Title of Invention

A CLUTCH ASSEMBLY WITH SELECTIVELY VARIABLE MODES OF OPERATION

Abstract A clutch assembly includes a first race and a second race that is selectively rotatable with respect to the first race about an axis of rotation. A plurality of rockers is operatively connected to the first race and spring biased into engagement with the second race to transmit torque between the first and second races. A member is selectively translatable between first and second positions to control the ability of the rockers to transmit torque between the first and second rockers, and thereby to control the ability of the races to rotate relative to one another.
Full Text GP-308908-PTT-DLT
1
ROCKER CLUTCH ASSEMBLY
TECHNICAL FIELD
[0001] This invention relates to rocker clutches having selectively variable modes
of operation.
BACKGROUND OF THE INVENTION
[0002] The prior art includes one-way clutches that are configured to prevent
rotation of a first member relative to a second member in one direction, and to permit
rotation of the first member relative to the second member in another direction.
Vehicle powertrains may employ one-way clutches. For example, a one-way clutch
may be implemented to transfer torque from an engine to the transmission, and to
interrupt the transfer of reverse torque from the transmission to the engine. Prior art
one-way clutches include roller-type clutches and sprag-type clutches.
SUMMARY OF THE INVENTION
[0003] A clutch assembly includes a first race defining a plurality of pockets, a
second race being selectively rotatable with respect to the first race about an axis and
defining a plurality of teeth, a plurality of springs, and a plurality rockers. Each of the
rockers is at least partially positioned within a respective pocket, and is biased by one
of the springs into engagement with the teeth.
[0004] A selector member is selectively axially translatable between a first
position and a second position. In the first position, the selector member permits
engagement of at least one of the rockers with the teeth. In the second position, the
selector member prevents engagement of the at least one of die rockers with the teeth.
Accordingly, the ability of the first rocker to transmit torque between the first and
second races is controllable by moving the selector member.
[0005] The clutch assembly provided herein enables high packaging efficiency
since the selectively variable torque carrying capacity is accomplished with a single pair

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of races. Furthermore, the axial translation of the selector member facilitates
implementation of the clutch assembly into existing systems that may already have an
axial actuator in place, such as a clutch piston.
[0006] The above features and advantages and other features and advantages of
the present invention are readily apparent from the following detailed description of the
best modes for carrying out the invention when taken in connection with the
accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
[0007] FIGURE 1 is an exploded perspective view of a rocker clutch assembly
including a selector ring, an inner race, an outer race, and first and second pluralities of
rockers;
[0008] FIGURE 2a is a schematic cross-sectional view, taken along a plane that is
perpendicular to an axis of rotation, of the clutch assembly of Figure 1 with the selector
ring in a first position;
[0009] FIGURE 2b is a schematic, cross-sectional depiction of two of the rockers
and the selector ring in the first position;
[0010] FIGURE 2c is a schematic cross-sectional side view of one of the first
plurality of rockers in a first interaction with the outer race;
[0011] FIGURE 2d is a schematic cross-sectional side view of the rocker of
Figure 2c in a second interaction with the outer race;
[0012] FIGURE 2e is a schematic cross-sectional side view of one of the second
plurality of rockers interacting with the outer race;
[0013] FIGURE 3a is a schematic, cross-sectional view, taken along a plane that
is perpendicular to the axis of rotation, of the clutch assembly of Figure 1 with the
selector ring in a second position;
[0014] FIGURE 3b is a schematic depiction of the two rockers of Figure 2b with
the selector ring in the second position;
[0015] FIGURE 3c is a schematic cross-sectional side view of one of the second
plurality of rockers in a retracted position; and

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[0016] FIGURE 4 is a schematic side view of a portion of the clutch assembly
operatively connected to an actuator that is configured to selectively move the selector
ring between the first and second positions.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0017] Referring to Figure 1, a rocker clutch assembly 10 is schematically
depicted. The rocker clutch assembly 10 may be used, for example, to control the torque
transfer in an automatic transmission, a manual transmission, a hybrid vehicle, a dual
clutch transmission, a transfer case, or an engine accessory drive. The rocker clutch
assembly 10 includes a generally annular inner race 12 and a generally annular outer race
14. The inner race 12 and the outer race 14 are coaxially positioned about an axis (shown
at 16 in Figure 2a). A bushing 18 is preferably provided to pilot the outer race 14 as it
rotates relative to the inner race 12. A selector member, such as selector ring 20, is
positioned radially between the inner race 12 and the outer race 14. The rocker clutch
assembly 10 also includes an apply plate 22 that is selectively translatable in an axial
direction in order to cause axial translation of the selector ring 20.
[0018] The inner race 12 defines an inner surface 24 that is preferably splined to
facilitate attachment to a shaft member (not shown). The outer surface 26 of the inner
race 12 defines a plurality of pockets 28. The clutch assemly 10 also includes a first
plurality of rockers 30A and a second plurality of rockers 30B. Rockers 30A, 30B are
identical to each other except for their orientation. Each pocket 28 includes a respective
recess (shown at 32 in Figure 2a) configured to retain a respective spring (shown at 34 in
Figure 2a).
[0019] The outer race 14 defines an outer surface 36 that is preferably splined to
facilitate attachment to a shaft member (not shown). The inner surface 38 of the outer
race 14 defines a plurality of teeth 40. The teeth 40 define notches 41 therebetween.
[0020] The selector ring 20 defines a plurality of rectangular windows 42 and a
plurality of L-shaped windows 44. Each of the windows 44 includes a narrow portion 46
and a wide portion 48. More specifically, the narrow portions 46 have a smaller axial
dimension than the wide portions 48. The selector ring 20 is characterized by portions

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50. Each of portions 50 partially define a respective narrow portion 46 and a respective
wide portion 58.
[0021] The apply plate 22 has a radially outer surface 52 defining a plurality of
teeth 54. The teeth 54 are configured to engage a complementary feature on an external
member (not shown) such that the apply plate 22 is prevented from rotating about the
axis. The apply plate 22 is operatively connected to the selector ring 20 such that axial
movement of the plate 22 results in axial movement of the ring 20.
[0022] Referring to Figure 2a, wherein like reference numbers refer to like
components from Figure 1, the outer race 14 is disposed concentrically around the inner
race 12, such that the outer surface 26 of the inner race 12 is in juxtaposition with the
inner surface 38 of the outer race 14, and such that the pockets 28 are open in the
direction of the teeth 40. Each of the first plurality of rockers 30A and each of the second
plurality of rockers 30B is partially disposed within a respective one of the pockets 28,
and is biased by a respective spring 34 into engagement with the teeth 40. The outer race
14 is selectively rotatable with respect to the inner race 12 about axis 16.
[0023] Referring to Figures 2a and 2b, the selector ring 20 is disposed radially
between the inner race 12 and the outer race 14, and is depicted in a first position in
which each window 42 is positioned such that a respective one of the first plurality of
rockers 30A is extendable radially therethrough. When the ring 20 is in the first position,
each wide portion 48 of windows 44 is positioned such that a respective one of the first
plurality of rockers 30A is extendable radially therethrough. When the ring 20 is in the
first position, each narrow portion 46 of the windows 44 is positioned such that a
respective one of the second plurality of rockers 30B is extendable radially therethrough.
Each of the first plurality of rockers 30A is extendable through one of the windows 42 or
one of the wide portions 48. Each of the second plurality of rockers 30B is extendable
through one of the narrow portions 46.
[0024] Referring to Figure 2c, wherein like reference numbers refer to like
components from Figures 1 and 2a-b, a rocker 30A is depicted interacting with the inner
race 12 and the outer race 14; the rocker 30A depicted in Figure 2c is representative of all
of the first plurality of rockers 30A. Rocker 30A includes a body portion 70 and an

GP-308908-PTT-DLT
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engagement arm or pawl 72 protruding from the body portion 70. According to the
preferred embodiment, the engagement arm 72 defines generally opposing first and
second surfaces 76, 78, and a terminal end surface 80. Each pocket 28 includes a recess
32 adapted to retain a spring 34. Each spring 34 extends from a respective recess 32 and
engages a respective one of rockers 30A such that a portion of the rocker is biased into
engagement with the teeth 40 of the outer race 14.
[0025] More specifically, spring 34 contacts surface 78, urging the engagement
arm 72 radially outward toward the outer race 14 so that the engagement arm 72 engages
the teeth 40. In the context of the present application, an engagement arm 72, or a rocker
30A, 30B, engages teeth when a portion of the rocker or engagement arm is at a radial
distance from the axis (shown at 16 in Figure 2a) sufficient to contact one of the teeth 40.
In the embodiment depicted, spring 34 biases the engagement arm 72 sufficiently radially
outward such that, absent a counteracting force, the engagement arm 72 extends into one
of the notches 41 defined between the teeth 40.
[0026] Each rocker 30A is configured to permit rotation of the outer race 14 with
respect to the inner race 12 about the axis 16 in a first direction and to prevent rotation of
the outer race 14 with respect to the inner race 12 about the axis 16 in a second direction
when the rocker 30A engages the teeth 40 of the outer race 14. In other words, rockers
30A are configured not to transmit torque between the inner and outer races 12, 14 in the
first direction, and to transmit torque between the races 12, 14 in the second direction.
[0027] More specifically, the rocker 30A is configured such that, if the outer race
14 rotates counterclockwise relative to the inner race 12, one of the teeth 40 contacts
surface 76 of the rocker 30A. The orientation of the surface 76, and the angle at which
the tooth 40 contacts the surface 76, is such that the tooth 40 applies a force on the
surface 76 that rotates the engagement arm 72 of the rocker 30A about a pivot axis 74
away from the outer race 14, compressing the spring 34. The rotation of the engagement
arm 72 permits the tooth 40 to slide across surface 76 during relative rotation of the outer
race with respect to the inner race in the counterclockwise direction, and therefore
rockers 30A do not prevent rotation of the outer race with respect to the inner race in the
counterclockwise direction. Pivot axis 74 is parallel to axis 16.

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[0028] Referring to Figure 2d, wherein like reference numbers refer to like
components from Figures l-2c, rocker 30A is depicted with the engagement arm 72
extending radially outward into notch 41. If the outer race 14 rotates clockwise with
respect to the inner race 12, a tooth 40 contacts surface 80 of the engagement arm 72.
The orientation of the surface 80, and the angle at which the tooth 40 contacts the surface
80, is such that the tooth 40 applies a force on the surface 80, and surface 80 transmits a
corresponding reaction force on the tooth, that prevents the outer race 14 from rotating
with respect to the inner race 12 in the clockwise direction.
[0029] According to the preferred embodiment, the body portion 70 of each
rocker 30A defines surfaces 90, 92 and 94. Surfaces 90 and 92 are both circular
cylindrical surfaces whose arcs are concentric with the pivot center 74. The surfaces 90.
92 are configured to guide rotation or pivoting of the rocker 30A about the pivot center
74 and limit that pivoting to one degree of freedom.
[0030] When surface 80 is in contact with a tooth 40, as shown in Figure 2d, a
reaction force is applied to surface 92 from the inner race 12, and there is preferably no
reaction force applied to surface 90. Because the center of surface 92 is preferably
located at the pivot center 74, this reaction force is distributed along surface 92 and
produces no torque tending to pivot the rocker 30A about the pivot center 74. The
surface 94 is configured to limit the rotation or pivoting of the rocker 30A in either the
clockwise or counter clockwise direction. A center of mass 96 of the rocker 30A can be
located in relation to the pivot center 74 such that centrifugal force tends either to engage
or to disengage the rocker 30A, depending on whether the rocker 30A is mounted to the
inner race 12 or the outer race 14.
[0031] Referring to Figure 2e, wherein like reference numbers refer to like
components from Figures 1 -2d, rockers 30B are substantially identical to rockers 30A
except for their orientation with respect to the inner and outer races 12, 14. More
specifically, rockers 30B are oriented such that each rocker 30B permits rotation of the
outer race 14 with respect to the inner race 12 in the second direction and prevents
rotation of the outer race 14 with respect to the inner race 12 in the first direction when
the rocker 30B engages the teeth 40 of the outer race 14. In other words, rockers 30B are

GP-308908-PTT-DLT
7
configured not to transmit torque between the inner and outer races 12, 14 in the first
direction, and to transmit torque between the races 12, 14 in the second direction when
the rockers 30B are engaged with the teeth 40.
[0032] Spring 34 biases the engagement arm 72 of rocker 30B into engagement
with the teeth 40 and into notch 41. If the outer race 14 rotates counterclockwise with
respect to the inner race 12, one of the teeth 40 contacts surface 80 of the rocker 30B, and
rotation of the outer race 14 in the counterclockwise direction with respect to the inner
race 12 is prevented in the same manner that rockers 30A prevent rotation of the outer
race 14 in the clockwise direction. If the outer race 14 rotates clockwise with respect to
the inner race 12, the teeth 40 will contact surface 76 of the rocker 30B such that the
rocker 30B pivots and permits the teeth 40 to slide acress surface 76, thereby permitting
rotation of the outer race 14 in the clockwise direction with respect to the inner race 12.
[0033] Referring to Figures 3a and 3b, wherein like reference numbers refer to
like components from Figures l-2e, the selector ring 20 is selectively translatable in the
axial direction from the first position (shown in Figures 2a and 2b) to a second position
shown in Figures 3a and 3b. Windows 42 and wide portions 48 are sufficiently wide in
the axial direction such that rockers 30A extend therethrough when the ring 20 is in the
second position. Accordingly, the selector ring 20 permits rockers 30A to engage the
teeth 40 of the outer ring 14 in both the first and second positions, and therefore the
function of the rockers 30A is identical when the ring is in the first and second positions.
However, when the ring is in the second position, portions 50 of the ring 20 are
positioned radially between each of rockers 30B and the outer race 14 to prevent
engagement of the rockers 30B with the teeth 40 of the outer race 14.
[0034] More specifically, and with reference to Figure 3c, movement of the ring
20 from the first to the second position causes portion 50 to contact surface 76 and
counteract the bias of spring 34, thereby to pivot the rocker 30B out of engagement with
the teeth 40 of the outer race 14. In other words, the ring 20 in the second position
retains the rockers 30B in a retracted position in which no part of the rockers 30B extends
sufficiently radially to contact or otherwise interact with the teeth 40 or the notches 41.

GP-308908-PTT-DLT
8
[0035] Accordingly, with the selector ring 20 in the second position, the rockers
30A prevent the rotation of the outer race 14 in the clockwise direction, and rockers
30B do not engage the teeth, thereby allowing the outer race to rotate in the
counterclockwise direction relative to the inner race 12. The ability of the clutch
assembly to convey torque between the first and second races in one direction is
selectively variable by translating the selector member. Movement of the selector
member 20 from the first position to the second position causes the torque carrying
ability of the clutch assembly 10 to change from dual-directional to single-directional.
[0036] Other selector ring configurations may be employed within the scope of
the claimed invention to vary the engagement of rockers 30A, 30B. For example, the
windows of the selector ring may be configured such that axial translation of the ring
between various positions results causes the clutch assembly 10 to lock-up in either
direction (i.e., clockwise or counter clockwise), lock-up in both directions, or over-run in
both directions within the scope of the claimed invention.
[0037] The illustrations and descriptions have demonstrated the rocker elements
30A, 30B retained by and located at least partially within the inner race 12.
Alternatively, and within the scope of the claimed invention, the rocker elements 30A,
30B may be retained in pockets formed by the outer race 14 and engage teeth defined by
the inner race 12.
[0038] Referring to Figure 4, wherein like reference numbers refer to like
components from Figures 1-3, the clutch assembly 10 is schematically depicted installed
in a vehicle 102 as part of a powertrain component 106, which may, for example, be a
dual clutch transmission (DCT), hybrid powertrain, manual transmission, automatic
transmission, engine accessory drive, etc. The inner race 12 is mounted with respect to a
stationary member 112, such as a transmission housing, chassis frame, or vehicle body, to
prevent rotation of the inner race 12 with respect to the stationary member 112. The
outer race 14 is mounted with respect to a rotatable member for rotation therewith. In the
embodiment depicted, the rotatable member is a member of a planetary gearset 1 16.
[0039] An actuator 124, such as a hydraulically-actuated piston, solenoid, etc., is
mounted with respect to the stationary member 112 and is configured to selectively

GP-308908-PTT-DLT
9
translate the selector ring 20 relative to the stationary member 112 in the axial direction
between the first and second positions. The actuator 124 is operatively connected to the
ring 20 via the apply plate (shown at 22 in Figure 1). A spring 128 operatively
interconnects the stationary member 112 and the selector ring 20 to bias the selector ring
in the first position. The ring 20 is prevented from rotating with respect to the stationary
member 112, and therefore with respect to the inner race 12, such as by its connection to
the apply plate (not shown in Figure 4), so that the windows of the ring 20 maintain their
alignment with a respective rocker. The apply plate is mounted with respect to the
stationary member, such as via the teeth (shown at 54 in Figure 1) so that the apply plate
is axially translatable, but not rotatable with respect to the stationary member 112 and the
inner race 12.
[0040] It should be noted that, if the actuator 124 is characterized by insufficient
linear travel to move the selector ring 20 between the first and second positions, various
linear travel amplifiers may be employed. In an exemplary embodiment, radially-
oriented levers may interconnect the actuator and the ring. Alternatively, in place of a
lever, a single slotted disk may be employed. The disk may also serve as a piston return
spring if formed of an elastic material.
[0041] While the best modes for carrying out the invention have been described
in detail, those familiar with the art to which this invention relates will recognize various
alternative designs and embodiments for practicing the invention within the scope of the
appended claims.

GP-308908-PTT-DLT
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CLAIMS
1. A clutch assembly comprising:
a first race defining a plurality of pockets;
a second race being selectively rotatable with respect to the first race about
an axis and defining a plurality of teeth;
a plurality of springs;
a plurality of rockers, each of said rockers being at least partially
positioned within respective ones of said pockets, and being biased by a respective one of
said springs into engagement with said teeth; and
a selector member being selectively axially translatable between a first
position in which the member permits engagement of at least one of the rockers with said
teeth, and a second position in which the member prevents engagement of said at least
one of the rockers with said teeth.
2. The clutch assembly of claim 1, wherein the selector member is
generally ring shaped, and is at least partially radially disposed between the first and
second races.
3. The clutch assembly of claim 1, wherein said plurality of rockers
includes a first rocker and a second rocker; said first rocker being configured such that
engagement of the first rocker with said teeth prevents rotation of the second race with
respect to the first race in a first direction, and said second rocker being configured such
that engagement of the second rocker with said teeth prevents rotation of the second race
with respect to the first race in a second direction.
4. The clutch assembly of claim 3, wherein the selector member
permits engagement of the first rocker with the teeth when in the first and second
positions; and wherein the selector member permits engagement of the second rocker

GP-308908-PTT-DLT
11
with the teeth when in the first position and prevents engagement of the second rocker
with the teeth when in the second position.
5. The clutch assembly of claim 4, wherein the selector member
defines an aperture characterized by a wide portion through which said first rocker
extends when the member is in the first and second positions, and a respective narrow
portion through which said second rocker extends when the member is in the first
position.
6. The clutch assembly of claim 1, further comprising an actuator
operatively connected to the selector member and configured to selectively move the
selector member between the first and second positions.
7. A clutch assembly comprising:
a first race; a second race being selectively rotatable with respect to the
first race about an axis of rotation; one of said first race and said second race defining a
plurality of pockets and the other of said first race and said second race defining a
plurality of teeth;
a plurality of springs;
a first plurality of rockers, each of said first plurality of rockers being at
least partially positioned within a respective one of said pockets, and each of said first
plurality of rockers being biased by a respective one of said springs into engagement with
said teeth to prevent rotation of the second race with respect to the first race in a first
direction and permit rotation of the second race with respect to the first race in second
direction;
a second plurality of rockers, each of said second plurality of rockers
being at least partially positioned within a respective one of said pockets, and each of said
second plurality of rockers being biased by a respective one of said springs into
engagement with said teeth to prevent rotation of the second race with respect to the first

GP-308908-PTT-DLT
12
race in the second direction and permit rotation of the second race with respect to the first
race in the first direction; and
a member being configured for linear translation between a first position
in which the member permits the engagement of the first plurality of rockers with said
teeth and a second position in which the member prevents the engagement of the first
plurality of rockers with said teeth.
8. The clutch assembly of claim 7, wherein said first race, said
second race, said first plurality of rockers, and said second plurality of rockers are
coplanar in a plane that is perpendicular to the axis of rotation.
9. The clutch assembly of claim 7, wherein said pockets, said teeth,
and said first and second pluralities of rockers are coplanar in a plane that is
perpendicular to the axis of rotation.
10. The clutch assembly of claim 7, wherein said member is
selectively translatable axially between the first and second positions.
11. The clutch assembly of claim 7, wherein the member permits
engagement of the second plurality of rockers with said teeth in the first and second
positions.
12. The clutch assembly of claim 7, wherein the member is annular.
13. The clutch assembly of claim 7, further comprising an actuator
operatively connected to the member.
14. The clutch assembly of claim 7, wherein the second race is
concentrically disposed around the first race.

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13
15. A clutch assembly comprising:
an inner race; an outer race being concentrically disposed around the inner
race and being selectively rotatable with respect to the inner race about an axis of
rotation; one of said inner race and said outer race defining a plurality of pockets and the
other of said inner race and said outer race defining a plurality of teeth;
a plurality of springs;
a first plurality of rockers, each of said first plurality of rockers being at
least partially positioned within a respective one of said pockets, and each of said first
plurality of rockers being biased by a respective one of said springs into engagement with
said teeth to prevent rotation of the outer race with respect to the inner race in a first
direction and permit rotation of the outer race with respect to the inner race in second
direction;
a second plurality of rockers, each of said second plurality of rockers
being at least partially positioned within a respective one of said pockets, and each of said
second plurality of rockers being biased by a respective one of said springs into
engagement with said teeth to prevent rotation of the outer race with respect to the inner
race in the second direction and permit rotation of the outer race with respect to the inner
race in the first direction;
said outer race, said inner race, said first plurality of rockers, and said
second plurality of rockers being coplanar in a plane that is perpendicular to said axis of
rotation; and
a generally annular member being disposed radially between said inner
ring and said outer ring and being axially translatable to control the engagement of said
first plurality of rockers with said teeth.

A clutch assembly includes a first race and a second race that is selectively
rotatable with respect to the first race about an axis of rotation. A plurality of rockers is
operatively connected to the first race and spring biased into engagement with the second
race to transmit torque between the first and second races. A member is selectively
translatable between first and second positions to control the ability of the rockers to
transmit torque between the first and second rockers, and thereby to control the ability of
the races to rotate relative to one another.

Documents:

01572-kol-2007-abstract.pdf

01572-kol-2007-assignment.pdf

01572-kol-2007-claims.pdf

01572-kol-2007-correspondence others 1.1.pdf

01572-kol-2007-correspondence others.pdf

01572-kol-2007-description complete.pdf

01572-kol-2007-drawings.pdf

01572-kol-2007-form 1.pdf

01572-kol-2007-form 2.pdf

01572-kol-2007-form 3.pdf

01572-kol-2007-form 5.pdf

01572-kol-2007-priority document.pdf

1572-KOL-2007-ABSTRACT 1.1.pdf

1572-KOL-2007-ABSTRACT-1.2.pdf

1572-KOL-2007-AMANDED CLAIMS-1.1.pdf

1572-KOL-2007-AMANDED CLAIMS.pdf

1572-KOL-2007-AMANDED PAGES OF SPECIFICATION.pdf

1572-KOL-2007-ASSIGNMENT.pdf

1572-KOL-2007-CORRESPONDENCE 1.1.pdf

1572-KOL-2007-CORRESPONDENCE 1.2.pdf

1572-KOL-2007-CORRESPONDENCE OTHERS 1.2.pdf

1572-KOL-2007-CORRESPONDENCE OTHERS 1.3.pdf

1572-KOL-2007-CORRESPONDENCE-1.1.pdf

1572-KOL-2007-DESCRIPTION (COMPLETE) 1.1.pdf

1572-KOL-2007-DESCRIPTION (COMPLETE)-1.2.pdf

1572-KOL-2007-DRAWINGS 1.1.pdf

1572-KOL-2007-DRAWINGS-1.2.pdf

1572-KOL-2007-EXAMINATION REPORT REPLY RECIEVED.pdf

1572-KOL-2007-EXAMINATION REPORT.pdf

1572-KOL-2007-FORM 1-1.1.pdf

1572-KOL-2007-FORM 1-1.2.pdf

1572-KOL-2007-FORM 18.pdf

1572-KOL-2007-FORM 2-1.1.pdf

1572-KOL-2007-FORM 2-1.2.pdf

1572-KOL-2007-FORM 3 1.2.pdf

1572-KOL-2007-FORM 3-1.1.pdf

1572-KOL-2007-FORM 5.pdf

1572-KOL-2007-GPA.pdf

1572-KOL-2007-GRANTED-ABSTRACT.pdf

1572-KOL-2007-GRANTED-CLAIMS.pdf

1572-KOL-2007-GRANTED-DESCRIPTION (COMPLETE).pdf

1572-KOL-2007-GRANTED-DRAWINGS.pdf

1572-KOL-2007-GRANTED-FORM 1.pdf

1572-KOL-2007-GRANTED-FORM 2.pdf

1572-KOL-2007-GRANTED-LETTER PATENT.pdf

1572-KOL-2007-GRANTED-SPECIFICATION.pdf

1572-KOL-2007-OTHERS 1.2.pdf

1572-KOL-2007-OTHERS-1.1.pdf

1572-KOL-2007-OTHERS.pdf

1572-KOL-2007-PA-1.1.pdf

1572-KOL-2007-PA.pdf

1572-KOL-2007-REPLY TO EXAMINATION REPORT.pdf

abstract-01572-kol-2007.jpg


Patent Number 250018
Indian Patent Application Number 1572/KOL/2007
PG Journal Number 48/2011
Publication Date 02-Dec-2011
Grant Date 29-Nov-2011
Date of Filing 21-Nov-2007
Name of Patentee GM GLOBAL TECHNOLOGY OPERATIONS, INC.
Applicant Address 300 GM RENAISSANCE CENTER, DETROIT, MICHIGAN
Inventors:
# Inventor's Name Inventor's Address
1 SCOTT H. WITTKOPP 6189 OAKHURST DRIVE, YPSILANTI, MICHIGAN 48197
2 CLINTON E. CAREY 215 RIVERVIEW AVENUE MONROE, MICHIGAN 48162
3 JAMES M. HART 16011 HAGGERTY, BELLEVILLE MI 48111
PCT International Classification Number F16D41/08; F16D41/00
PCT International Application Number N/A
PCT International Filing date
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 11/622602 2007-01-12 U.S.A.