Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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CONTINUOUSLY VARIABLE TRANSMISSION
RELATED APPLICATIONS
[0001] This application claims the benefit of U.S. Patent Application No.
14/166,336,
filed on January 28, 2014, which is herein incorporated by reference in its
entirety.
BACKGROUND
[0002] A continuously variable transmission (CVT) is a type of transmission
capable of
providing more useable power, better fuel economy and a smoother driving
experience than a
traditional manual or automatic transmission. A typical automotive
transmission may include
a fixed number of gears from which to select. The transmission may employ a
gear-set that
provides a given number of gear ratios. The transmission shifts gears in an
attempt to
provide the most appropriate gear ratio for a given situation. Switching into
a particular gear
may allow the vehicle to produce near maximum power it can with the least
amount of
energy.
[0003] A continuously variable transmission (CVT) is a transmission capable
of changing
seamlessly through an infinite number of effective gear ratios between maximum
and
minimum values. A CVT makes it possible to vary progressively the transmission
ratio.
This contrasts with other mechanical transmissions that offer a fixed number
of gear ratios.
A CVT may provide better fuel economy than other transmissions, by enabling
the engine to
run at its most efficient revolutions per minute (RPM) for a range of vehicle
power and speed
combinations. A CVT may also be used to maximize the performance of a vehicle
by
allowing the engine to turn at the RPM at which it produces peak power. This
is typically
higher than the RPM that achieves peak efficiency. A CVT may create a more
fuel efficient
vehicle. The nearly unlimited number of positions helps ensure it is always
using the
appropriate amount of power.
SUMMARY
[0004] Disclosed herein is a continuously variable transmission that may
include an input
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disk rotatable about a disk axis of rotation. The input disk may include an
input disk traction
surface. The continuously variable transmission may also include an output
disk rotatable
about the disk axis of rotation. The output disk may include an output disk
traction surface.
An input ring member rotatable about an input axis of rotation may include an
input ring
traction surface located at an input ring traction surface radial distance
from the input axis of
rotation. The input ring traction surface may engage the input disk traction
surface at an
input contact patch oriented substantially perpendicular to a first input
contact patch vector
length extending from the input contact patch to the disk axis of rotation and
a second input
contact patch vector length extending perpendicular from the input contact
patch to the input
axis of rotation. An output ring member rotatable about an output axis of
rotation may
include an output ring traction surface located at an output ring traction
surface radial
distance from the output axis of rotation. The output ring traction surface
may engage the
output disk traction surface at an output contact patch oriented substantially
perpendicular to
a first output contact patch vector length extending perpendicular from the
output contact
patch to the disk axis of rotation and a second output contact patch vector
length extending
from the output contact patch to the output axis of rotation. The sum of a
length of the first
input contact patch vector and a length of the first output contact patch
vector is greater than
a length of at least one of the second input contact patch vector and the
second output contact
patch vector.
BRIEF DESCRIPTION OF THE DRAWINGS
[0005] The description herein makes reference to the accompanying drawings
wherein
like reference numerals refer to like parts throughout the several views, and
wherein:
[0006] FIG. 1 is a cross-sectional schematic illustration of an exemplary
continuously
variable transmission with a speed ratio selector arranged in a first speed
ratio position;
[0007] FIG. 2 is a cross-sectional view of the continuously variable
transmission of FIG.
1 showing a location and orientation of various contact patch vectors;
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[0008] FIG. 3 is a partial cross-sectional view of the continuously
variable transmission
of FIG. 1 taken along section line 3-3, with the speed ratio selector arranged
in the first speed
ratio position;
[0009] FIG. 4 is a schematic illustration of the continuously variable
transmission of FIG.
1 with the speed ratio selector arranged in a second speed ratio position;
[0010] FIG. 5 is a partial cross-sectional view of the continuously
variable transmission
of FIG. 4 taken along section line 5-5, with the speed ratio selector arranged
in the second
speed ratio position;
[0011] FIG. 6 is a schematic illustration of an alternately configured
continuously
variable transmission with a speed ratio selector arranged in a first speed
ratio position;
[0012] FIG. 7 is a cross-sectional view of the continuously variable
transmission of FIG.
6 showing a location and orientation of various contact patch vectors;
[0013] FIG. 8 is a partial cross-sectional view of the continuously
variable transmission
of FIG. 6 taken along section line 8-8, with the speed ratio selector arranged
in the first speed
ratio position;
[0014] FIG. 9 is a schematic illustration of the continuously variable
transmission of FIG.
6 with the speed ratio selector arranged in a second speed ratio position;
[0015] FIG. 10 is a partial cross-sectional view of the continuously
variable transmission
of FIG. 9 taken along section line 10-10, with the speed ratio selector
arranged in the second
speed ratio position;
[0016] FIG. 11 is a schematic illustration of continuously variable
transmission
employing a single ring member operably connecting an input drive member to an
output
drive member, the ring member arranged in a first speed ratio position;
[0017] FIG. 12 is a schematic illustration of the continuously variable
transmission of
FIG. 11, with the ring member arranged in a second speed ratio position;
[0018] FIG. 13 is schematic illustration of a continuously variable
transmission
employing a hydraulically actuated speed ratio selector, the speed ratio
selector arranged in a
first speed ratio position;
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[0019] FIG. 14 is a schematic illustration of the continuously variable
transmission of
FIG. 13 with the speed ratio selector arranged in a second speed ratio
position;
[0020] FIG. 15 is a schematic illustration of yet another alternately
configured
continuously variable transmission employing a geared ring member arrange in a
first speed
ratio position;
[0021] FIG. 16 is a partial cross-sectional view of the continuously
variable transmission
of FIG. 15 taken along section line 16-16;
[0022] FIG. 17 is a schematic illustration of the continuously variable
transmission of
FIG. 15, with the ring member arranged in a second speed ratio position;
[0023] FIG. 18 is a schematic illustration of yet another alternately
configured
continuously variable transmission employing a piloted ring member arranged in
a first speed
ratio position;
[0024] FIG. 19 is a schematic illustration of the continuously variable
transmission of
FIG. 18, with the ring member arranged in a second speed ratio position;
[0025] FIG. 20 is a schematic illustration of yet another alternately
configured
continuously variable transmission shown arranged in a first speed ratio
position;
[0026] FIG. 21 is an end view of the continuously variable transmission
illustrated in
FIG. 20; and
[0027] FIG. 22 is a schematic illustration of the continuously variable
transmission of
FIG. 20 shown arranged in a second speed ratio position.
DETAILED DESCRIPTION
[0028] Referring now to the discussion that follows and also to the
drawings, illustrative
approaches to the disclosed systems and methods are described in detail.
Although the
drawings represent some possible approaches, the drawings are not necessarily
to scale and
certain features may be exaggerated, removed, sectioned out-of-plane or
partially sectioned to
better illustrate and explain the present invention. Further, the descriptions
set forth herein
are not intended to be exhaustive or otherwise limit or restrict the claims to
the precise forms
and configurations shown in the drawings and disclosed in the following
detailed description.
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[0029] With reference to FIG. 1, an exemplary continuously variable
transmission 40
operable for transferring rotational energy between an input shaft 42 and an
output shaft 44.
The input shaft 42 is rotatable about an input axis of rotation 46 and the
output shaft 44 is
rotatable about an output axis of rotation 48. The input axis of rotation 46
may be arranged
substantially parallel to the output axis of rotation 48. The input axis of
rotation 46 may be
offset from the output axis of rotation 48 by a distance 50. The input and
output shafts 42
and 44, respectively, may each be rotatably supported within a housing 52 by
bearings 54.
The bearings 54 may have any of various configurations, including, but not
limited to, a roller
bearing, ball bearing and a tapered bearing, and may include other
configurations. Multiple
bearings 54 and/or bearing types may be used for supporting the input and
output shafts 42
and 44. The position and orientation of the input shaft 42 is generally fixed
relative to the
output shaft 44.
[0030] The continuously variable transmission 40 may include an input drive
mechanism
56 and an output drive mechanism 58 spaced from the input drive mechanism 56.
The input
and output drive mechanisms 56 and 58 may be arranged in series. The input and
output
drive mechanisms 56 and 58, respectively, operate in conjunction with one
another to transfer
rotational torque from the input shaft 42 to the output shaft 44. The input
and output drive
mechanisms 56 and 58 may be selectively adjusted to vary a speed ratio (e.g.,
speed ratio =
(rotational speed of output shaft 44) (rotational speed of input shaft 42))
of the continuously
variable transmission 40. The continuously variable transmission 40 may employ
a speed
ratio selector 60 operable to selectively adjust the speed ratio.
[0031] The input drive mechanism 56 may employ a first input disk 62 and a
second
input disk 64 positioned adjacent the first input disk 62. The first and
second input disks 62
and 64 are each rotatable about a disk axis of rotation 66. The disk axis of
rotation 66 may
be aligned generally parallel with the input axis of rotation 46 and/or the
output axis of
rotation 48. The location of the disk axis of rotation 66 may be selectively
adjusted relative
to the input axis of rotation 46 and/or the output axis of rotation 48 while
maintaining the
orientation of the disk axis of rotation 66 relative to the input axis of
rotation 46 and/or the
output axis of rotation 48. In other words, the disk axis of rotation 66
remains substantially
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parallel to the input axis of rotation 46 and the output axis of rotation 48
when adjusting the
position of the disk axis of rotation 66 relative to the input axis of
rotation 42 and/or the
output axis of rotation 44.
[0032] The first and second input disks 62 and 64 extend generally radially
outward from
the disk axis of rotation 66. An edge 67 defines an outer circumferential
perimeter of the first
input disk 62. The first input disk 62 may include a generally convex
conically-shaped first
input disk traction surface 68 positioned adjacent input shaft 42 and an
opposite inner surface
70 positioned adjacent the second input disk 64. The inner surface 70 of the
first input disk
62 may have generally planar surface contour, as illustrated, for example, in
FIG. 1, or may
include various other shapes and/or contours. For example, the inner surface
70 may include
one or more recessed regions to help minimize weight and/or rotational inertia
of the first
input disk 62.
[0033] The first input disk 62 may be fixedly attached to an inner shaft 72
that extends
latterly outward from the inner surface 70 of the first input disk 62. The
first input disk 62
may alternatively be integrally formed with the inner shaft 72. A longitudinal
axis of the
inner shaft 72 substantially coincides with the disk axis of rotation 66.
[0034] With continued reference to FIG. 1, an edge 74 defines an outer
circumferential
perimeter of the second input disk 64. The second input disk 64 may include an
inner surface
76 positioned adjacent the first input disk 62 and a generally convex
conically-shaped second
input disk traction surface 78 located opposite the inner surface 76. The
second input disk 64
may be generally configured as a mirror image of the first input disk 62 when
viewed from
the perspective of FIG. 1. Similar to first input disk 62, the inner surface
76 of the second
input disk 64 may have generally planar surface contour, as illustrated, for
example, in FIG.
1, or may include various other shapes and/or contours. For example, the inner
surface 76
may include one or more recessed regions to help minimize weight and/or
rotational inertia
of the second input disk 64.
[0035] The second input disk 64 may be fixedly attached to a hollow
cylindrically-shaped
outer shaft 80 that extends latterly outward from the second input disk
traction surface 78 of
the second input disk 64. The second input disk 64 may alternatively be
integrally formed
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with the outer shaft 80. A longitudinal axis of the outer shaft 80
substantially coincides with
the disk axis of rotation 66. The outer shaft 80 includes an elongated outer
shaft passage 82
for receiving inner shaft 72. The outer shaft passage 82 extends lengthwise
along the disk
axis of rotation 66. The inner shaft 72 and outer shaft 80 are moveable
axially relative to one
another along the disk axis of rotation 66 to enable a distance D1 between the
first input disk
traction surface 68 and the second input disk traction surface 68 to be
selectively varied. The
inner shaft 72 and outer shaft 80 may be configured so as to be rotatable
relative to one
another, or may alternatively be rotatably fixed to one another. The latter
may be
accomplished, for example, through use of a spline that allows axial movement
between the
inner and outer shafts 72 and 80, while simultaneously preventing the inner
and outer shafts
72 and 80 from rotating relative to one another. Either way, the inner shaft
72 and outer shaft
80 are generally free to move axially relative to one another.
[0036] The output drive mechanism 58 may be similarly configured as the
input drive
mechanism 56, and may include for example, a first output disk 84 and a second
output disk
86 positioned adjacent the first output disk 84. The first and second output
disks 84 and 86
are each rotatable about the disk axis of rotation 66. The first and second
output disks 84 and
86 extend generally radially outward from the disk axis of rotation 66.
[0037] An edge 88 defines an outer circumferential perimeter of the first
output disk 84.
The first output disk 84 may include a generally convex conically-shaped first
output disk
traction surface 90 arranged adjacent output shaft 44 and an opposite inner
surface 92
positioned adjacent the second output disk 86. The inner surface 92 of the
first output disk
84 may have generally planar surface contour, as illustrated, for example, in
FIG. 1, or may
include various other shapes and/or contours. For example, the inner surface
92 may include
one or more recessed regions to help minimize weight and/or rotational inertia
of the first
output disk 84.
[0038] The first output disk 84 may be fixedly attached to an end 93 of
inner shaft 72
opposite the first input disk 62, causing the first input disk 62 and the
first output disk 84 to
operably rotate in unison about the disk axis of rotation 66. To facilitate
assembly, end 93 of
the inner shaft 72 and first output disk 84 may include conjoining threads to
enable the first
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output disk 84 to be threaded onto the inner shaft 72. Other fastening
mechanisms may also
be used to attach the first output disk 84 to end 83 of the inner shaft 72,
such as bolts, rivets,
screws, gluing, brazing and welding, to name a few. Alternatively, the first
output disk 84
may be integrally formed with the inner shaft 72.
[0039] With continued reference to FIG. 1, an edge 94 defines an outer
circumferential
perimeter of the second output disk 86. The second output disk 86 may include
an inner
surface 96 positioned adjacent the first output disk 84 and a generally convex
conically-
shaped second input disk traction surface 98 located opposite the inner
surface 96. The
second output disk 86 may be generally configured as a mirror image of the
first output disk
84 when viewed from the perspective of FIG. 1. Similar to first output disk
84, the inner
surface 96 of the second input disk 96 may have generally planar surface
contour, as
illustrated, for example, in FIG. 1, or may include various other shapes
and/or contours. For
example, the inner surface 96 may include one or more recessed regions to help
minimize
weight and/or rotational inertia of the second output disk 86.
[0040] The second output disk 86 may be fixedly attached to an end 100 of
the outer
shaft 80, causing the second input disk 64 and the second output disk 86 to
operably rotate in
unison about the disk axis of rotation 66. To facilitate assembly, end 100 of
the outer shaft
80 and second output disk 86 may include conjoining threads to enable the
second output
disk 86 to be threaded onto the outer shaft 80. Other fastening mechanisms may
also be used
to attach the second output disk 86 to end 100 of the outer shaft 80, such as
bolts, rivets,
screws, gluing, brazing and welding, to name a few. Alternatively, the second
output disk 86
may be integrally formed with the outer shaft 80.
[0041] Similar to first input disk 62 and second input disk 64, the first
output disk 84 and
the second output disk 86 are moveable axially relative to one another along
the disk axis or
rotation 66. This enables a distance D2 between the first output disk traction
surface 90 and
the second output disk traction surface 98 to be selectively varied.
[0042] The input drive mechanism 56 may include an input ring member 102
fixedly
connected to the input shaft 42 for concurrent rotation therewith. The input
ring member 102
operates to rotatably couple the first and second input disks 62 and 64 to the
input shaft 42.
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The position and orientation of the input ring member 102 remains
substantially fixed
relative to the input shaft 42. The input ring member 102 may have a generally
C-shaped
configuration with an open end 104 arranged opposite a closed end 106. The
closed end 106
may be fixedly attached to or integrally formed with the input shaft 42. A
generally circular
opening 103 in the open end 104 of the input ring member 102 is defined by a
circumferential
edge 108.
[0043] The first and second input disks 62 and 64 may be positioned within
an interior
cavity 110 of the input ring member 102, with the corresponding inner and
outer shafts 72
and 80 extending through the opening 103 in the input ring member 102. The
opening 103
may be sized larger than the first and second input disks 62 and 64 to
facilitate positioning of
the disks within the interior cavity 110 of the input ring member 102.
[0044] The input ring member 102 may include an input ring first traction
surface 112
engageable with the first input disk traction surface 68 of the first input
disk 62, and an input
ring second traction surface 114 engageable with the second input disk
traction surface 78.
The input ring first and second traction surfaces 112 and 114 may be
configured as
continuous rings extending inward from an inner surface 116 of the input ring
member 102.
The input ring first and second traction surfaces 112 and 114 may be located
at a radius 117
from the input axis of rotation 46. The input ring second traction surface 114
may be
arranged immediately adjacent the opening 103 in the input ring member 102.
The input ring
first traction surface may be located opposite the input ring second traction
surface 114 along
a side of the input ring member 102 attached to the input shaft 42.
[0045] The output drive mechanism 58 may include an output ring member 118
fixedly
connected to the output shaft 44 for concurrent rotation therewith. The output
ring member
118 operates to rotatably couple the first and second output disks 84 and 86
to the output
shaft 44. The position and orientation of the output ring member 118 remains
substantially
fixed relative to the output shaft 44. The output ring member 118 may have a
generally C-
shaped configuration with an open end 120 arranged opposite a closed end 122.
The closed
end 122 may be fixedly attached to or integrally formed with the output shaft
44. A generally
circular opening 124 in the open end 120 of the output ring member 118 is
defined by a
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circumferential edge 126.
[0046] The first and second output disks 84 and 86 may be positioned within
an interior
cavity 130 of the output ring member 118, with the corresponding inner and
outer shafts 72
and 80 extending through the opening 124 in the output ring member 118. The
opening 124
may be sized larger than the first and second output disks 84 and 86 to
facilitate positioning
of the disks within the interior cavity 130 of the output ring member 118.
[0047] The output ring member 118 may include an output ring first traction
surface 132
engageable with the first output disk traction surface 90 of the first output
disk 84, and an
output ring second traction surface 134 engageable with the second output disk
traction
surface 98. The output ring first and second traction surfaces 132 and 134 may
be configured
as a continuous ring extending generally inward from an inner surface 138 of
the output ring
member 118. The output ring first and second traction surfaces 132 and 134 may
be located
at a radius 136 from the output axis of rotation 48. The output ring second
traction surface
134 may be arranged immediately adjacent the opening 124 in the output ring
member 118.
The output ring first traction surface 132 may be located opposite the output
ring second
traction surface 134 along a side of the output ring member 118 attached to
the output shaft
44.
[0048] The continuously variable transmission 40 operates to transfer
torque from the
input shaft 42 to the output shaft 44. Torque from the input shaft 42 may be
transmitted from
the input ring member 102 to the first input disk 62 across a first input
contact patch 140
where the input ring first traction surface 112 engages the first input disk
traction surface 78,
and to the second input disk 64 across a second input contact patch 142 where
the input ring
second traction surface 114 engages the second input disk traction surface 78.
The first and
second input contact patches 140 and 142 are located at a radius 143 from the
disk axis of
rotation 66. The radius 143 of the first and second input contact patches 140
and 142 varies
as the speed ratio of the continuously variable transmission 40 is varied. The
inner shaft 72
transfers torque from the first input disk 62 to the first output disk 84. The
outer shaft 80
transfers torque from the second input disk 64 to the second output disk 86.
Torque may be
transferred from the first output disk 84 to the output ring member 118 across
a first output
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contact patch 144 where the output ring first traction surface 132 engages the
first output disk
traction surface 90. Torque may be transferred from the second output disk 86
to the output
ring member 118 across a second output contact patch 146 where the output ring
second
traction surface 134 engages the second output disk traction surface 134. The
first and
second output contact patches 144 and 146 are located at a radius 147 from the
disk axis of
rotation 66. It should be noted that for purposes of discussion the first and
second contact
patches 144 and 146 are illustrated as occurring within a common plane, so as
to be arranged
on diametrically opposite sides of disk axis of rotation 66 (i.e.,
approximately 180 degrees
apart). In practice, however, first and second contact patches 144 and 146 may
be located
out-of-plane, such that the angular location of the first and second contact
patches relative to
one another is something other than 180 degrees. The radius 147 of the first
and second
output contact patches 144 and 146 varies as the speed ratio of the
continuously variable
transmission 40 is varied. The output ring member 118 operates to transfer
torque from the
first and second output disks 84 and 86 to the output shaft 44.
[0049] The speed ratio of the continuously variable transmission 40 is a
function of the
radial location 143 of the first and second input contact patches 140 and 142,
and the radial
location 147 of the first and second output contact patches 144 and 146. The
speed ratio of
the continuously variable transmission 40 is partially determined by the
radial location at
which the input ring first and second traction surfaces 112 and 114 engage the
first and
second input disk traction surfaces 68 and 78, respectively (i.e., the radial
location 143 of the
first and second input contact patches 140 and 142). The rotational speed of
the output shaft
44 decreases, relative to the rotational speed of the input shaft 42, as the
radial location 143
of the first and second input contact patches 140 and 142 increases. On the
other hand, the
rotational speed of the output shaft 44 increases as the radial location 143
of the first and
second input contact patches 140 and 142 decreases. The radial location at
which the output
ring first and second traction surfaces 132 and 134 engage the first and
second output disk
traction surfaces 90 and 98, respectively (i.e., the radial location 147 of
the first and second
output contact patches 144 and 146) has the opposite effect. The rotational
speed of the
output shaft 44 increases, relative to the rotational speed of the input shaft
42, as the radial
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location 147 of the first and second output contact patches 144 and 146
increases. On the
other hand, the rotational speed of the output shaft 44 decreases as the
radial location 147 of
the first and second output contact patches 144 and 146 decreases.
[0050] The speed ratio may be selectively adjusted by moving the location
of the disk
axis of rotation 66 relative to the input axis of rotation 46 and the output
axis of rotation 48,
which effects the radial location 143 at which the input ring member 102
engages the first
and second input disks 62 and 64, and the radial location 147 at which the
output ring
member 118 engages the first and second output disks 84 and 86. Since the
first input disk
46 is connected to the first output disk 84 by way of inner shaft 72, and the
second input disk
64 is connected to the second output disk 86 by way of outer shaft 80, any
movement of the
first and second input disks 62 and 64 results in corresponding movement of
the first and
second output disks 84 and 86. For example, moving the first and second input
disks 62 and
64 radially upward (as viewed from the perspective of FIG. 1) also moves the
first and second
output disks radially upward. On the other hand, moving the first and second
input disks 62
and 64 radially downward (as viewed from the perspective of FIG. 1) also moves
the first and
second output disks radially downward.
[0051] With reference to FIG. 2, the first input contact patch 140 is
aligned substantially
perpendicular to a first input contact patch vector 154 extending from the
first input contact
patch 140 to the disk axis of rotation 66, and aligned substantially
perpendicular to a second
input contact patch vector length 156 extending from the first input contact
patch 140 to the
input axis of rotation 46. Similarly, the first output contact patch 146 is
aligned substantially
perpendicular to a first output contact patch vector 158 extending from the
first output
contact patch 146 to the disk axis of rotation 66, and aligned substantially
perpendicular to a
second output contact patch vector 160 extending from the first output contact
patch 146 to
the output axis of rotation 48. The configuration and arrangement of the
various components
of the continuously variable transmission 40 is such that a sum of a length of
the first input
contact patch vector 154 and a length of the first output contact patch vector
158 is greater
than a length of the second input contact patch vector 156 and a length of the
second output
contact patch vector 160. The following relationship holds true for all speed
ratios:
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A. ((length of first input contact patch vector 154) + (length of first
output
contact patch vector 158)) > (length of second input contact patch vector
156); and
B. ((length of first input contact patch vector 154) + (length of first
output
contact patch vector 158)) > (length of second output contact patch vector
160)
[0052] A similar relationship also holds true for the second input contact
patch 142 and
the second output contact patch 144. For example, a sum of a length of a first
input contact
patch vector extending from the second input contact patch 142 to the disk
axis of rotation 66
and aligned substantially perpendicular to the second input contact patch 142,
and a length of
a first output contact patch vector extending from the second output contact
patch 146 to the
disk axis of rotation 66 and aligned substantially perpendicular to the second
output contact
patch 146 is greater than at least one of a length of a second input contact
patch vector
extending from the second input contact patch 142 to the input axis of
rotation 46 and aligned
substantially perpendicular to the second output contact patch 142, and a
length of a second
output contact patch vector extending from the second output contact patch 146
to the output
axis of rotation 48 and aligned substantially perpendicular to the second
output contact patch
146.
[0053] With reference to FIGS. 1 and 3-5, the speed ratio selector 60 may
be used to
selectively adjust the speed ratio of the continuously variable transmission
40. The speed
ratio selector 60 may have any of a wide variety of configurations. The speed
ratio selector
60 may employ any device capable of adjusting a location of the first and
second input disks
62 and 64 relative to the input ring 102 and the first and second output disks
84 and 86
relative to the output ring 118. This may be accomplished, for example, by
selectively
adjusting the location of the disk axis of rotation 66 relative to the input
axis of rotation 46
and/or the output axis of rotation 48. An example of one possible
configuration of the speed
ratio selector 60 is illustrated in the drawing figures. The speed ratio
selector 60 may include,
for example, a pair of interconnected links operably connecting the outer
shaft 80, and
correspondingly, the inner shaft 72, the first and second input disks 62 and
64, and the first
and second output disks 84 and 86, to the housing 52. The speed ratio selector
60 operates to
vary the location of the disk axis of rotation 66 relative to the input axis
of rotation 46 and
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output axis of rotation 48, and thus the speed ratio. The speed ratio selector
60 may include a
first link 148 pivotally attached to the outer shaft 80 and a second link 150
pivotally attached
to the first link 148 and the housing 52. The speed ratio selector 60 may
employ one or more
bearings 152 located at the pivot points of the speed ratio selector 60. The
speed ratio may be
varied by alternately collapsing and extending the first and second links 148
and 150, which
varies a distance between the disk axis of rotation 66 and the housing 52, and
correspondingly, the location of the disk axis of rotation 66 relative to the
input axis of
rotation 46 and the output axis of rotation 48.
[0054] FIGS. 1 and 3 illustrate the speed ratio selector 60 arranged in a
first speed ratio
position, in which the first and second links 148 and 150 are fully extended.
In this position
the input ring member 102 engages the first and second input disks 62 and 64
near their
respective outer edges 67 and 74, and the output ring member 118 engages the
first and
second output disks 84 and 86 closer toward the disk axis of rotation 66. This
arrangement
produces the lowest speed ratio (e.g., speed ratio = (rotational speed of
output shaft 44)
(rotational speed of input shaft 42)), wherein the output shaft 44 has a lower
rotational speed
than the input shaft 42.
[0055] FIGS. 4 and 5 illustrate the speed ratio selector 60 arranged in a
second speed
ratio position, in which the first and second links 148 and 150 are fully
collapsed. In this
position the output ring member 118 engages the first and second output disks
84 and 86 near
their respective outer edges 88 and 94, and the input ring member 102 engages
the first and
second input disks 62 and 64 closer toward the disk axis of rotation 66. This
arrangement
produces the highest speed ratio, wherein the output shaft 44 has a lower
rotational speed
than the input shaft 42. The speed ratio selector 60 may be infinitely
adjustable between the
first speed ratio position (for example, as illustrated in FIGS. 1 and 3) and
the second speed
ratio position (for example, as illustrated in FIGS. 4 and 5).
[0056] The speed ratio selector 60 illustrated in the drawing figures is
merely one
example of the various types and configuration of actuators that may be used
to selectively
adjust the speed ratio of the continuously variable transmission. Other types
and
configurations of actuating mechanisms may also be employed. For example, the
speed ratio
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selector 60 may include electro-mechanical, hydraulic, pneumatic and
mechanical actuators,
as well as combinations thereof. Other mechanisms capable of selectively
adjusting the
radial location of the first and second input disks 62 and 64 relative to the
input ring member
102, and the radial location of the first and second output disks 84 and 86
relative to the
output ring member 118, may also be employed for selectively adjusting the
speed ratio of
the continuously variable transmission 40.
[0057] With reference to FIG. 6, an alternately configured continuously
variable
transmission 200 operable for transferring rotational energy between the input
shaft 42 and
the output shaft 44. The input shaft 42 is rotatable about the input axis of
rotation 46 and the
output shaft 44 is rotatable about an output axis of rotation 48. The input
axis of rotation 46
may be arranged substantially parallel to the output axis of rotation 48. The
input axis of
rotation 46 may be offset from the output axis of rotation 48 by the distance
50. The input
and output shafts 42 and 44, respectively, may each be rotatably supported
within the housing
52 by bearings 54. The position and orientation of the input shaft 42 is
generally fixed
relative to the output shaft 44. The offset distance 50 may be used to
compensate for variation
in working fluid viscosity.
[0058] The continuously variable transmission 200 may include an input
drive
mechanism 202 and an output drive mechanism 204 spaced from the input drive
mechanism
202. The input and output drive mechanisms 202 and 204, respectively, operate
in
conjunction with one another to transfer rotational torque from the input
shaft 42 to the
output shaft 44. The input and output drive mechanisms 202 and 204 may be
arranged in
series. The input and output drive mechanisms 202 and 204 may be selectively
adjusted to
vary the speed ratio (e.g., speed ratio = (rotational speed of output shaft
44) (rotational
speed of input shaft 42)) of the continuously variable transmission 200. The
continuously
variable transmission 200 may employ the speed ratio selector 60 operable to
selectively
adjust the speed ratio.
[0059] The input drive mechanism 202 may employ a first input disk 206 and
a second
input disk 208 positioned adjacent the first input disk 206. The first and
second input disks
206 and 208 are each rotatable about a disk axis of rotation 210. The disk
axis of rotation
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210 may be aligned generally parallel with the input axis of rotation 46
and/or the output axis
of rotation 48. The location of the disk axis of rotation 210 may be
selectively adjusted
relative to the input axis of rotation 46 and/or the output axis of rotation
48 while maintaining
the orientation of the disk axis of rotation 210 relative to the input axis of
rotation 46 and/or
the output axis of rotation 48. In other words, the disk axis of rotation 210
remains
substantially parallel to the input axis of rotation 46 and the output axis of
rotation 48 when
adjusting the position of the disk axis of rotation 210 relative to the input
axis of rotation 42
and/or the output axis of rotation 44.
[0060] The first and second input disks 206 and 208 extend generally
radially outward
from the disk axis of rotation 210. An edge 212 defines an outer
circumferential perimeter of
the first input disk 206. The first input disk 206 may include a generally
convex conically-
shaped first input disk traction surface 214 positioned opposite the input
shaft 42 and
adjacent the second input disk 208. Opposite the input disk traction surface
214 is an outer
surface 216 positioned adjacent the input shaft 42. The outer surface 216 of
the first input
disk 206 may have generally planar surface contour, as illustrated, for
example, in FIG. 6, or
may include various other shapes and/or contours. For example, the inner
surface 216 may
include one or more recessed regions to help minimize weight and/or rotational
inertia of the
first input disk 206.
[0061] The first input disk 206 may be fixedly attached to an inner shaft
218 that extends
laterally outward from the first input disk traction surface 214 of the first
input disk 206. The
first input disk 206 may alternatively be integrally formed with the inner
shaft 218. A
longitudinal axis of the inner shaft 218 substantially coincides with the disk
axis of rotation
210.
[0062] With continued reference to FIG. 6, an edge 220 defines an outer
circumferential
perimeter of the second input disk 208. The second input disk 208 may include
a generally
convex conically-shaped second input disk traction surface 222 positioned
adjacent the first
input disk 206 and an outer surface 224 located opposite the second input disk
traction
surface 222. The second input disk 208 may be generally configured as a mirror
image of the
first input disk 206 when viewed from the perspective of FIG. 6. Similar to
first input disk
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206, the outer surface 224 of the second input disk 208 may have generally
planar surface
contour, as illustrated, for example, in FIG. 6, or may include various other
shapes and/or
contours. For example, the outer surface 224 may include one or more recessed
regions to
help minimize weight and/or rotational inertia of the second input disk 208.
[0063] The second input disk 208 may be fixedly attached to a hollow
cylindrically-
shaped outer shaft 226 that extends latterly outward from the outer surface
224 of the second
input disk 208. The second input disk 208 may alternatively be integrally
formed with the
outer shaft 226. A longitudinal axis of the outer shaft 226 substantially
coincides with the
disk axis of rotation 210. The outer shaft 226 includes an elongated outer
shaft passage 228
for receiving inner shaft 218. The outer shaft passage 226 extends lengthwise
along the disk
axis of rotation 210. The inner shaft 218 and outer shaft 226 are moveable
axially relative to
one another along the disk axis of rotation 210 to enable a distance D1
between the first input
disk traction surface 214 and the second input disk traction surface 22 to be
selectively
varied. The inner shaft 218 and outer shaft 226 may be configured so as to be
rotatable
relative to one another, or may alternatively be rotatably fixed to one
another. The latter may
be accomplished, for example, through use of a spline that allows axial
movement of the
inner and outer shafts 218 and 226 relative to one another, while
simultaneously preventing
the inner and outer shafts 218 and 226 from rotating relative to one another.
Either way, the
inner shaft 218 and outer shaft 226 are generally free to move axially
relative to one another.
[0064] The output drive mechanism 204 may be similarly configured as the
input drive
mechanism 202, and may include for example, a first output disk 230 and a
second output
disk 232 positioned adjacent the first output disk 230. The first and second
output disks 230
and 232 are each rotatable about the disk axis of rotation 210. The first and
second output
disks 230 and 232 extend generally radially outward from the disk axis of
rotation 210.
[0065] An edge 234 defines an outer circumferential perimeter of the first
output disk
230. The first output disk 230 may include a generally convex conically-shaped
first output
disk traction surface 236 arranged opposite the output shaft 44 and an
adjacent the second
output disk 232. An outer surface 238 of the first output disk 230 may have a
generally
planar surface contour, as illustrated, for example, in FIG. 6, or may include
various other
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shapes and/or contours. For example, the outer surface 238 may include one or
more
recessed regions to help minimize weight and/or rotational inertia of the
first output disk 230.
[0066] The first output disk 230 may be fixedly attached to an end 240 of
inner shaft 218
opposite the first input disk 206, causing the first input disk 206 and the
first output disk 230
to operably rotate in unison about the disk axis of rotation 210. To
facilitate assembly, end
240 of the inner shaft 218 and the first output disk 230 may include
conjoining threads to
enable the first output disk 230 to be threaded onto the inner shaft 218.
Other fastening
mechanisms may also be used to attach the first output disk 230 to end 240 of
the inner shaft
218, such as bolts, rivets, screws, gluing, brazing and welding, to name a
few. Alternatively,
the first output disk 230 may be integrally formed with the inner shaft 218.
[0067] With continued reference to FIG. 6, an edge 242 defines an outer
circumferential
perimeter of the second output disk 232. The second output disk 232 may
include a generally
convex conically-shaped second input disk traction surface 244 positioned
adjacent the first
output disk 230 and located opposite an outer surface 246. The second output
disk 232 may
be generally configured as a mirror image of the first output disk 230 when
viewed from the
perspective of FIG. 6. Similar to the first output disk 230, the outer surface
246 of the second
input disk 232 may have generally planar surface contour, as illustrated, for
example, in FIG.
6, or may include various other shapes and/or contours. For example, the outer
surface 246
may include one or more recessed regions to help minimize weight and/or
rotational inertia
of the second output disk 232.
[0068] The second output disk 232 may be fixedly attached to an end 248 of
the outer
shaft 226, causing the second input disk 208 and the second output disk 232 to
operably
rotate in unison about the disk axis of rotation 210. To facilitate assembly,
end 248 of the
outer shaft 226 and the second output disk 232 may include conjoining threads
to enable the
second output disk 232 to be threaded onto the outer shaft 226. Other
fastening mechanisms
may also be used to attach the second output disk 232 to end 248 of the outer
shaft 226, such
as bolts, rivets, screws, gluing, brazing and welding, to name a few.
Alternatively, the second
output disk 232 may be integrally formed with the outer shaft 226.
[0069] Similar to first input disk 206 and second input disk 208, the first
output disk 230
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and the second output disk 232 are moveable axially relative to one another
along the disk
axis or rotation 210. This enables a distance D2 between the first output disk
traction surface
236 and the second output disk traction surface 244 to be selectively varied.
[0070] The
input drive mechanism 202 may include an input ring member 250 fixedly
connected to the input shaft 42 for concurrent rotation therewith. The input
ring member 250
operates to rotatably couple the first and second input disks 206 and 208 to
the input shaft 42.
The position and orientation of the input ring member 250 remains
substantially fixed
relative to the input shaft 42. The input ring member 250 may have a generally
C-shaped
configuration with an open end 254 arranged opposite a closed end 256. The
closed end 256
may be fixedly attached to or integrally formed with the input shaft 42. A
generally circular
opening 252 in the open end 254 of the input ring member 250 is defined by a
circumferential
edge 258.
[0071] The
first input disk 206 may be positioned within an interior cavity 260 of the
input ring member 250, with the inner shaft 218 extending through the opening
252 in the
input ring member 250. The opening 252 may be sized larger than the first
input disk 206 to
facilitate positioning of the disk within the interior cavity 260 of the input
ring member 250.
The second input disk 208 may be positioned outside of the input ring member
250 adjacent
the opening 252.
[0072] The
input ring member 250 may include an input ring first traction surface 262
engageable with the first input disk traction surface 214 of the first input
disk 206, and an
input ring second traction surface 264 engageable with the second input disk
traction surface
222. The input ring first and second traction surfaces 262 and 264 may be
configured as a
continuous ring. The input ring first and second traction surfaces 262 and 264
may be
located at a radius 265 from the input axis of rotation 46. The input ring
first and second
traction surfaces 262 and 264 may be arranged immediately adjacent the opening
252 in the
input ring member 250. The input ring first and second traction surfaces 262
and 264
generally face in opposite directions, with the first input ring traction
surface 262 extending
generally inward toward the interior cavity 260 and the second input traction
surface 264
extending generally outward and away from the interior cavity 260.
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[0073] The output drive mechanism 204 may include an output ring member 266
fixedly
connected to the output shaft 44 for concurrent rotation therewith. The output
ring member
266 operates to rotatably couple the first and second output disks 230 and 232
to the output
shaft 44. The position and orientation of the output ring member 266 remains
substantially
fixed relative to the output shaft 44. The output ring member 266 may have a
generally C-
shaped configuration with an open end 268 arranged opposite a closed end 270.
The closed
end 270 may be fixedly attached to or integrally formed with the output shaft
44. A generally
circular opening 272 in the open end 270 of the output ring member 266 is
defined by a
circumferential edge 274.
[0074] The first output disk 230 may be positioned within an interior
cavity 276 of the
output ring member 266, with the inner shaft 218 extending through the opening
268 in the
output ring member 266. The opening 268 may be sized larger than the first
output disk 230
to facilitate positioning of the disk within the interior cavity 276 of the
output ring member
266. The second output disk 232 may be positioned outside of the output ring
member 266
adjacent the opening 268.
[0075] The output ring member 266 may include an output ring first traction
surface 278
engageable with the first output disk traction surface 236 of the first output
disk 230, and an
output ring second traction surface 280 engageable with the second output disk
traction
surface 244. The output ring first and second traction surfaces 278 and 280
may be
configured as a continuous ring. The output ring first and second traction
surfaces 278 and
280 may be located at a radius 281 from the input axis of rotation 46. The
output ring first
and second traction surfaces 278 and 280 may be arranged immediately adjacent
the opening
268 in the output ring member 266. The output ring first and second traction
surfaces 278
and 280 generally face in opposite directions, with the first output ring
traction surface 278
extending generally inward toward the interior cavity 276 and the second
output traction
surface 280 extending generally outward and away from the interior cavity 276.
[0076] With reference to FIG. 6, the continuously variable transmission 200
operates to
transfer torque from the input shaft 42 to the output shaft 44. Torque from
the input shaft 42
may be transmitted from the input ring member 250 to the first input disk 206
across a first
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input contact patch 282 where the input ring first traction surface 262
engages the first input
disk traction surface 214, and to the second input disk 208 across a second
input contact
patch 284 where the input ring second traction surface 264 engages the second
input disk
traction surface 222. The first and second input contact patches 282 and 284
are located at a
radius 285 from the disk axis of rotation 210. The radius 285 of the first and
second input
contact patches 282 and 284 varies as the speed ratio of the continuously
variable
transmission 200 is varied. The inner shaft 218 transfers torque from the
first input disk 206
to the first output disk 230. The outer shaft 226 transfers torque from the
second input disk
208 to the second output disk 232. Torque may be transferred from the first
output disk 230
to the output ring member 266 across a first output contact patch 286 where
the output ring
first traction surface 278 engages the first output disk traction surface 236.
Torque may be
transferred from the second output disk 232 to the output ring member 266
across a second
output contact patch 288 where the output ring second traction surface 280
engages the
second output disk traction surface 244. The first and second output contact
patches 286 and
288 are located at a radius 289 from the disk axis of rotation 210. The radius
289 of the first
and second output contact patches 286 and 288 varies as the speed ratio of the
continuously
variable transmission 200 is varied. The output ring member 266 operates to
transfer torque
from the first and second output disks 230 and 232 to the output shaft 44.
[0077] The speed ratio of the continuously variable transmission 200 is a
function of the
radial location 285 of the first and second input contact patches 282 and 284,
and the radial
location 289 of the first and second output contact patches 286 and 288. The
speed ratio of
the continuously variable transmission 200 is partially determined by the
radial location at
which the input ring first and second traction surfaces 262 and 264 engage the
first and
second input disk traction surfaces 214 and 222, respectively (i.e., the
radial location 285 of
the first and second input contact patches 282 and 284). The rotational speed
of the output
shaft 44 decreases, relative to the rotational speed of the input shaft 42, as
the radial location
285 of the first and second input contact patches 282 and 284 increases. On
the other hand,
the rotational speed of the output shaft 44 increases as the radial location
285 of the first and
second input contact patches 282 and 284 decreases. The radial location at
which the output
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ring first and second traction surfaces 278 and 280 engage the first and
second output disk
traction surfaces 236 and 244, respectively (i.e., the radial location 289 of
the first and second
output contact patches 286 and 288) has the opposite effect. The rotational
speed of the
output shaft 44 increases, relative to the rotational speed of the input shaft
42, as the radial
location 289 of the first and second output contact patches 286 and 288
decreases. On the
other hand, the rotational speed of the output shaft 44 decreases as the
radial location 289 of
the first and second output contact patches 286 and 288 increases.
[0078] The speed ratio may be selectively adjusted by moving the location
of the disk
axis of rotation 210 relative to the input axis of rotation 46 and/or the
output axis of rotation
48, which effects the radial location 285 at which the input ring member 250
engages the first
and second input disks 206 and 208, and the radial location 289 at which the
output ring
member 266 engages the first and second output disks 230 and 232. Since the
first input disk
206 is connected to the first output disk 230 by way of inner shaft 218, and
the second input
disk 208 is connected to the second output disk 232 by way of outer shaft 226,
any movement
of the first and second input disks 206 and 208 results in corresponding
movement of the first
and second output disks 230 and 232. For example, moving the first and second
input disks
206 and 208 radially upward (as viewed from the perspective of FIG. 6) also
moves the first
and second output disks 230 and 232 radially upward. On the other hand, moving
the first
and second input disks 206 and 208 radially downward (as viewed from the
perspective of
FIG. 6) also moves the first and second output disks 230 and 232 radially
downward.
[0079] With reference to FIG. 7, the second input contact patch 284 is
aligned
substantially perpendicular to a first input contact patch vector 290
extending from the
second input contact patch 284 to the disk axis of rotation 210, and aligned
substantially
perpendicular to a second input contact patch vector 292 extending from the
second input
contact patch 284 to the input axis of rotation 46. Similarly, the second
output contact patch
286 is aligned substantially perpendicular to a first output contact patch
vector 294 extending
from the first output contact patch 286 to the disk axis of rotation 210, and
aligned
substantially perpendicular to a second output contact patch vector 296
extending from the
second output contact patch 286 to the output axis of rotation 48. The
configuration and
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arrangement of the various components of the continuously variable
transmission 200 is such
that a sum of a length of the first input contact patch vector 290 and a
length of the first
output contact patch vector 294 is greater than a length of the second input
contact patch
vector 292 and a length of the second output contact patch vector 296. The
following
relationship holds true for all speed ratios:
A. ((length of first input contact patch vector 290) + (length of first
output
contact patch vector 294)) > (length of second input contact patch vector
292); and
B. ((length of first input contact patch vector 290) + (length of first
output
contact patch vector 294)) > (length of second output contact patch vector
296)
[0080] A similar relationship also holds true for the first input contact
patch 282 and the
first output contact patch 288. For example, a sum of a length of a first
input contact patch
vector length extending from the first input contact patch 282 to the disk
axis of rotation 210
and aligned substantially perpendicular to the first input contact patch 282,
and a length of a
first output contact patch vector length extending from the first output
contact patch 288 to
the disk axis of rotation 66 and aligned substantially perpendicular to the
first output contact
patch 288 is greater than at least one of a length of a second input contact
patch vector length
extending from the first input contact patch 282 to the input axis of rotation
46 and aligned
substantially perpendicular to the first input contact patch 282, and a length
of a second
output contact patch vector length extending from the first output contact
patch 288 to the
output axis of rotation 48 and aligned substantially perpendicular to the
first output contact
patch 288.
[0081] The speed ratio selector 60 may be used to selectively adjust the
speed ratio of the
continuously variable transmission 200. The speed ratio selector 60 may be
configured as
previously described in connection with FIGS. 1 and 3-5. FIGS. 6 and 8
illustrate the speed
ratio selector 60 arranged in a second speed ratio position, in which the
first and second links
148 and 150 are fully extended. In this position the input ring member 250
engages the first
and second input disks 206 and 208 near their respective outer edges 212 and
220, and the
output ring member 266 engages the first and second output disks 230 and 232
closer toward
the disk axis of rotation 210. This arrangement produces the highest speed
ratio (e.g., speed
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ratio = (rotational speed of output shaft 44) (rotational speed of input
shaft 42)), wherein
the output shaft 44 has a higher rotational speed than the input shaft 42.
[0082] FIGS. 9 and 10 illustrate the speed ratio selector 60 arranged in a
first speed ratio
position, in which the first and second links 148 and 150 are fully collapsed.
In this position
the output ring member 266 engages the first and second output disks 230 and
232 near their
respective outer edges 234 and 242, and the input ring member 250 engages the
first and
second input disks 206 and 208 closer toward the disk axis of rotation 210.
This arrangement
produces the lowest speed ratio, wherein the output shaft 44 has a lower
rotational speed than
the input shaft 42. The speed ratio selector 60 may be infinitely adjustable
between the first
speed ratio position (for example, as illustrated in FIGS. 6 and 8) and the
second speed ratio
position (for example, as illustrated in FIGS. 9 and 10).
[0083] With reference to FIG. 11, an alternately configured continuously
variable
transmission 300 operable for transferring rotational energy between the input
shaft 42 and
the output shaft 44. The input shaft 42 is rotatable about the input axis of
rotation 46 and the
output shaft 44 is rotatable about an output axis of rotation 48. The input
axis of rotation 46
may be arranged substantially parallel to the output axis of rotation 48. The
position and
orientation of the input shaft 42 is generally fixed relative to the output
shaft 44.
[0084] The continuously variable transmission 300 may include an input
drive
mechanism 302 and an output drive mechanism 304 spaced from the input drive
mechanism
302. The input and output drive mechanisms 302 and 304 may be arranged in
series. The
input and output drive mechanisms 302 and 304, respectively, operate in
conjunction with
one another to transfer rotational torque from the input shaft 42 to the
output shaft 44.
[0085] The input drive mechanism 302 may employ a first input disk 306 and
a second
input disk 308 positioned adjacent the first input disk 306. The first input
disk 306 may be
fixedly attached to the input shaft 42. The second input disk 308 may be
fixedly attached to a
hollow cylindrically-shaped input outer shaft 326 that extends laterally
outward from the
second input disk 308. The first and second input disks 306 and 308 are each
rotatable about
an input disk axis of rotation 310. The input disk axis of rotation 310
substantially coincides
with a longitudinal axis of the input shaft 42 and the input outer shaft 326.
The input shaft 42
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and the input outer shaft 326 may be rotatably supported within the housing 52
by one or
more bearings 54.
[0086] The first and second input disks 306 and 308 extend generally
radially outward
from the input disk axis of rotation 310. An edge 312 defines an outer
circumferential
perimeter of the first input disk 306. The first input disk 306 may include a
generally convex
conically-shaped first input disk traction surface 314 positioned adjacent the
second input
disk 308. An edge 320 defines an outer circumferential perimeter of the second
input disk
308. The second input disk 308 may include a generally convex conically-shaped
second
input disk traction surface 322 positioned adjacent the first input disk 306.
The second input
disk 308 may be generally configured as a mirror image of the first input disk
306 when
viewed from the perspective of FIG. 11.
[0087] The axial location of the input outer shaft 326 and the second input
disk 308 may
be axially fixed relative to the housing 52. The input shaft 42 and the first
input disk 306
may be moveable axially along the input disk axis of rotation 310 relative to
the second input
disk 306 to enable the distance D1 between the first input disk traction
surface 314 and the
second input disk traction surface 322 to be selectively varied.
Alternatively, the axially
location of the input shaft 42 and the first input disk 306 may be axially
fixed relative to the
input outer shaft 326 and the second input disk 308, and the input outer shaft
326 and the
second input disk 308 may be moveable axially along the input disk axis of
rotation 310
relative to the input shaft 42 and the first input disk 306.
[0088] An input biasing mechanism 329 may be operably connected to the
input shaft 42.
The input biasing mechanism 329 operates to urge the first input disk 306
toward the second
input disk 308. Various biasing mechanisms may be employed, which may include
for
example, a spring, such as a coil spring, and various hydraulic, mechanical,
electro-
mechanical devices capable of generating a biasing force.
[0089] The input shaft 42 and input outer shaft 326 may be configured so as
to be
rotatable relative to one another, or alternatively rotatably fixed to one
another. The latter
may be accomplished, for example, by employing a spline that enables axial
movement of the
input shaft 42 and the input outer shaft 326 relative to one another, while
simultaneously
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preventing the input shaft 42 and input outer shaft 326 from rotating relative
to one another.
Either way, the input shaft 42 and input outer shaft 326 are generally free to
move axially
relative to one another.
[0090] The output drive mechanism 304 may be similarly configured as the
input drive
mechanism 302, and may include for example, a first output disk 330 and a
second output
disk 332 positioned adjacent the first output disk 330. The first and second
output disks 330
and 332 are each rotatable about an output disk axis of rotation 328. The
first output disk
330 may be fixedly attached to the output shaft 44. The second output disk 332
may be
fixedly attached to a hollow cylindrically-shaped output outer shaft 333 that
extends latterly
outward from the second output disk 332. The output disk axis of rotation 328
substantially
coincides with a longitudinal axis of the output shaft 44 and the output outer
shaft 333. The
output shaft 44 and the output outer shaft 333 may be rotatably supported
within the housing
52 by one or more bearings 54.
[0091] The first and second output disks 330 and 332 extend generally
radially outward
from the output disk axis of rotation 328. An edge 334 defines an outer
circumferential
perimeter of the first output disk 330. The first output disk 330 may include
a generally
convex conically-shaped first output disk traction surface 336 arranged
adjacent the second
output disk 332. An edge 338 defines an outer circumferential perimeter of the
second output
disk 332. The second output disk 332 may include a generally convex conically-
shaped
second output disk traction surface 340 positioned adjacent the first input
disk 330. The
second output disk 332 may be generally configured as a mirror image of the
first output disk
330 when viewed from the perspective of FIG. 11.
[0092] An axial location of the second output disk 332 may be substantially
fixed relative
to the housing 52. The output shaft 44 may be moveable axially along the
output disk axis of
rotation 328 relative to the output outer shaft 333 and the first output disk
330 to enable the
distance D2 between the first output disk traction surface 336 and the second
output disk
traction surface 340 to be selectively varied. Alternatively, the axially
location of the output
shaft 44 may be axially fixed relative to the housing 52, and the output outer
shaft 333 and
second output disk 332 may be moveable axially along the output disk axis of
rotation 328
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relative to the output shaft 44 and the first output disk 330.
[0093] An output biasing mechanism 341 may be operably connected to the
output shaft
44. The output biasing mechanism 341 operates to urge the first output disk
330 toward the
second output disk 332. Various biasing mechanisms may be employed, which may
include
for example, a spring, such as a coil, and various hydraulic, mechanical,
electro-mechanical
devices capable of generating a biasing force.
[0094] The output shaft 44 and output outer shaft 333 may be configured so
as to be
rotatable relative to one another, or alternatively rotatably fixed to one
another. The latter
may be accomplished, for example, by employing a spline that permits axial
movement of the
output shaft 44 and the input outer shaft 333 relative to one another, while
simultaneously
preventing the output shaft 44 and output outer shaft 333 from rotating
relative to one
another. Either way, the output shaft 44 and output outer shaft 333 are
generally free to move
axially relative to one another.
[0095] The continuously variable drive mechanism 300 may include a ring
member 342
operably connecting the input drive mechanism 302 to the output drive
mechanism 304. The
ring member 342 may be moved radially relative to the input drive mechanism
302 and the
output drive mechanism 304. The radial location of the ring member 342 may be
selectively
adjusted relative to the input and output drive mechanisms 302 and 304 to vary
the speed
ratio (e.g., speed ratio = (rotational speed of output shaft 44) (rotational
speed of input shaft
42)) of the continuously variable transmission 300.
[0096] A speed ratio selector 344 may be operably connected to the ring
member 342 to
selectively adjust the speed ratio of the continuously variable transmission
300. The speed
ratio selector 344 operates to adjust the radial location of the ring member
342 relative to the
input and output drive mechanisms 302 and 304 to achieve a selected speed
ratio. The speed
ratio selector 344 may have any of a wide variety of configurations. The speed
ratio selector
344 may employ any device capable of adjusting a location of the ring member
342 relative
to the first and second input disks 306 and 308 of the input drive mechanism
302, and the
first and second output disks 330 and 332 of the output drive mechanism 304.
[0097] The ring member 342 may include a pair of interconnected co-rotating
rings. The
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co-rotating rings may include an input traction ring 346 that engages the
first and second
input disks 306 and 308, and an output traction ring 348 that engages the
first and second
output disks 330 and 332. A generally cylindrical-shaped connecting ring 350
may fixedly
connect the input traction ring 346 to the output traction ring 348. The input
and output
traction rings 346 and 348 may be arranged substantially perpendicular to the
input and
output disk access of rotation 328 and 310.
[0098] The input traction ring 346 may include a first traction surface 352
engageable
with the first input disk traction surface 314 of the first input disk 306,
and a second traction
surface 354 engageable with the second input disk traction surface 308. The
input traction
ring first and second traction surfaces 352 and 354 may be configured as a
continuous ring.
The input traction ring first and second traction surfaces 352 and 354 may be
located at a
radius 356 from a ring member axis of rotation 355. The input traction ring
first and second
traction surfaces 352 and 354 are arranged on opposite sides of the input
traction ring 346,
with the first traction surface 352 facing the first input disk 306 and the
second traction
surface 354 facing the second input disk 308.
[0099] The output traction ring 348 may include a first traction surface
358 engageable
with the first output disk traction surface 336 of the first output disk 330,
and a second
traction surface 360 engageable with the second output disk traction surface
340. The output
traction ring first and second traction surfaces 358 and 360 may be configured
as a
continuous ring. The output traction ring first and second traction surfaces
358 and 360 may
be located at a radius 362 from the ring member axis of rotation 355. The
output traction
ring first and second traction surfaces 358 and 360 are arranged on opposite
sides of the
output traction ring 348, with the first traction surface 358 facing the first
output disk 330 and
the second traction surface 360 facing the second output disk 332.
[00100] The continuously variable transmission 300 operates to transfer torque
from the
input shaft 42 to the output shaft 44. Torque from the input shaft 42 may be
transferred from
the first input disk 306 to the ring member 342 across a first input contact
patch 364 where
the input traction ring first traction surface 352 engages the first input
disk traction surface
314. For configurations in which the input shaft 42 is rotatably fixed to the
input outer shaft
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326, for example, by means of spline, torque from the input shaft 42 may be
transferred to the
ring member 342 across a second input contact patch 366 where the input
traction ring
second traction surface 354 engages the second input disk traction surface
322. The first and
second input contact patches 364 and 366 are located at a radius 368 from the
input disk axis
of rotation 310. The radius 368 of the first and second input contact patches
364 and 366
varies as the speed ratio of the continuously variable transmission 300 is
varied.
[00101] The ring member 342 transfers torque from the input drive mechanism
302 to the
output drive mechanism 304. Torque may be transferred from the ring member 342
to the
first output disk 330 across a first output contact patch 370 where the output
traction ring first
traction surface 358 engages the first output disk traction surface 336.
Torque may be
transferred from the ring member 342 to the second output disk 332 across a
second output
contact patch 372 where the output traction ring second traction surface 360
engages the
second output disk traction surface 340. The first and second output contact
patches 370 and
372 are located at a radius 374 from the output disk axis of rotation 328. The
radius 374 of
the first and second output contact patches 370 and 372 varies as the speed
ratio of the
continuously variable transmission 300 is varied. Torque transferred from the
ring member
342 to first output disk 330 may be output through the output outer shaft 333.
[00102] For configurations in which the output shaft 44 is rotatably fixed to
the output
outer shaft 333, for example, by means of spline, torque from the output outer
shaft 333 may
be transferred across the connection between the two shafts to the output
shaft 44.
Alternatively, torque from the output shaft 44 may be transferred across the
connection
between the two shafts to the output outer shaft 333.
[00103] The speed ratio of the continuously variable transmission 300 is a
function of the
radial location 368 of the first and second input contact patches 364 and 366,
and the radial
location 374 of the first and second output contact patches 370 and 372. The
speed ratio of
the continuously variable transmission 300 is partially determined by the
radial location at
which the input traction ring first and second traction surfaces 352 and 354
engage the first
and second input disk traction surfaces 314 and 322, respectively (i.e., the
radial location 368
of the first and second input contact patches 364 and 366). The rotational
speed of the output
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shaft 44 increases, relative to the rotational speed of the input shaft 42, as
the radial location
368 of the first and second input contact patches 364 and 366 increases. On
the other hand,
the rotational speed of the output shaft 44 decreases as the radial location
368 of the first and
second input contact patches 364 and 366 decreases. The radial location at
which the output
traction ring first and second traction surfaces 370 and 372 engage the first
and second output
disk traction surfaces 336 and 340, respectively (i.e., the radial location
374 of the first and
second output contact patches 370 and 372) has the opposite effect. The
rotational speed of
the output shaft 44 increases, relative to the rotational speed of the input
shaft 42, as the
radial location 374 of the first and second output contact patches 370 and 372
decreases. On
the other hand, the rotational speed of the output shaft 44 decreases as the
radial location 374
of the first and second output contact patches 370 and 372 increases.
[00104] The speed ratio may be selectively adjusted by moving the location of
the ring
member axis of rotation 355 relative to the input disk axis of rotation 310
and/or the output
disk axis of rotation 328, which effects the radial location 368 at which the
ring member 342
engages the first and second input disks 306 and 308, and the radial location
374 at which the
ring member 342 engages the first and second output disks 330 and 332. Moving
the ring
member 342 radially relative to the first and second input disks 304 and 306
results in
corresponding movement of the ring member 342 relative to the first and second
output disks
330 and 332. For example, moving the ring member 342 radially outward relative
to the first
and second input disks 306 and 308 also moves the ring member 342 radially
inward relative
to the first and second output disks 330 and 332. On the other hand, moving
the ring member
342 radially inward relative to the first and second input disks 306 and 308
also moves the
ring member 342 radially outward relative to the first and second output disks
330 and 332.
[00105] With continued reference to FIG. 11, the first input contact patch 364
is aligned
substantially perpendicular to a first input contact patch vector 376
extending from the first
input contact patch 364 to the input disk axis of rotation 310, and aligned
substantially
perpendicular to a second input contact patch vector 378 extending from the
first input
contact patch 364 to the ring member axis of rotation 355. Similarly, the
first output contact
patch 370 is aligned substantially perpendicular to a first output contact
patch vector 380
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extending from the first output contact patch 370 to the output disk axis of
rotation 328, and
aligned substantially perpendicular to a second output contact patch vector
382 extending
from the first output contact patch 370 to the ring member axis of rotation
355. The
configuration and arrangement of the various components of the continuously
variable
transmission 300 is such that a sum of a length of the first input contact
patch vector 376 and
a length of the first output contact patch vector 380 is greater than a length
of the second
input contact patch vector 378 and a length of the second output contact patch
vector 382.
The following relationship holds true for all speed ratios:
A. ((length of first input contact patch vector 376) + (length of first
output
contact patch vector 380)) > (length of second input contact patch vector
378); and
B. ((length of first input contact patch vector 376) + (length of first
output
contact patch vector 380)) > (length of second output contact patch vector
382)
[00106] A similar relationship also holds true for the second input contact
patch 366 and
the second output contact patch 372. For example, a sum of a length of a first
input contact
patch vector length extending from the second input contact patch 366 to the
input disk axis
of rotation 310 and aligned substantially perpendicular to the second input
contact patch 366,
and a length of a first output contact patch vector length extending from the
second output
contact patch 372 to the output disk axis of rotation 328 and aligned
substantially
perpendicular to the second output contact patch 372 is greater than at least
one of a length of
a second input contact patch vector length extending from the second input
contact patch 366
to the ring member axis of rotation 355 and aligned substantially
perpendicular to the second
input contact patch 366, and a length of a second output contact patch vector
length
extending from the second output contact patch 372 to the ring member axis of
rotation 355
and aligned substantially perpendicular to the second output contact patch
372.
[00107] With reference to FIGS. 11 and 12, the speed ratio selector 344 may
be used to
selectively adjust the speed ratio of the continuously variable transmission
300. FIG. 11
illustrates the speed ratio selector 344 arranged in a first speed ratio
position. In this position
the ring member 342 engages the first and second output disks 330 and 332 near
their
respective outer edges 334 and 338, and the ring member 342 engages the first
and second
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input disks 306 and 308 closer toward the input disk axis of rotation 310.
This arrangement
produces the lowest speed ratio (e.g., speed ratio = (rotational speed of
output shaft 44)
(rotational speed of input shaft 42)), wherein the output shaft 44 has a lower
rotational speed
than the input shaft 42.
[00108] FIG. 12 illustrate the speed ratio selector 344 arranged in a second
speed ratio
position. In this position the ring member 342 engages the first and second
input disks 306
and 308 near their respective outer edges 312 and 320, and the ring member 346
engages the
first and second output disks 330 and 332 closer toward the output disk axis
of rotation 328.
This arrangement produces the highest speed ratio, wherein the output shaft 44
has a higher
rotational speed than the input shaft 42. The speed ratio selector 60 may be
infinitely
adjustable between the first speed ratio position (for example, as illustrated
in FIG. 11) and
the second speed ratio position (for example, as illustrated in FIG. 12).
[00109] As described previously, input biasing mechanism 329 and output
biasing
mechanism 341 may include various configurations. An example of one such
configuration
is illustrated in FIGS. 13 and 14, which includes a hydraulic system used to
produce the
biasing force for controlling the traction forces generated between the ring
member 342 and
the first and second input disks 306 and 308 and the first and second output
disks 330 and
332. This particular configuration of the input and output biasing mechanisms
329 and 341
utilizes hydraulic pressure to generate a biasing force for urging the second
input disk 308
toward the first output disk 306 and the second output disk 332 toward the
first output disk
330. Input biasing mechanism 329 may include a hydraulic reservoir 384
configured to exert
a biasing force against the second input disk 308. The hydraulic reservoir 384
may be
defined by a rear surface 385 of the second input disk 308 and a cover 386
positioned
adjacent the second input disk 308. The second input disk 308 may slideably
engage the
input shaft 42. The cover 386 may include a generally cylindrically-shaped
flange 387 that
slideably engages a generally cylindrically-shaped flange 388 extending from
the rear surface
385 of the second input disk 308. A seal 389, such as an 0-ring, may be
disposed between
the flange 387 of the cover 386 and the flange 388 of the second input disk
308 to prevent
hydraulic fluid from escaping hydraulic reservoir 384. A seal 390 may be
employed to seal
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an opening that may occur between the cover 386 and the input shaft 42 and an
opening that
may occur between the second input disk 308 and the input shaft 42.
[00110] The output biasing mechanisms 341 may be similarly configured as the
input
biasing mechanism 329. For example, the output biasing mechanism 341 may
include a
hydraulic reservoir 391 configured to exert a biasing force against the second
output disk
332. The hydraulic reservoir 391 may be defined by a rear surface 392 of the
second output
disk 330 and a cover 393 positioned adjacent the second output disk 330. The
second input
disk 330 may slideably engage the output shaft 44. The cover 393 may include a
generally
cylindrically-shaped flange 394 that slideably engages a generally
cylindrically-shaped flange
395 extending from the rear surface 392 of the second output disk 330. Seal
389, such as an
0-ring, may be disposed between the flange 394 of the cover 393 and the flange
395 of the
second output disk 330 to prevent hydraulic fluid from escaping hydraulic
reservoir 391.
Seal 390 may be employed to seal an opening that may occur between the cover
393 and the
output shaft 44 and an opening that may occur between the second output disk
330 and the
output shaft 44.
[00111] A fluid passage 396 may fluidly connect the hydraulic reservoir 384 of
the input
biasing mechanism 329 to the hydraulic reservoir 391of the output biasing
mechanism 341.
A hydraulic pump 397 may be fluidly connected to the fluid passage 396. The
hydraulic
pump 397 operates to control a pressure of the hydraulic fluid present within
the system, and
thus the traction forces generated between the ring member 342 and the first
and second input
disks 306 and 308 and the first and second output disks 330 and 332.
[00112] The input and output biasing mechanisms 329 and 341operate in
conjunction with
one another to provide a generally consistent biasing force. The volume of the
hydraulic
reservoirs 384 and 391 may vary as the speed ratio of the continuously
variable transmission
300 is varied. For example, FIG. 13 illustrates the continuously variable
transmission 300
arranged in the first speed ratio position, and FIG. 14 illustrates the speed
ratio selector 344
arranged in a second speed ratio position. With the speed ratio selector 342
arranged in the
first speed ratio position (i.e., FIG. 13), the ring member 342 engages the
first and second
output disks 330 and 332 near their respective outer edges 334 and 338, and
the ring member
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342 engages the first and second input disks 306 and 308 closer toward the
input disk axis of
rotation 310. This arrangement produces a maximum separation between the first
input disk
306 and the second input disk 308, and a minimum separation between the first
output disk
330 and the second output disk 332. With the speed ratio selector 342 arranged
in the second
speed ratio position (i.e., FIG. 14), the ring member 342 engages the first
and second input
disks 306 and 308 near their respective outer edges 312 and 320, and the ring
member 346
engages the first and second output disks 330 and 332 closer toward the output
disk axis of
rotation 328. This arrangement produces a minimum separation between the first
input disk
306 and the second input disk 308, and a maximum separation between the first
output disk
330 and the second output disk 332.
[00113] Selectively moving the ring member 342 from the first speed ratio
position (i.e.,
FIG. 13) toward the second speed ratio position (i.e., FIG. 14) causes the
second input disk
308 to move toward the first input disk 306 and thereby increase the volume of
the hydraulic
reservoir 384, and the second output disk 332 to move away from the first
output disk 330,
and thereby decrease the volume of the hydraulic reservoir 391. On the other
hand, moving
the ring member 342 from the second speed ratio position (i.e., FIG. 14)
toward the first
speed ratio position (i.e., FIG. 13) causes the second input disk 308 to move
away from the
first input disk 306 and thereby increase the volume of the hydraulic
reservoir 384, and the
second output disk 332 to move toward the first output disk 330 and thereby
decrease the
volume of the hydraulic reservoir 391. Hydraulic fluid may be transferred back
and forth
between the hydraulic reservoir 384 and hydraulic reservoir 391 through fluid
passage 396 as
the ring member 342 is cycled between the various speed ratio positions.
[00114] With reference to FIG. 15, an alternately configured exemplary
continuously
variable transmission 400 is operable for transferring rotational energy
between the input
shaft 42 and the output shaft 44. The input shaft 42 is rotatable about the
input axis of
rotation 46 and the output shaft 44 is rotatable about the output axis of
rotation 48. The input
axis of rotation 46 may be arranged substantially parallel to the output axis
of rotation 48.
The input axis of rotation 46 may be offset from the output axis of rotation
48 by the distance
50. The input and output shafts 42 and 44, respectively, may each be rotatably
supported
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within the housing 52 by bearings 54. The position and orientation of the
input shaft 42 is
generally fixed relative to the output shaft 44.
[00115] The continuously variable transmission 400 may include an input drive
mechanism 402 and an output drive mechanism 404 spaced from the input drive
mechanism
402. The input and output drive mechanisms 402 and 404 may be arranged in
series. The
input and output drive mechanisms 402 and 404, respectively, operate in
conjunction with
one another to transfer rotational torque from the input shaft 42 to the
output shaft 44.
[00116] The input drive mechanism 402 may employ an input disk 406 rotatable
about the
input axis of rotation 46. The input disk 406 may be fixedly attached or
integrally formed
with the input shaft 42. The input disk 406 extends generally radially outward
from the input
axis of rotation 46. An edge 408 defines an outer circumferential perimeter of
the input disk
406. The input disk 406 may include a generally convex conically-shaped input
disk first
traction surface 410 and an opposite input disk second traction surface 412.
The input disk
first and second traction surfaces 410 and 412 may be generally configured as
mirror
opposites when viewed from the perspective of FIG. 15.
[00117] The output drive mechanism 404 may be similarly configured as the
input drive
mechanism 402, and may include for example, an output disk 414 rotatable about
the output
axis of rotation 48. The output disk 414 may be fixedly attached or integrally
formed with
the output shaft 48. The output disk 414 extends generally radially outward
from the output
axis of rotation 48. An edge 416 defines an outer circumferential perimeter of
the output disk
414. The output disk 414 may include a generally convex conically-shaped
output disk first
traction surface 418 and an opposite output disk second traction surface 420.
The output disk
first and second traction surfaces 418 and 420 may be generally configured as
mirror
opposites when viewed from the perspective of FIG. 15.
[00118] The continuously variable transmission 400 may include a ring member
422
operably connecting the input drive mechanism 402 to the output drive
mechanism 404. The
ring member 422 may be moved radially relative to the input drive mechanism
402 and the
output drive mechanism 404. The radial location of the ring member 422 may be
selectively
adjusted relative to the input and output drive mechanisms 402 and 404 to vary
the speed
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ratio (e.g., speed ratio = (rotational speed of output shaft 44) (rotational
speed of input shaft
42)) of the continuously variable transmission 400.
[00119] The ring member 422 may include a pair of interconnected co-rotating
rings. The
co-rotating rings may include an input traction ring 426 that engages the
input disk first
traction surface 410, and an output traction ring 428 that engages the output
disk first traction
surface 418. A generally cylindrical-shaped connecting ring 430 may fixedly
connect the
input traction ring 426 to the output traction ring 428. The input and output
traction rings
426 and 428 may be arranged substantially parallel to one another and
substantially
perpendicular to the input and output axis of rotation 46 and 48.
[00120] The input traction ring 426 may include an input ring traction surface
432
engageable with the input disk first traction surface 410. The input ring
traction surface 432
may be configured as a continuous ring. The input ring traction surface 432
may be located
at a radius 434 from a ring member axis of rotation 436.
[00121] The output traction ring 428 may include an output ring traction
surface 438
engageable with the output disk first traction surface 418. The output ring
traction surface
438 may be configured as a continuous ring. The output ring traction surface
428 may be
located at a radius 440 from the ring member axis of rotation 436. The output
ring traction
surface 438 and the input ring traction surface 432 may be arranged at
opposite axial ends of
the ring member 422, with the input ring traction surface 432 generally facing
the output ring
traction surface 438.
[00122] With reference to FIGS. 15 and 16, the continuously variable
transmission 400
may include an intermediate traction ring 442 disposed between the input
traction ring 426
and the output traction ring 428. The intermediate traction ring 442 may be
generally
configured as an annular disk having an outer circumference 444 and an inner
circumference
446. The intermediate traction ring 442 may be aligned generally parallel to
the input and
output traction rings 426 and 428 and substantially perpendicular to the ring
member axis of
rotation 436. The outer circumference 446 may include a helical spline 448, or
similar
connecting mechanism, that slideably engages a corresponding connecting
mechanism, for
example a helical spline 450, located on an inner circumference 452 of the
connecting ring
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430. The helical splines 448 and 450 enable the intermediate traction ring 442
to move
axially along an axial path of travel (i.e., along ring member axis of
rotation 436) relative to
the ring member 422 while maintaining the angular orientation of the
intermediate traction
ring relative to the input and output traction rings 426 and 428 and the ring
member axis or
rotation 436. The helical splines 448 and 450 operate to rotatably fix the
intermediate
traction ring 442 to the ring member 422, thereby causing the intermediate
traction ring to
rotate in substantial unison with the input and output traction rings 426 and
428.
[00123] With reference to FIGS. 15 and 17, moving ring member 422 radially
along radial
path of travel 455 causes a corresponding axial movement of ring member 422
and
intermediate traction ring 442 in opposite directions along axial path of
travel 451. For
example, moving ring member 422 radially upward as viewed from the perspective
of FIGS.
15 and 17) from the radial position illustrated in FIG. 17 to the radial
position illustrated in
FIG. 15 causes input traction ring 426 to move rightward (as viewed from the
perspective of
FIGS. 15 and 17) as input ring traction surface 432 travels radially outward
along input disk
first traction surface 410 and output ring traction surface 438 travels
radially inward along
output disk first traction surface 418. This also causes intermediate traction
ring 442 to move
leftward (as viewed from the perspective of FIGS. 15 and 17) as intermediate
input traction
surface 454 travels radially outward along input disk second traction surface
412 and
intermediate output traction surface 456 travels radially inward along output
disk second
traction surface 420. Moving ring member 422 radially downward (as viewed from
the
perspective of FIGS. 15 and 17) causes input traction ring 426, output
traction ring 438 and
the intermediate traction ring 442 to move axially along axial path of travel
451 in a direction
opposite the direction when moving the ring member 422 radially upward.
[00124] The intermediate traction ring 442 may include an intermediate input
traction
surface 454 engageable with the input disk second traction surface 412. The
intermediate
input traction surface 454 may be configured as a continuous ring. The
intermediate input
traction surface 454 may be located at a radius 458 from the ring member axis
of rotation
436.
[00125] The intermediate traction ring 442 may include an intermediate
output traction
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surface 456 engageable with the output disk second traction surface 420. The
intermediate
output traction surface 456 may be configured as a continuous ring. The
intermediate output
traction surface 456 may be located at the radius 458 from the ring member
axis of rotation
436. The intermediate output traction surface 458 and the intermediate input
traction surface
454 may be arranged on opposite sides of the intermediate traction ring 442,
with the
intermediate input traction surface 454 generally facing in an opposing
direction of the
intermediate output traction surface 456.
[00126] The ring member 422 may be moved radially along a radial path of
travel 455
relative to the input drive mechanism 402 and the output drive mechanism 404.
The radial
location of the ring member 422 may be selectively adjusted relative to the
input and output
drive mechanisms 402 and 404 to vary the speed ratio (e.g., speed ratio =
(rotational speed of
output shaft 44) (rotational speed of input shaft 42)) of the continuously
variable
transmission 400.
[00127] A speed ratio selector 460 may be operably connected to the ring
member 422 to
selectively adjust the speed ratio of the continuously variable transmission
400. The speed
ratio selector 460 operates to adjust the radial location of the ring member
422 relative to the
input and output drive mechanisms 402 and 404 to achieve a selected speed
ratio. The speed
ratio selector 460 may have any of a wide variety of configurations. The speed
ratio selector
460 may employ any device capable of adjusting a location of the ring member
460 relative
to the input disk 406 of the input drive mechanism 402, and the output disk
414 of the output
drive mechanism 404.
[00128] The continuously variable transmission 400 operates to transfer torque
from the
input shaft 42 to the output shaft 44. Torque from the input shaft 42 may be
transferred from
the input disk 406 to the ring member 422 across a first input contact patch
462 where the
input ring traction surface 432 engages the input disk first traction surface
410.
[00129] Torque may be transferred from the ring member 422 to the output disk
414
across a first output contact patch 468 where the output ring traction surface
438 engages the
output disk first traction surface 418. Torque transferred from the ring
member 422 to output
disk 414 may be output through the output shaft 44.
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[00130] Torque from the input shaft 42 may also be transferred from the input
disk 406
through the intermediate traction ring 442 to the output disk 414. Torque from
the input disk
406 may be transmitted across a second input contact patch 474 where the
intermediate input
traction surface 454 of the intermediate traction ring 442 engages the input
disk second
traction surface 412. Torque may be transferred from the intermediate traction
ring 442 to
the output disk 414 across a second output contact patch 476 where the
intermediate output
traction surface 456 of the intermediate traction ring 442 engages the output
disk second
traction surface 420. The first and second input contact patches 462 and 474
are located at a
radius 478 from the input axis of rotation 46. The first and second output
contact patches
468 and 476 are located at a radius 480 from the output axis of rotation 48.
The radius 478 of
the first and second input contact patches 462 and 474, and the radius 480 of
the first and
second output contact patches 468 and 476 varies as the speed ratio of the
continuously
variable transmission 400 is varied.
[00131] The input and output shafts 42 and 44 exert their respective torques
on the input
disk first and second traction surfaces 410 and 412 and the output disk first
and second
traction surfaces 418 and 420, respectively. The torques generate equal and
opposite forces
at the first input and output contact patches 462 and 468 and the second input
and output
contact patches 474 and 476. The forces may be transmitted from the input disk
406 to the
output disk 414 by traction contact between the input and output disks 406 and
414 and the
ring member 422.
[00132] The traction forces generated at the input first input contact patch
462 and the first
output contact patch 468 includes a radial component that urges the ring
member 422 tightly
into contact with the input and output disks 406 and 414 to help maintain a
position of the
ring member 422 relative to the input and output disks 406 and 414. A
tangential component
transmits a tractive force between the ring member 422 and the input and
output disks 406
and 414. A normal component is dependent on the geometry of the input and
output disks
406 and 414 and a circumferential location of the contact patches 462 and 468
relative to one
another, and is generally adequate to prevent slippage between the input and
output disks 406
and 414 and the ring member 422. The input disk second traction surface 412
and output
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disk second traction surface 420 experiences a set of forces that balance the
forces on the
opposite input disk first traction surface 410 and the output disk first
traction surface 418.
[00133] The vector component forces (i.e., radial, tangential and normal)
acting at the first
and second input contact patches 462 and 474 and the first and second output
contact patches
468 and 476 generally balance to produce a net zero force. The opposing forces
tend to cause
the ring member 422 and intermediate traction ring 442 to pinch the input and
output disks
406 and 414 to produce sufficient clamping force between the ring member 422
and
intermediate traction ring 442 and the input and output disks 406 and 414 to
accomplish
traction without slip.
[00134] The speed ratio of the continuously variable transmission 400 is a
function of the
radial location 478 of the first and second input contact patches 462 and 474,
and the radial
location 480 of the first and second output contact patches 468 and 476. The
speed ratio of
the continuously variable transmission 400 is partially determined by the
radial location at
which the input ring traction surface 432 engages the input disk first
traction surface 410 and
the radial location at which the intermediate input traction surface 454
engages the input disk
second traction surface 412 (i.e., the radial location 478 of the first and
second input contact
patches 462 and 474). The rotational speed of the output shaft 44 increases,
relative to the
rotational speed of the input shaft 42, as the radial location 478 of the
first and second input
contact patches 462 and 474 increases. On the other hand, the rotational speed
of the output
shaft 44 decreases as the radial location 478 of the first and second input
contact patches 462
and 474 decreases.
[00135] The radial location at which the output ring traction surface 438
engages the
output disk first traction surface 418 and the radial location at which the
intermediate output
traction surface 456 engages the output disk second traction surface 420
(i.e., the radial
location 480 of the first and second output contact patches 468 and 476) has a
compounding
influence on speed ratio. The rotational speed of the output shaft 44
increases, relative to the
rotational speed of the input shaft 42, as the radial location 480 of the
first and second output
contact patches 468 and 476 decreases. On the other hand, the rotational speed
of the output
shaft 44 decreases as the radial location 480 of the first and second output
contact patches
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468 and 476 increases.
[00136] The speed ratio may be selectively adjusted by moving the location of
the ring
member axis of rotation 436 relative to the input axis of rotation 46 and/or
the output axis of
rotation 48, which effects the radial location 478 at which the ring member
422 engages the
input disk 406, and the radial location 480 at which the ring member 422
engages the output
disk 414. Moving the ring member 422 radially relative to the input disk 406
results in
corresponding movement of the ring member 422 relative to the output disk 414.
For
example, moving the ring member 422 radially outward relative to the input
disk 406 also
moves the ring member 422 radially inward relative to the output disk 414. On
the other
hand, moving the ring member 422 radially inward relative to the input disk
406 also moves
the ring member 422 radially outward relative to the output disk 414.
[00137] With continued reference to FIG. 15, the first input contact patch 462
is aligned
substantially perpendicular to a first input contact patch vector 482
extending from the first
input contact patch 462 to the input axis of rotation 46, and aligned
substantially
perpendicular to a second input contact patch vector 484 extending from the
first input
contact patch 462 to the ring member axis of rotation 436. Similarly, the
first output contact
patch 468 is aligned substantially perpendicular to a first output contact
patch vector 486
extending from the first output contact patch 468 to the output axis of
rotation 48, and
aligned substantially perpendicular to a second output contact patch vector
488 extending
from the first output contact patch 468 to the ring member axis of rotation
436. The
configuration and arrangement of the various components of the continuously
variable
transmission 400 is such that a sum of a length of the first input contact
patch vector 482 and
a length of the first output contact patch vector 486 is greater than a length
of the second
input contact patch vector 484 and a length of the second output contact patch
vector 488.
The following relationship holds true for all speed ratios:
A. ((length of first input contact patch vector 482) + (length of first
output
contact patch vector 486)) > (length of second input contact patch vector
484); and
B. ((length of first input contact patch vector 482) + (length of first
output
contact patch vector 486)) > (length of second output contact patch vector
488)
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[00138] A similar relationship also holds true for the second input contact
patch 474 and
the second output contact patch 476. For example, a sum of a length of a first
input contact
patch vector length extending from the second input contact patch 474 to the
input axis of
rotation 46 and aligned substantially perpendicular to the second input
contact patch 474, and
a length of a first output contact patch vector length extending from the
second output contact
patch 476 to the output axis of rotation 48 and aligned substantially
perpendicular to the
second output contact patch 476 is greater than at least one of a length of a
second input
contact patch vector length extending from the second input contact patch 474
to the ring
member axis of rotation 436 and aligned substantially perpendicular to the
second input
contact patch 474, and a length of a second output contact patch vector length
extending from
the second output contact patch 476 to the ring member axis of rotation 436
and aligned
substantially perpendicular to the second output contact patch 476.
[00139] With reference to FIGS. 15 and 17, the speed ratio selector 460 may
be used to
selectively adjust the speed ratio of the continuously variable transmission
400. FIG. 15
illustrates the speed ratio selector 460 arranged in a first speed ratio
position. In this position
the ring member 422 engages the input disk 406 near its respective outer edge
408, and the
ring member 422 engages the output disk 414 closer toward the output axis of
rotation 48.
This arrangement produces the highest speed ratio (e.g., speed ratio =
(rotational speed of
output shaft 44) (rotational speed of input shaft 42)), wherein the output
shaft 44 has a
higher rotational speed than the input shaft 42.
[00140] FIG. 17 illustrate the speed ratio selector 460 arranged in a second
speed ratio
position. In this position the ring member 422 engages the output disk 414
near its outer
edge 416, and the ring member 422 engages the input disk 406 closer toward the
input axis of
rotation 46. This arrangement produces the lowest speed ratio, wherein the
output shaft 44
has a lower rotational speed than the input shaft 42. The speed ratio selector
460 may be
infinitely adjustable between the first speed ratio position (for example, as
illustrated in FIG.
15) and the second speed ratio position (for example, as illustrated in FIG.
17).
[00141] With reference to FIG. 18, an alternately configured exemplary
continuously
variable transmission 700 is operable for transferring rotational energy
between input shaft 42
42
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and the output shaft 44. Continuously variable transmission 700 is similarly
configured as
continuously variable transmission 400, but utilizes an alternate mechanism
for controlling
alignment of an intermediate traction ring 702 and a ring member 706 relative
to input disk
406 and output disk 414. Intermediate traction ring 702 and ring member 706
operably
connect input drive mechanism 402 to output drive mechanism 404. Ring member
706 and
intermediate traction ring 702 may be selectively moved in unison radially
relative to the
input drive mechanism 402 and the output drive mechanism 404. The radial
location of the
ring member 706 and the intermediate traction ring 702 may be selectively
adjusted relative
to the input and output drive mechanisms 402 and 404 to vary the speed ratio
(e.g., speed
ratio = (rotational speed of output shaft 44) (rotational speed of input
shaft 42)) of the
continuously variable transmission 700.
[00142] The ring member 706 may include a pair of interconnected co-rotating
rings. The
co-rotating rings may include an input traction ring 708 that engages the
input disk first
traction surface 410, and an output traction ring 710 that engages the output
disk first traction
surface 418. The input and output traction rings 708 and 710 may be arranged
substantially
parallel to one another and substantially perpendicular to the input and
output axis of rotation
46 and 48.
[00143] Input traction ring 708 may include a generally cylindrical-shaped
input traction
ring support 712 extending laterally outward from input traction ring 708.
Output traction
ring 710 may include an output traction ring support 714 extending laterally
outward from
output traction ring 710. Output traction ring support 714 may be sized larger
(i.e., have a
larger diameter) than input traction ring support 712. Output traction ring
support 714
extends around and at least partially overlays input traction ring support
712. An inner
circumference 716 of output traction ring support 714 may have a larger
diameter than a
diameter of an outer circumference 718 of input traction ring support 712,
thereby forming a
circumferential annulus 720 between input traction ring support 712 and output
traction ring
support 714. Input and output traction ring supports 712 and 714 may be
fixedly connected
to one another by a radial connector 722 to cause input traction ring 708 and
output traction
ring 710 to rotate in unison.
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[00144] The input traction ring 708 may include an input ring traction surface
724
engageable with the input disk first traction surface 410. The input ring
traction surface 724
may be configured as a continuous ring.
[00145] The output traction ring 710 may include an output ring traction
surface 726
engageable with the output disk first traction surface 418. The output ring
traction surface
726 may be configured as a continuous ring. The output ring traction surface
726 and the
input ring traction surface 724 may be arranged so as to generally face one
another.
[00146] With reference to FIGS. 15 and 16, the continuously variable
transmission 700
may include the intermediate traction ring 702 disposed between the input
traction ring 708
and the output traction ring 710. The intermediate traction ring 702 may be
generally
configured as an annular disk having an outer circumference 728 and an inner
circumference
730. The intermediate traction ring 702 may be aligned generally parallel to
the input and
output traction rings 708 and 710 and substantially perpendicular to the ring
member axis of
rotation 732. The outer circumference 728 may include a generally cylindrical-
shaped input
traction ring support 734 extending laterally outward from intermediate
traction ring 702.
Intermediate traction ring support 734 at least partially extends into the
annulus 720 formed
between output traction ring support 714 and input traction ring support 712.
An outer
circumference 736 of intermediate traction ring support 734 may slideably
engage the inner
circumference 716 of output traction ring support 714. This arrangement
enables the
intermediate traction ring 702 to move axially (i.e., along ring member axis
of rotation 732)
relative to the ring member 706 while maintaining the angular orientation of
the intermediate
traction ring 734 relative to the input and output traction rings 708 and 710
and the ring
member axis or rotation 732. Alternatively, an inner circumference 738 of
intermediate
traction ring support 734 may slideably engage the outer circumference 718 of
input traction
ring support 712.
[00147] The intermediate traction ring 702 may include an intermediate input
traction
surface 740 engageable with the input disk second traction surface 412. The
intermediate
input traction surface 740 may be configured as a continuous ring.
[00148] The intermediate traction ring 702 may include an intermediate
output traction
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surface 742 engageable with the output disk second traction surface 420. The
intermediate
output traction surface 742 may be configured as a continuous ring. The
intermediate output
traction surface 742 and the intermediate input traction surface 740 may be
arranged on
opposite sides of the intermediate traction ring 702, with the intermediate
input traction
surface 740 generally facing in an opposing direction of the intermediate
output traction
surface 742.
[00149] With continued reference to FIGS. 18 and 19, moving ring member 706
radially
along radial path of travel 455 causes a corresponding axial movement of ring
member 422
and intermediate traction ring 442 in opposite directions along axial path of
travel 451. For
example, moving ring member 422 radially upward (as viewed from the
perspective of FIGS.
18 and 19) from the radial position illustrated in FIG. 19 to the radial
position illustrated in
FIG. 18 causes input traction ring 708 to move rightward (as viewed from the
perspective of
FIGS. 18 and 19) as input ring traction surface 724 travels radially outward
along input disk
first traction surface 410 and output ring traction surface 726 travels
radially inward along
output disk first traction surface 418. This also causes intermediate traction
ring 702 to move
leftward (as viewed from the perspective of FIGS. 18 and 19) as intermediate
input traction
surface 740 travels radially outward along input disk second traction surface
412 and
intermediate output traction surface 742 travels radially inward along output
disk second
traction surface 420. Moving ring member 706 radially downward (as viewed from
the
perspective of FIGS. 18 and 19) causes input traction ring 708, output
traction ring 710 and
the intermediate traction ring 702 to move axially along axial path of travel
451 in a direction
opposite the direction when moving the ring member 706 radially upward.
[00150] The ring member 706 may be moved radially along path of travel 455
relative to
the input drive mechanism 402 and the output drive mechanism 404. The radial
location of
the ring member 706 may be selectively adjusted relative to the input and
output drive
mechanisms 402 and 404 to vary the speed ratio (e.g., speed ratio =
(rotational speed of
output shaft 44) (rotational speed of input shaft 42)) of the continuously
variable
transmission 700.
[00151] The speed ratio selector 460 may be operably connected to the ring
member 706
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to selectively adjust the speed ratio of the continuously variable
transmission 700. The speed
ratio selector 460 operates to adjust the radial location of the ring member
706 relative to the
input and output drive mechanisms 402 and 404 to achieve a selected speed
ratio. The speed
ratio may be selectively adjusted by moving the location of the ring member
axis of rotation
473 relative to the input axis of rotation 46 and/or the output axis of
rotation 48, which
effects the radial locations at which the ring member 706 engages the input
disk 406 and the
output disk 414. Moving the ring member 706 radially relative to the input
disk 406 results
in corresponding movement of the ring member 706 relative to the output disk
414. For
example, moving the ring member 706 radially outward relative to the input
disk 406 also
moves the ring member 706 radially inward relative to the output disk 414. On
the other
hand, moving the ring member 706 radially inward relative to the input disk
406 also moves
the ring member 706 radially outward relative to the output disk 414
[00152] A common feature between the various exemplary configurations of the
continuously variable transmission, among others, is that the sum of the input
and output
contact patch vector lengths (for example, a length of first input contact
patch vector 154 and
first output contact patch vector 158, as illustrated in FIG. 2) is greater
than the lengths of
corresponding ring member vectors 156 and 160 (for example, input ring member
102 as
illustrated in FIG. 2). Also, each of the exemplary configurations depict the
ring members as
having their respective traction surfaces (for example, input ring first
traction surface 112, as
illustrated in FIG. 1) positioned at a fixed radius, whereas the radius of the
corresponding
disk traction surface (for example, first input disk traction surface 68, as
illustrated in FIG. 1)
varies, as this arrangement may generally provide the greatest range of drive
ratios.
Alternatively, the radial location of the disk traction surface may be fixed
and the radial
location of the ring traction surface may be allowed to vary as the means for
adjusting the
drive ratio.
[00153] With reference to FIGS. 20 and 21, an exemplary two-stage continuously
variable
transmission 500 is operable for transferring rotational energy between the
input shaft 42 and
the output shaft 44. The two-stage continuously variable transmission 500 may
include a
first drive mechanism 502 and a second drive mechanism 504. The first and
second drive
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mechanisms 502 and 504 may be arranged in series. The first and second drive
mechanisms
502 and 504 operate to transfer rotational torque from the input shaft 42 to
the output shaft
44. The first and second drive mechanisms 502 and 504 may be selectively
adjusted to vary a
speed ratio (e.g., speed ratio = (rotational speed of output shaft 44)
(rotational speed of
input shaft 42)) of the tow-stage continuously variable transmission 500. The
two-stage
continuously variable transmission 500 may employ a speed ratio selector 506
operable to
selectively adjust the speed ratio.
[00154] The first drive mechanism 502 may be fixedly attached to the input
shaft 42 and
the second drive mechanism 504 may be fixedly attached to the output shaft 44.
An
intermediate shaft 508 operably connects the first drive mechanism 502 to the
second drive
mechanism 504. The input shaft 42 and the output shaft 44 are rotatable about
a common
axis of rotation 510. The position and orientation of the input shaft 42 is
generally fixed
relative to the output shaft 44.
[00155] The first drive mechanism 502 may employ a first input disk 512 and a
first output
disk 514 positioned adjacent the first input disk 512. The first input and
output disks 512 and
514 are each rotatable about the axis of rotation 510. The first input and
output disks 512 and
514 extend generally radially outward from the axis of rotation 510. An edge
516 defines an
outer circumferential perimeter of the first input disk 512. The first input
disk 512 may
include a first input disk traction surface 520 positioned adjacent input
shaft 42 and an
opposite inner surface 522 positioned adjacent the first output disk 514. The
inner surface
522 of the first input disk 62 may have generally planar surface contour, as
illustrated, for
example, in FIG. 20, or may include various other shapes and/or contours.
[00156] With continued reference to FIG. 20, an edge 524 defines an outer
circumferential
perimeter of the first output disk 514. The first output disk 514 may include
an inner surface
526 positioned adjacent the first input disk 512 and a first output disk
traction surface 528
located opposite the inner surface 526. The first output disk 514 may be
generally configured
as a mirror image of the first input disk 512 when viewed from the perspective
of FIG. 20.
Similar to first input disk 512, the inner surface 526 of the first output
disk 514 may have
generally planar surface contour, as illustrated, for example, in FIG. 20, or
may include
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various other shapes and/or contours. The first output disk 514 may be fixedly
attached to
the intermediate shaft 508.
[00157] The first input disk 512 and the first output disk 514 may be
rotatably supported
relative to one another. For example, a bearing 530 may be disposed between
the inner
surface 522 of the first input disk 512 and the inner surface 526 of the first
output disk 514.
The bearing 530 may be integrally formed with the first input disk 512 and the
first output
disk 514, for example, as illustrated in FIG. 20, or may be configured as a
separate
component that attaches to the inner surface 522 of the first input disk 512
and the inner
surface 526 of the first output disk 514.
[00158] The second drive mechanism 504 may be similarly configured as the
first drive
mechanism 502, and may include for example, a second input disk 532 and a
second output
disk 534 positioned adjacent the second input disk 532. The second input disk
532 and the
second output disk 534 are each rotatable about the axis of rotation 510. The
second input
and output disks 532 and 534 extend generally radially outward from the axis
of rotation 510.
[00159] An edge 536 defines an outer circumferential perimeter of the second
input disk
532. The second output disk 534 may include a second input disk traction
surface 538 and an
opposite inner surface 540 positioned adjacent the second output disk 534. The
inner surface
540 of the second input disk 532 may have generally planar surface contour, as
illustrated, for
example, in FIG. 20, or may include various other shapes and/or contours. The
second input
disk 532 may be fixedly attached to the intermediate shaft 508.
[00160] The second output disk 534 may be fixedly attached to the output shaft
44. An
edge 542 defines an outer circumferential perimeter of the second output disk
534. The
second output disk 534 may include an inner surface 544 positioned adjacent
the second
input disk 532 and a second output disk traction surface 546 located opposite
the inner
surface 544. The second output disk 534 may be generally configured as a
mirror image of
the second input disk 532 when viewed from the perspective of FIG. 20. Similar
to second
input disk 532, the inner surface 544 of the second output disk 534 may have a
generally
planar surface contour, as illustrated, for example, in FIG. 20, or may
include various other
shapes and/or contours.
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[00161] The second input disk 532 and the second output disk 534 may be
rotatably
supported relative to one another. For example, the bearing 530 may be
disposed between
the inner surface 540 of the second input disk 532 and the inner surface 544
of the second
output disk 534. The bearing 530 may be integrally formed with the second
input disk 532
and the second output disk 534, for example, as illustrated in FIG. 20, or may
be configured
as a separate component that attaches to the inner surface 540 of the second
input disk 532
and the inner surface 544 of the second output disk 534.
[00162] The first drive mechanism 502 may include a first ring member 548 that
operates
to rotatably couple the first input disk 512 to the first output disk 514. The
first ring member
548 is rotatable about a first ring member axis of rotation 549. The first
ring member axis of
rotation 549 is oriented substantially perpendicular to a plane extending
through a bearing
588 for rotatably supporting the first ring member 548. The first ring member
548 may be
moved radially relative to the first input disk 512 and the first output disk
514. The radial
location of the first ring member 548 may be selectively adjusted relative to
the first input
disk 512 and the first output disk 514 to vary the speed ratio of the first
drive mechanism 502
(e.g., first drive mechanism speed ratio = (rotational speed of output shaft
44) (rotational
speed of the intermediate shaft 508)).
[00163] The second drive mechanism 504 may include a second ring member 550
that
operates to rotatably couple the second input disk 532 to the second output
disk 534. The
second ring member 550 is rotatable about a second ring member axis of
rotation 551. The
second ring member axis of rotation 551 is aligned substantially perpendicular
to a plane
extending through bearing 588 that rotatably supports the second ring member
550. The
second ring member 550 may be moved radially relative to the second input disk
532 and the
second first output disk 534. The radial location of the second ring member
550 may be
selectively adjusted relative to the second input disk 532 and the second
output disk 534 to
vary the speed ratio of the second drive mechanism 504 (e.g., second drive
mechanism speed
ratio = (rotational speed of intermediate shaft 508) (rotational speed of
the output shaft
44)).
[00164] The first ring member 548 may include a pair of interconnected co-
rotating rings.
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The co-rotating rings may include an input traction ring 552 that engages the
first input disk
512, and an output traction ring 554 spaced from the input traction ring 552
and which
engages the first output disk 514. A generally cylindrical-shaped connecting
ring 556 may
fixedly connect the input traction ring 552 to the output traction ring 554.
The input and
output traction rings 552 and 554 extend generally radially inward from the
connecting ring
556.
[00165] The input traction ring 552 may include a first ring member input
traction surface
558 engageable with the first input disk traction surface 520 of the first
input disk 512. The
output traction ring 554 may include a first ring member output traction
surface 560
engageable with the first output disk traction surface 528 of the first output
disk 514. The
first ring member input and output traction surfaces 558 and 560 may be
configured as
continuous rings. The first ring member input traction surface 558 may be
located at a radius
562 from a ring member effective axis of rotation 566. The ring member
effective axis of
rotation 566 may not coincide with the first ring member axis of rotation 549
or the second
ring member axis of rotation 551 depending on the orientation of bearing 588.
Rather, the
first and second ring member axis of rotation 549 and 551 may be oriented at
an oblique
angle relative to the ring member effective axis of rotation 566. The ring
member effective
axis or rotation 566 is aligned substantially parallel to the axis of rotation
510 of input shaft
42 and output shaft 44. The first ring member output traction surface 560 may
be located at a
radius 564 from the ring member effective axis of rotation 566. The first ring
member input
and output traction surfaces 558 and 560 are arranged on opposite sides of the
first ring
member 548, with the first ring member input traction surface 558 facing the
first input disk
512 and the first ring member output traction surface 560 facing the first
output disk 514.
[00166] The second ring member 550 may be similarly configured as the first
ring member
548. The second ring member 550 may include a pair of interconnected co-
rotating rings.
The co-rotating rings may include an input traction ring 568 that engages the
second input
disk 532, and an output traction ring 570 spaced from the input traction ring
568 and which
engages the second output disk 534. A generally cylindrical-shaped connecting
ring 572 may
fixedly connect the input traction ring 568 to the output traction ring 570.
The input and
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output traction rings 568 and 570 extend generally radially inward from the
connecting ring
572.
[00167] The input traction ring 568 may include a second ring member input
traction
surface 574 engageable with the second input disk traction surface 538 of the
second input
disk 532. The output traction ring 570 may include a second ring member output
traction
surface 576 engageable with the second output disk traction surface 546 of the
second output
disk 534. The second ring member input and output traction surfaces 574 and
576 may be
configured as continuous rings. The second ring member input traction surface
574 may be
located at a radius 578 from a ring member effective axis of rotation 566. The
second ring
member output traction surface 576 may be located at a radius 580 from the
ring member
effective axis of rotation 566. The first ring member input and output
traction surfaces 574
and 576 are arranged on opposite sides of the second ring member 550, with the
second ring
member input traction surface 574 facing the second input disk 532 and the
second ring
member output traction surface 576 facing the second output disk 534.
[00168] The speed ratio selector 506 may be operably connected to the first
and second
ring members 548 and 550 to selectively adjust the speed ratio of the two-
stage continuously
variable transmission 500. The speed ratio selector 506 operates to adjust the
radial location
of the first ring member 548 relative to the first input disk 512 and the
first output disk 514,
and adjust the radial location of the second ring member 550 relative to the
second input disk
532 and the second output disk 534, to achieve a selected speed ratio.
[00169] The speed ratio selector 506 may have any of a wide variety of
configurations.
The speed ratio selector 506 may employ any device capable of adjusting a
location of the
first ring member 548 relative to the first input and output disks 512 and
514, and the
location of the second ring member 550 relative to the second input and output
disk 532 and
534. An example of one such configuration is illustrated in FIGS. 20-22.
[00170] With reference to FIGS. 20 and 21, the speed ratio selector 506 may
include an
actuator 582 having a hollow inner region 584 defined by a generally circular
cylindrically-
shaped inner surface 586. A longitudinal axis of the inner surface 586
substantially coincides
with the ring member effective axis of rotation 566. The first and second ring
members 548
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and 550 may be rotatably disposed within the interior region 584 of the
actuator 582. The
first ring member 548 may be rotatably supported on a bearing 588 mounted on
the inner
surface 586 of the actuator 582. The second ring member 550 may be similarly
rotatably
mounted to the inner surface 586 of the actuator 582 using a second bearing
588. The
bearing 588 may be configured as a separate component or may be at least
partially integrally
formed with the actuator 582 and/or first and second ring members 548 and 550.
[00171] The actuator 582 may be rotatably attached to the housing 55, for
example, using
one or more bearings 590. The bearing 590 may be mounted to an outer
circumference 592
of the actuator 582 and the housing 55. The outer circumference 592 of the
actuator 582 may
have a generally circular shape with a center axis that coincides with an axis
of rotation 594
of the actuator 582. The axis of rotation 594 of the actuator 582 may be
offset from the ring
member effective axis of rotation 566 by a distance 596. As a consequence, a
thickness T of
the actuator 582 varies circumferentially, as shown, for example, in FIG. 19,
with a minimum
and maximum thickness T of the actuator occurring on diametrically opposite
sides of the
actuator 582. The eccentricity between the inner surface 586 and the outer
circumference
592 of the actuator 582 allows a radial location of the first and second ring
members 548 and
550 to be selectively varied relative to the first input and output disks 512
and 514 and the
second input and output disks 532 and 534 by rotating the actuator 582 about
its axis of
rotation 594.
[00172] The two-stage continuously variable transmission 500 operates to
transfer torque
from the input shaft 42 to the output shaft 44. Torque from the input shaft 42
may be
transferred from the first input disk 512 to the first ring member 548 across
a first input
contact patch 598 where the first ring member input traction surface 558
engages the first
input disk traction surface 520. Torque may be transferred from the first ring
member 548 to
the first output disk 514 across a first output contact patch 600 where the
first ring member
output traction surface 560 engages the first output disk traction surface
528. The first input
contact patch 598 is located at a radius 602 from the input and output shaft
axis of rotation
510, and the first output contact patch 600 is located at a radius 604 from
the input and output
shaft axis of rotation 510. The radius 602 of the first input contact patch
598 and the radius
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604 of the first output contact patch 600 varies as the speed ratio of the two-
stage
continuously variable transmission 500 is varied.
[00173] Torque from the first output disk 514 is transmitted along the
intermediate shaft
508 to the second input disk 532. Torque from the second input disk 532 may be
transferred
to the second ring member 550 across a second input contact patch 606 where
the second ring
member input traction surface 574 engages the second input disk traction
surface 538.
Torque may be transferred from the second ring member 550 to the second output
disk 534
across a second output contact patch 608 where the second ring member output
traction
surface 576 engages the second output disk traction surface 546. The second
input contact
patch 606 is located at a radius 610 from the input and output shaft axis of
rotation 510, and
the second output contact patch 608 is located at a radius 612 from the input
and output shaft
axis of rotation 510. The radius 610 of the second input contact patch 606 and
the radius 612
of the second output contact patch 608 varies as the speed ratio of the two-
stage continuously
variable transmission 500 is varied. Torque transferred from the second ring
member 550 to
second output disk 534 may be output through the output shaft 44.
[00174] The speed ratio of the two-stage continuously variable transmission
500 is a
function of the radial locations 602 and 604 of the first input and output
contact patches 598
and 600, respectively, and the radial locations 610 and 612 of the second
input and output
contact patches 606 and 608, respectively. The rotational speed of the output
shaft 44
increases, relative to the rotational speed of the input shaft 42, as the
radial locations 602 and
610 of the first and second input contact patches 598 and 606 respectively
increase, and the
radial locations 604 and 612 of the first and second output contact patches
608 and 612
respectively decrease. On the other hand, the rotational speed of the output
shaft 44
decreases as the radial locations 602 and 610 of the first and second input
contact patches 598
and 606 respectively decrease, and the radial locations 604 and 612 of the
first and second
output contact patches 608 and 612 respectfully increase.
[00175] With reference to FIGS. 20 and 22, the speed ratio selector 506 may
be used to
selectively adjust the speed ratio of the two-stage continuously variable
transmission 500.
FIG. 20 illustrates the speed ratio selector 506 arranged in a first speed
ratio position. In this
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position the first and second ring members 548 and 550 engage the first and
second output
disks 514 and 534 near their respective outer edges 524 and 542, and engage
the first and
second input disks 512 and 532 closer toward the input and output axis of
rotation 510. This
arrangement produces the lowest speed ratio (e.g., speed ratio = (rotational
speed of output
shaft 44) (rotational speed of input shaft 42)), wherein the output shaft 44
has a lower
rotational speed than the input shaft 42.
[00176] FIG. 22 illustrates the speed ratio selector 506 arranged in a second
speed ratio
position. In this position the first and second ring members 548 and 550
engage the first and
second output disks 514 and 534 near their respective outer edges 524 and 542,
and engage
the first and second input disks 512 and 532 closer toward the input and
output axis of
rotation 510. This arrangement produces the lowest speed ratio (e.g., speed
ratio = (rotational
speed of output shaft 44) (rotational speed of input shaft 42)), wherein the
output shaft 44
has a lower rotational speed than the input shaft 42. The speed ratio selector
506 may be
infinitely adjustable between the first speed ratio position (for example, as
illustrated in
FIGS. 20 and 21) and the second speed ratio position (for example, as
illustrated in FIG. 22).
The illustrated speed ratio selector 506 is configured to provide a shift
ratio of 1:1, but may
also be configured to provide other speed ratios depending on the design and
performance
requirement of a particular application.
[00177] The configuration of the first drive mechanism 502 of the continuously
variable
drive mechanism 500 is such that a sum of the radial location 602 of the first
input contact
patch 598 and the radial location 604 of the first output contact patch 600 is
greater than the
radius 562 of the first ring member input traction surface 558 and the radius
564 of the first
ring member output traction surface 560. The following holds true for all
speed ratios:
A. ((radius 602) + (radius 604)) > (radius 562)
B. ((radius 602) + (radius 604)) > (radius 564)
[00178] A similar relationship also holds true for the second drive mechanism
504. For
example, the configuration of the second drive mechanism 504 of the
continuously variable
transmission 500 is such that a sum of the radial location 610 of the second
input contact
patch 606 and the radial location 612 of the second output contact patch 608
is greater than
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the radius 578 of the second ring member input traction surface 574 and the
radius 580 of the
second ring member output traction surface 576. The following holds true for
all speed
ratios:
A. ((radius 610) + (radius 612)) > (radius 578)
B. ((radius 610) + (radius 612)) > (radius 580)
[00179] It is intended that the scope of the present methods and apparatuses
be defined by
the following claims. However, it must be understood that the various
disclosed
configurations and operation of the continuously variable transmission may be
practiced
otherwise than is specifically explained and illustrated without departing
from its spirit or
scope. It should be understood by those skilled in the art that various
alternatives to the
configurations described herein may be employed in practicing the claims
without departing
from the spirit and scope as defined in the following claims. The scope of the
disclosed
systems and methods should be determined, not with reference to the above
description, but
should instead be determined with reference to the appended claims, along with
the full scope
of equivalents to which such claims are entitled. It is anticipated and
intended that future
developments will occur in the arts discussed herein, and that the disclosed
systems and
methods will be incorporated into such future examples. Furthermore, all terms
used in the
claims are intended to be given their broadest reasonable constructions and
their ordinary
meanings as understood by those skilled in the art unless an explicit
indication to the contrary
is made herein. In particular, use of the singular articles such as "a,"
"the," "said," etc.,
should be read to recite one or more of the indicated elements unless a claim
recites an
explicit limitation to the contrary. It is intended that the following claims
define the scope of
the device and that the method and apparatus within the scope of these claims
and their
equivalents be covered thereby. In sum, it should be understood that the
device is capable of
modification and variation and is limited only by the following claims.
