A two-way overrunning clutch is automatically conditioned for operation in either direction of rotation. A plurality of spaced drag springs are in frictional contact with the clutch housing so as to provide balanced radial drag forces on the wedging elements of the clutch, thereby biasing the clutch toward an engaged position thereof. This frictional contact with the clutch housing is reduced by balanced dynamic friction forces developed upon rotation of the clutch.

BACKGROUND OF THE INVENTION 
This invention relates generally to clutch mechanisms. In particular, it 
relates to clutches of the two-way overrunning type. 
Known clutch devices of this type generally provide a pair of spaced clutch 
races and a plurality of wedging elements supported by a cage intermediate 
the races. The wedging elements are rotationally displaceable relative to 
the races, and are movable into and out of wedging engagement therewith. 
Such a clutch device is disclosed in U.S. Pat. No. 3,055,471 wherein drag 
shoes are in frictional contact with the clutch housing, which drag shoes 
are connected with the cage in such a manner as to bias the wedging 
elements. Resilient means of some sort is provided for biasing the drag 
shoes toward frictional contact with the clutch housing. However, no 
provision is made for controlled reduction of the force of this frictional 
contact under dynamic conditions, or for controlled increase under static 
conditions. 
Other known clutch devices of this type include torsion springs wrapped 
around the clutch housing or an element associated therewith to establish 
the frictional contact which serves to bias the wedging elements. Such a 
clutch device is disclosed in U.S. Pat. No. 3,380,563 wherein a torsion 
spring provides frictional contact with the clutch housing in order to 
bias a system of rollers. Upon rotation, the cage picks up a portion of 
the torsion spring and spreads it so as to reduce the force of this 
frictional contact. However, the arrangement provides for a single 
reaction point which is neither balanced nor centered. This creates the 
possibility of cocking the roller cage, resulting in undesirable binding 
of the rollers. 
SUMMARY OF THE INVENTION 
This invention is directed in brief to an improved two-way overrunning 
clutch mechanism. The clutch includes a pair of spaced elements defining 
clutch races and a clutch cage supporting a plurality of rollers between 
the races. The rollers are displaceable relative to the races into and out 
of wedging engagement therewith for effecting clutch engagement and 
disengagement. 
The cage is biased toward clutch engagement in an improved manner. A 
plurality of spaced spring clips are in engagement with the cage and in 
frictional contact with the clutch housing so as to establish balanced 
pre-load static friction forces resulting in frictional engagement with 
the clutch housing. In operation, each spring clip is picked up at a 
reaction point spaced from its point of frictional contact with the clutch 
housing. Friction generated upon rotation of the clutch results in a 
moment tending to twist each spring clip about its respective reaction 
point. This moment tends to reduce the friction force developed by each 
spring clip. As a result, the force of frictional contact of the spring 
clips with the clutch housing is significantly lower under dynamic 
conditions than under static conditions.

While this invention is susceptible of embodiment in many different forms, 
there is shown in the drawing and will herein be described in detail a 
preferred embodiment with the understanding that the present disclosure is 
to be considered as an exemplification of the principles of the invention 
and is not intended to limit the invention to this embodiment. 
DESCRIPTION OF THE PREFERRED EMBODIMENT 
Referring now to the drawing in greater detail, there is shown generally a 
two-way overrunning clutch mechanism 10. It is contemplated that in one of 
its applications, clutch 10 may be incorporated in a torque transfer case 
associated with a four-wheel drive vehicle. Such a torque transfer case 
would be suitable for transmitting torque from a prime mover through a 
plurality of drive axle assemblies to drive front and rear pairs of 
traction wheels. 
Clutch 10 is supported in a housing 12 which may be the housing of an 
associated torque transfer case. Housing 12 supports a pair of spaced 
bearings 14 and 16. A first shaft 18 is journalled in bearing 14 for 
rotation in housing 12. Shaft 18 may be driven by a prime mover and 
connected with a propeller shaft for driving the rear axle of a four-wheel 
drive vehicle. A cam 20 is splined to shaft 18 for rotation therewith. Cam 
20 defines a plurality of flats or ramp surfaces 22 which serve as the 
inner race of clutch 10. A second shaft 24 is journalled in bearing 16 for 
rotation in housing 12. Shaft 24 may be connected with a propeller shaft 
for driving the front axle of a four-wheel drive vehicle. Shaft 24 defines 
an upstanding flange 26 and an annular extension 28. Extension 28 defines 
an inner cylindrical surface 30 which serves as the outer race of clutch 
10. 
An annular cage 32 supports a plurality of wedging elements 34, one of 
which is associated with each flat 22 of cam 20. In one form of the 
invention, wedging elements 34 are rollers and clutch 10 is a roller 
clutch. Cage 32 defines a plurality of outwardly extending fingers 36. As 
best shown in FIGS. 1 and 3, a drive ring 38 is supported by fingers 36 
for rotation therewith. Ring 38 defines a plurality of annularly spaced 
lugs 40 around its inner perimeter. Lugs 40 preferably are formed from a 
low friction material. A plurality of spring clips 42 are in spaced 
relationship within the annular configuration of ring 38. Each spring clip 
42 is associated with a lug 40 of ring 38, and defines a pair of end tabs 
44 and 46 spaced slightly further apart than the length of its associated 
lug 40. This, in effect, there is a lost motion connection therebetween. 
A sleeve 48 is press fit in housing 12 so as to be secured thereto. In one 
form of the invention, housing 12 may be formed from aluminum and sleeve 
48 from steel. Each spring clip 42 is in frictional contact with sleeve 48 
and is pre-loaded such that a friction force F is developed which acts on 
sleeve 48. In the schematic diagram of FIG. 5, it may be considered that 
each force F acts through a single friction point on sleeve 48. It should 
be understood that each spring clip 42 develops a friction force F and 
that these forces are balanced around sleeve 48. 
In association with a transfer case for use in a four-wheel drive vehicle, 
for example, shaft 18 would be connected with the rear axle and shaft 24 
with the front axle. Power would be directed to shaft 18 and the rear 
axle. Shaft 24 would rotate slightly faster than shaft 18 when the vehicle 
is turning, since the front wheels travel through a larger turning radius 
than do the rear wheels. If desired, means could be provided for causing 
shaft 24 normally to rotate slightly faster than shaft 18. Cam 20 rotates 
with shaft 18, and extension 28 with shaft 24. Thus, outer race 30 
normally could overrun inner race 22. 
In operation, cage 32 is rotated and fingers 36 carry ring 38. Assuming, 
for example, counterclockwise rotation of ring 38 as shown in FIG. 3, lugs 
40 abut tabs 46 of spring clips 42 and carry spring clips 42 therewith in 
the counterclockwise direction. Each lug 40 abuts a spring clip 42 at a 
reaction point, as shown in FIG. 5. Thus, there is a reaction point 
associated with each friction point, and they are spaced equally around 
the inner periphery of ring 38. Due to the frictional contact of clips 42 
with sleeve 48, which is in effect frictional contact with housing 12, 
balanced radial forces are developed which result in a relative drag 
effect on cage 32. This relative drag effect is developed without any 
axial forces acting on cage 32, and thus there is no tendency for rollers 
34 to bind. 
The drag effect on cage 32 tends to bias rollers 34 toward a wedging 
position between inner race 22 and outer race 30, thus tending to engage 
clutch 10. The slight overrun of extension 28 relative to cam 20 tends to 
overcome the effect of this bias by developing a force which acts on 
rollers 34 such that they tend to be biased away from engagement, toward 
the freewheel position of clutch 10. Thus, relative rotation between 
extension 28 and cam 20 prevents engagement of clutch 10. 
When this relative rotation approaches zero, the drag effect on cage 32 
causes rollers 34 to wedge between cam 20 and extension 28. When this 
takes place, clutch 10 will be engaged and torque will be transferred to 
shaft 24. 
It is desirable that the friction force F be at a maximum when the 
mechanism is at rest or when it is reversing direction. It is also 
desirable that the friction force F be diminished under dynamic conditions 
when the mechanism is rotating in either direction. This is accomplished 
by the lost motion relationship between each lug 40 and tabs 44 and 46 of 
its associated spring clip 42. When ring 38 is at rest, such as, for 
example, during the slight interval when an associated vehicle is shifted 
from forward to reverse or vice-versa, the force F exerted by spring clips 
42 on sleeve 48 is, in effect, static friction acting through the friction 
point. As ring 38 begins to rotate, each lug 40 abuts a spring clip 42 at 
the reaction point and begins to drive spring clip 42. As a result, 
another friction force F.sub.f is developed. This force F.sub.f acting 
through the distance Y, the radial distance between the friction point and 
the reaction point, develops a moment which acts about the reaction point 
(clockwise in FIG. 5). The force F acting through the friction point under 
dynamic conditions thus is reduced. Force F under dynamic conditions would 
be equal to force F under static conditions minus F.sub.f (Y)/(L) cosine 
A, where L is the distance between the reaction and friction points and A 
is the angle formed by this line and the tangent to sleeve 48 through the 
friction point. As F.sub.f, L, Y and cosine A are finite and positive, the 
result is that force F under dynamic conditions is less that it would be 
under static conditions. 
As advantage of the lost motion relationship between lug 40 and spring clip 
42 is that upon reversal of the direction of rotation such as, for 
example, from counterclockwise to clockwise as shown in FIG. 2, there 
would be sufficient time for rollers 34 to be shifted across cam 20 from 
one side of flats 22, through the central position shown, to the other 
side of flats 22. But for this relationship, upon reversal of direction, 
extension 28 conceivably could keep rollers 34 from shifting across cam 
20. This would result in undesirable lockup of clutch 10. 
Of course, initial rotation of ring 38 in the clockwise direction would 
cause lugs 40 to abut and drive tabs 44 of spring clips 42, and the 
biasing of clutch 10 would be the same. 
Turning to the configuration of FIG. 4, there is shown an alternative 
arrangement whereby a ring 38a is driven by fingers 36 of cage 32. Ring 
38a has outwardly extending lugs 40a which support spring clips 42 in the 
same manner as do inwardly extending lugs 40 of ring 38. A sleeve 48a as 
press fit in the interior of a channel (not shown) in housing 12. Spring 
clips 42 contact the inner surface of sleeve 48a. The operation of clutch 
10 is the same regardless of which configuration is used. 
Cage 32 is frictionally biased to ground in such a manner as to develop 
controlled, balanced radial drag forces but no axial biasing forces which 
would cause binding of the wedging elements. The frictional bias developed 
is a static frictional contact force, which force is reduced under dynamic 
conditions. 
Although one use for the clutch is in association with a transfer case for 
a four-wheel drive vehicle, it should be understood that this is not 
limiting, and its use in other environments is contemplated. Also, it 
should be understood that while one preferred embodiment of the invention 
has been shown and described, this is illustrative and may be modified by 
those skilled in the art without departing from the scope of the 
invention, which is to be limited only by the claims herein.