator decoupler, and
wherein the locking member is configured to be translatable by a secondary
actuator to disengage from the cam disc and release the preload torque of the energy
mechanism and thereby rotate the cam disc in the first direction to the second angular
position to laterally translate each coupling pin away from the longitudinal axis such
that each coupling pin is removed from the aperture of the driven part to selectively
decouple the driven part with the driving part via the actuator decoupler.
19. The actuator decoupler of claim 18, wherein the at least one coupling pin
includes at least one cam pin member, and the at least one cam pin member is carried
within a pair of cam slots.
20. The actuator decoupler of claim 18, wherein the cam members include an even
number of pairs of substantially aligned cam slots symmetrically disposed about the
longitudinal axis, wherein a coupling pin is carried within each pair of cam slots and
the aperture of the sleeve member, and wherein the housing member includes at least
two locking members symmetrically disposed about the longitudinal axis.
21. The actuator decoupler of claim 18, wherein the cam disc includes slots about
the periphery of at least one cam member, wherein the at least one locking member
includes a first arm including a protrusion configured to engage a slot of the cam disc,
and wherein the at least one locking member further includes second and third arms
longitudinally spaced from one another and configured to receive a secondary
actuator therebetween.
22. The actuator decoupler of claim 18, wherein when the driving part and the
driven part are selectively decoupled, the driven part is at least rotationally and
longitudinally free to translate with respect to the driving part.
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23. An actuator decoupler for selectively coupling to an actuation system such that
at least a first component of the actuation system is at least rotationally fixed to the
actuator decoupler when the actuation system is functioning properly, and for
selectively decoupling from at least the first component when a jam occurs in the
actuation system such that the first component is capable of rotationally and
longitudinally translating with respect to the actuator decoupler, the actuator
decoupler including:
a sleeve member configured to engage the first component of the actuation
system such that at least one aperture of the sleeve member is aligned with at least one
aperture of the first component;
at least one coupling pin configured to translate into, and out of, engagement
within the at least one aperture of the sleeve member and the at least one aperture of
the first component when the first component is engaged with the sleeve member to
selectively couple the actuator decoupler to the first component to at least rotationally
fix at least the first component of the actuation system to the actuator decoupler;
a biasing member configured to bias the at least one coupling pin out of
engagement within the at least one aperture of the first component when the actuator
decoupler is selectively coupled to the actuation system; and
a locking member selectively preventing the biasing member from translating
the at least one coupling pin out of engagement within the at least one aperture of the
first component when the actuator decoupler is coupled to the actuation system and
the actuation system is properly functioning, and selectively releasing the biasing
member to translate the at least one coupling pin out of engagement within the at least
one aperture of the first component when the actuator decoupler is coupled to the
actuation system and a jam occurs in the actuation system to decouple the first
component from the actuator decoupler such that at least the first component is
capable of rotationally and longitudinally translating with respect to the actuator
decoupler.
24. The actuator decoupler of claim 23, wherein the locking member is configured
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to be responsive to longitudinal movement of a secondary actuator to translate
between a first orientation in which the locking member prevents the biasing member
from translating the at least one coupling pin and a second orientation in which the
biasing member biases the at least one coupling pin and, in response thereto,
translates the at least one coupling pin, and wherein the locking member is configured
such that translation of the locking member between the first orientation and the
second orientation is prevented in any manner other than longitudinal translation of
the secondary actuator.