KR20190057023A - Continuously variable transmission - Google Patents

Abstract

The continuously variable transmission includes an input disk and an output disk rotatable about a disk rotation axis. An input ring member rotatable relative to the input rotational axis engages the input disc in the input contact patch. An output ring member rotatable relative to the output rotational axis engages the output disc in the output contact patch. The sum of the length of the first input contact patch vector extending from the input contact patch to the disk rotational axis and the length of the first output contact patch vector extending from the output contact patch to the disk rotational axis is a second input Is greater than the length of at least one of the contact patch vector and the second output contact patch vector extending from the output contact patch to the output rotation axis.

Description

Continuously variable transmission

This application claims the benefit of U.S. Patent Application No. 14 / 166,336, filed January 28, 2014, which is incorporated herein by reference in its entirety.

A continuously variable transmission (CVT) is a type of transmission that can provide more useful power, better economy and a smoother driving experience than a conventional manual or automatic transmission. A typical automotive transmission may include a fixed number of gears to select from. 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 to a specific gear can allow the vehicle to produce almost the maximum power possible with the least amount of energy.

The continuously variable transmission (CVT) is a transmission that can be continuously changed through an infinite number of effective gear ratios between a maximum value and a minimum value. The CVT can gradually change the speed ratio. This is contrasted with other mechanical transmissions that provide a fixed number of gear ratios. CVTs can provide better fuel economy than other transmissions by allowing the engine to operate at the most efficient rate per minute (RPM) for a range of vehicle power and speed combinations. The CVT can also be used to maximize the performance of the vehicle by allowing the engine to rotate at the RPM producing peak power. This is generally higher than the RPM achieving peak efficiency. CVT can make vehicles that are more fuel-efficient. An almost unlimited number of positions helps ensure that you always use the right amount of power.

There is disclosed herein a continuously variable transmission that may include an input disk rotatable about a disk rotation axis. The input disk may include an input disk traction surface. The continuously variable transmission may also include an output disc rotatable relative to the disc rotation axis. The output disk may include an output disk traction surface. The input ring member rotatable relative to the input rotational axis may include an input ring traction surface located at an input ring traction surface radial distance from the input rotational axis. The input ring traction surface includes a first input contact patch vector length extending from the input contact patch to the disk rotational axis and a second input contact patch vector extending vertically from the input contact patch to the input rotational axis. Lt; RTI ID = 0.0 > a < / RTI > The output ring member rotatable about the output rotation axis may include an output ring traction surface located at an output ring traction surface radial distance from the output rotation axis. The output ring traction surface includes a first output contact patch vector length extending vertically from the output contact patch to the disk rotation axis and a second output contact patch vector length extending from the output contact patch to the output rotation axis. Lt; RTI ID = 0.0 > a < / RTI > output disk traction surface. The sum of the length of the first input contact patch vector and the length of the first output contact patch vector is greater than the length of at least one of the second input contact patch vector and the second output contact patch vector.

The detailed description herein refers to the accompanying drawings, in which like reference numerals refer to like parts throughout the several views.
1 is a schematic cross-sectional view of an exemplary continuously variable transmission having a speed ratio selector disposed at a first speed ratio position;
Figure 2 is a cross-sectional view of the continuously variable transmission of Figure 1 showing the position and orientation of the various contact patch vectors.
3 is a partial cross-sectional view of the continuously variable transmission of FIG. 1 taken along section line 3-3, with a speed ratio selector disposed at a first speed ratio position.
Fig. 4 is a schematic view of the continuously variable transmission of Fig. 1 with a speed ratio selector disposed at a second speed ratio position.
Fig. 5 is a partial cross-sectional view of the continuously variable transmission of Fig. 4 taken along section line 5-5, with a speed ratio selector disposed at a second speed ratio position.
6 is a schematic diagram of an alternatively configured continuously variable transmission having a speed ratio selector disposed at a first speed ratio position;
7 is a cross-sectional view of the continuously variable transmission of FIG. 6 showing the position and orientation of various contact patch vectors.
Fig. 8 is a partial cross-sectional view of the continuously variable transmission of Fig. 6 taken along section line 8-8, with a speed ratio selector disposed at a first speed ratio position; Fig.
Fig. 9 is a schematic view of the continuously variable transmission of Fig. 6 with a speed ratio selector disposed at a second speed ratio position.
Fig. 10 is a partial cross-sectional view of the continuously variable transmission of Fig. 9 taken along section line 10-10 with a speed ratio selector located at a second speed ratio position; Fig.
11 is a schematic diagram of a continuously variable transmission in which an input drive member is operatively connected to an output drive member and employs a single ring member disposed in a first speed ratio position;
12 is a schematic view of the continuously variable transmission of FIG. 11 having a ring member disposed at a second speed ratio position;
13 is a schematic diagram of a continuously variable transmission employing a hydraulically operated speed ratio selector, wherein the speed ratio selector is disposed at a first speed ratio position;
14 is a schematic view of the continuously variable transmission of FIG. 13 with a speed ratio selector disposed at a second speed ratio position.
Fig. 15 is a schematic diagram of another alternative configured continuously variable transmission employing a geared ring member disposed at a first speed ratio position; Fig.
16 is a partial cross-sectional view of the continuously variable transmission of Fig. 15 taken along the section line 16-16.
Fig. 17 is a schematic view of the continuously variable transmission of Fig. 15 having a ring member disposed at a second speed ratio position; Fig.
Fig. 18 is a schematic diagram of another alternative configured continuously variable transmission employing a pilot ring member disposed in a first speed ratio position.
19 is a schematic view of the continuously variable transmission of FIG. 18 having a ring member disposed at a second speed ratio position;
Figure 20 is a schematic diagram of another alternatively configured continuously variable transmission shown as being disposed at a first speed ratio position;
21 is an end view of the continuously variable transmission shown in Fig.
22 is a schematic view of the continuously variable transmission of FIG. 20 shown as being disposed at the second speed ratio position.

With reference now to the following discussion and also to the drawings, an exemplary approach to the disclosed system and method is described in detail. Although the drawings show some possible approaches, the drawings are not necessarily to scale, and some features may be out of plane, exaggerated, removed, sectioned, or partially sectioned to better illustrate and describe the present invention have. In addition, the detailed description set forth herein is not intended to be exhaustive or to limit or limit the claim to the exact forms and arrangements set forth in the following detailed description, which are either generic or otherwise depicted in the drawings.

1, an exemplary continuously variable transmission 40 operable to transmit rotational energy between an input shaft 42 and an output shaft 44 is shown. The input shaft 42 is rotatable with respect to the input rotary shaft 46 and the output shaft 44 is rotatable with respect to the output rotary shaft 48. The input rotary shaft 46 may be disposed substantially parallel to the output rotary shaft 48. The input rotary shaft 46 may be offset from the output rotary shaft 48 by a distance 50. [ The input and output shafts 42 and 44 may each be rotatably supported within the housing 52 by bearings 54, respectively. The bearing 54 may have any of a variety of configurations, including but not limited to roller bearings, ball bearings, and tapered bearings, and may include other configurations. A plurality of bearings 54 and / or bearing types may be used to support 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.

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 operate in conjunction with each other to transmit rotational torque from the input shaft 42 to the output shaft 44, respectively. The input and output drive mechanisms 56 and 58 are configured to vary the speed ratio of the continuously variable transmission 40 (for example, the speed ratio = (the rotational speed of the output shaft 44) / (the rotational speed of the input shaft 42) As shown in FIG. The continuously variable transmission 40 may employ a speed ratio selector 60 operable to selectively adjust the speed ratio.

The input drive mechanism 56 may employ a first input disc 62 and a second input disc 64 positioned adjacent the first input disc 62. The first and second input discs 62 and 64 are rotatable relative to the disc rotation axis 66, respectively. The disk rotational axis 66 may be aligned substantially parallel to the input rotational axis 46 and / or the output rotational axis 48. The position of the disk rotational shaft 66 is selectively provided to the input rotational shaft 46 and / or the output rotational shaft 48 while maintaining the orientation of the disk rotational shaft 66 with respect to the input rotational shaft 46 or the output rotational shaft 48 Lt; / RTI > In other words, when adjusting the position of the disk rotation shaft 66 with respect to the input rotation axis 42 and / or the output rotation axis 66, the disk rotation axis 66 is substantially perpendicular to the input rotation axis 46 and the output rotation axis 66 And remain parallel.

The first and second input discs 62, 64 extend generally radially outward from the disc rotation axis 66. The edge 67 defines the outer circumference of the first input disc 62. The first input disc 62 includes a first input disc traction surface 68 of a generally convex conical shape positioned adjacent the input shaft 42 and an opposing inner surface 70 located adjacent the second input disc 64 ). The inner surface 70 of the first input disc 62 may have a generally planar surface contour as shown, for example, in FIG. 1, or may include various other contours and / or contours. For example, the inner surface 70 may include one or more recessed areas to help minimize the weight and / or rotational inertia of the first input disc 62.

The first input disc 62 may be fixedly attached to an inner shaft 72 which later extends outwardly from the inner surface 70 of the first input disc 62. Alternatively, the first input disc 62 may be formed integrally with the inner shaft 72. The longitudinal axis of the inner shaft 72 substantially coincides with the disk rotational axis 66.

1, the edge 74 defines the outer circumference of the second input disc 64. The second input disc 64 includes an inner surface 76 positioned adjacent the first input disc 62 and a second generally convex conical shaped input disc traction surface 78 located opposite the inner surface 76 ). The second input disc 64 may generally consist of a mirror image of the first input disc 62 in view of FIG. Similar to the first input disc 62, the inner surface 76 of the second input disc 64 may have a generally planar surface contour as shown, for example, in FIG. 1, / / ≪ / RTI > For example, the inner surface 76 may include one or more recessed regions to help minimize the weight and / or rotational inertia of the second input disc 64.

The second input disc 64 may be fixedly attached to an external shaft 80 of hollow cylindrical shape extending laterally outward from the second input disc traction surface 78 of the second input disc 64. Alternatively, the second input disc 64 may be formed integrally with the outer shaft 80. The longitudinal axis of the outer shaft 80 substantially coincides with the disk rotational axis 66. The outer shaft 80 includes a elongated outer shaft passage 82 for receiving the inner shaft 72. The outer shaft passage 82 extends in the longitudinal direction along the disk rotation shaft 66. The inner shaft 72 and the outer shaft 80 are axially movable relative to each other along the disk rotational axis 66 to define a distance between the first input disk traction surface 68 and the second input disk traction surface 68 RTI ID = 0.0 > D1 < / RTI > The inner shaft 72 and the outer shaft 80 may be configured to be rotatable relative to each other, or alternatively may be rotatably secured to one another. The latter is achieved, for example, by using a spline that allows axial movement between the inner shaft 72 and the outer shaft 80 while at the same time preventing the inner shaft 72 and the outer shaft 80 from rotating relative to each other . In either case, the inner shaft 72 and the outer shaft 80 are generally free to move axially relative to each other.

The output drive mechanism 58 may be configured similar to the input drive mechanism 56 and may include a first output disk 84 and a second output disk 86 positioned adjacent the first output disk 84, ). The first and second output discs 84, 86 are rotatable relative to the disc rotation axis 66, respectively. The first and second output discs 84, 86 extend radially outwardly from the disc rotation axis 66 generally.

The edge 88 defines the outer periphery of the first output disc 84. The first output disc 84 includes a first convexly shaped first output disc traction surface 90 disposed adjacent the output shaft 44 and an opposing inner surface 92 positioned adjacent the second output disc 86 ). The inner surface 92 of the first output disk 84 may have a generally planar surface contour, for example, as shown in FIG. 1, or may include various other shapes and / or contours. For example, the inner surface 92 may include one or more recessed areas to help minimize the weight and / or rotational inertia of the first output disc 84.

The first output disc 84 may be fixedly attached to the end 93 of the inner shaft 72 opposite the first input disc 62 so that the first input disc 62 and the first output disc 84 To be simultaneously operatively rotated with respect to the disk rotating shaft 66. [ The inner shaft 72 and the end 93 of the first output disc 84 are connected by a connecting thread that allows the first output disc 84 to be threaded onto the inner shaft 72 . Other fixing mechanisms may be used to attach the first output disc 84 to the end 83 of the inner shaft 72, such as bolts, rivets, screws, adhesives, brazing, and welding. Alternatively, the first output disc 84 may be formed integrally with the inner shaft 72.

1, the edge 94 defines the outer circumference of the second output disc 86. As shown in FIG. The second output disc 86 includes an inner surface 96 positioned adjacent the first output disc 84 and a second generally convex conical shaped input disc traction surface 98 located opposite the inner surface 96 ). The second output disc 86 may generally consist of a mirror image of the first output disc 84 when viewed from the perspective of FIG. Similar to the first output disc 84, the inner surface 96 of the second input disc 96 may have a generally planar surface contour as shown, for example, in FIG. 1, / / ≪ / RTI > For example, the inner surface 96 may include one or more recessed regions to help minimize the weight and / or rotational inertia of the second output disc 86.

The second output disc 86 may be fixedly attached to the end 100 of the outer shaft 80 such that the second input disc 64 and the second output disc 86 are simultaneously Rotates operatively. The outer shaft 80 and the end 100 of the second output disc 86 are connected by a connecting thread to allow the second output disc 86 to be threaded onto the outer shaft 80 . Other fixing mechanisms may be used to attach the second output disc 86 to the end 100 of the outer shaft 80, such as bolts, rivets, screws, adhesives, brazing, and welding. Alternatively, the second output disc 86 may be formed integrally with the outer shaft 80.

Similar to the first input disc 62 and the second input disc 64, the first output disc 84 and the second output disc 86 are axially movable relative to each other along the disc rotation axis 66 Do. This allows the distance D2 between the first output disk traction surface 90 and the second output disk traction surface 98 to be selectively changed.

The input drive mechanism 56 may include an input ring member 102 that is fixedly connected to the input shaft 42 for simultaneous rotation. The input ring member 102 operates to rotatably connect the first input disc 62 and the second input disc 64 to the input shaft 42. The position and orientation of the input ring member 102 remains substantially fixed with respect to the input shaft 42. [ The input ring member 102 may have a generally C-shaped configuration having an open end 104 disposed opposite the closed end 106. The closed end 106 may be fixedly attached to the input shaft 42 or formed integrally. The generally circular opening 103 in the open end 104 of the input ring member 102 is defined by the circumferential edge 108.

The first and second input disks 62 and 64 may be located within the inner cavity 110 of the input ring member 102 and the corresponding inner and outer shafts 72 and 80 may be located within the inner ring 110 of the input ring member 102 Extends through the opening (103). The aperture 103 may be sized to be larger than the first and second input discs 62 and 64 to facilitate positioning the disc within the inner cavity 110 of the input ring member 102. [

The input ring member 102 includes an input ring first traction surface 112 and a second input disc traction surface 78 that can engage the first input disc traction surface 68 of the first input disc 62, And may include an input ring second traction surface 114 that can be engaged. The input ring first and second traction surfaces 112 and 114 may be configured as a continuous ring extending inwardly from the inner surface 116 of the input ring member 102. [ The input ring first and second traction surfaces 112, 114 may be located at a radius 117 from the input rotational axis 46. The input ring second traction surface 114 may be disposed immediately adjacent to the opening 103 of the input ring member 102. The input ring first traction surface may be positioned opposite the input ring second traction surface 114 along the side of the input ring member 102 attached to the input shaft 42.

The output drive mechanism 58 may include an output ring member 118 that is fixedly connected to the output shaft 44 for simultaneous rotation. The output ring member 118 operates to rotatably couple the first and second output disks 84, 86 to the output shaft 44. The position and orientation of the output ring member 118 remains substantially fixed with respect to the output shaft 44. The output ring member 118 may have a generally C-shaped configuration with an open end 120 disposed opposite the closed end 122. The closed end 122 may be fixedly attached to the output shaft 44 or integrally formed therewith. The generally circular opening 124 in the open end 120 of the output ring member 118 is defined by the circumferential edge 126.

The first and second output discs 84 and 86 may be located within the inner cavity 130 of the output ring member 118 and the corresponding inner and outer shafts 72 and 80 may be positioned within the inner ring of the output ring member 118 And extends through opening 124. The opening 124 may be sized to be larger than the first and second output discs 84 and 86 to facilitate positioning of the disc within the inner cavity 130 of the output ring member 118.

The output ring member 118 includes an output ring first traction surface 132 and a second output disc traction surface 98 that can engage the first output disc traction surface 90 of the first output disc 84, And an output ring second traction surface 134 that can be engaged. The output ring first and second traction surfaces 132 and 134 may be configured as a continuous ring extending generally inwardly from the inner surface 138 of the output ring member 118. [ The output ring first and second traction surfaces 132,134 may be located at a radius 136 from the output rotation axis 48. [ The output ring second traction surface 134 may be disposed immediately adjacent to the opening 124 of the output ring member 118. The output ring first traction surface 132 may be positioned opposite the output ring second traction surface 134 along the side of the output ring member 118 attached to the output shaft 44.

The continuously variable transmission 40 is operative to transmit torque from the input shaft 42 to the output shaft 44. The torque from the input shaft 42 is transmitted from the input ring member 102 to the first input disc 62 and the input ring first traction surface 112 is coupled to the first input disc traction surface 78, A second input contact patch 142 is provided which extends across the contact patch 140 and into the second input disc 64 where the input ring second traction surface 114 engages the second input disc traction surface 78 Lt; / RTI >

The first and second input contact patches 140 and 142 are located at a radius 143 from the disk rotational axis 66. [ The radius 143 of the first and second input contact patches 140 and 142 changes as the speed ratio of the continuously variable transmission 40 changes. The inner shaft 72 transfers torque from the first input disc 62 to the first output disc 84. The outer shaft 80 transfers torque from the second input disc 64 to the second output disc 86. The torque is transmitted from the first output disc 84 to the output ring member 118 such that the output ring first traction surface 132 is transverse to the first output contact patch 144 that engages the first output disc traction surface 90 Can be delivered. The torque is transmitted from the second output disc 86 to the output ring member 118 and the second output contact patch 146 in which the output ring second traction surface 134 engages the second output disc traction surface 134 Can be delivered. The first and second output contact patches 144 and 146 are located at a radius 147 from the disk rotational axis 66. For purposes of discussion, it is noted that the first and second contact patches 144 and 146 are shown to occur in a common plane such that they are disposed on the radially opposite sides of the disk rotational axis 66 (i.e., spaced about 180 degrees apart) You should know. However, in practice, the first and second contact patches 144, 146 may be located out of plane, so that the angular position of the first and second contact patches relative to each other is a value 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 changes. The output ring member 118 operates to transfer torque from the first and second output disks 84, 86 to the output shaft 44.

The speed ratio of the continuously variable transmission 40 is set such that the radial position 143 of the first and second input contact patches 140 and 142 and the radial position 147 of the first and second output contact patches 144, . The speed ratio of the continuously variable transmission 40 is set such that the input ring first and second traction surfaces 112 and 114 are in a radial position in which they engage the first and second input disk traction surfaces 68 and 78 respectively And the radial position 143 of the second input contact patch 140, 142). The rotational speed of the output shaft 44 decreases with respect to the rotational speed of the input shaft 42 as the radial position 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 position 143 of the first and second input contact patches 140, 142 decreases. The output ring first and second traction surfaces 132,134 are in radial position (i.e., the first and second output contact patches 144,154, respectively) where they engage the first and second output disc traction surfaces 90,98, 146) has an opposite effect. The rotational speed of the output shaft 44 increases with respect to the rotational speed of the input shaft 42 as the radial position 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 position 147 of the first and second output contact patches 144, 146 decreases.

The speed ratio can be selectively adjusted by shifting the position of the disk rotation axis 66 relative to the input rotation axis 46 and the output rotation axis 48 so that the rotation axis 48 can be rotated by the rotation of the input ring member 102, A radial position 143 that engages the two input discs 62 and 64 and a radial position 147 where the output ring member 118 engages the first and second output discs 84 and 86. The first input disc 46 is connected to the first output disc 84 via the inner shaft 72 and the second input disc 64 is connected to the second output disc 86 via the outer shaft 80 , Any movement of the first and second input discs 62, 64 results in a corresponding movement of the first and second output discs 84, 86. For example, moving the first and second input disks 62 and 64 radially upward (as viewed in view of FIG. 1) moves the first and second output disks radially upward. On the other hand, moving the first input disk 62 and the second input disk 64 radially downward (as viewed in view of FIG. 1) moves the first and second output disks radially downward.

Referring to Figure 2, a first input contact patch 140 is substantially parallel to a first input contact patch vector 154 extending from the first input contact patch 140 to the disk rotation axis 66 And is substantially vertically aligned with the second input contact patch vector length 156 extending from the first input contact patch 140 to the input rotational axis 46. [ Similarly, the first output contact patch 146 is arranged substantially perpendicular to the first output contact patch vector 158 extending from the first output contact patch 146 to the disk rotation axis 66, And is arranged substantially perpendicular to the second output contact patch vector 160 extending from the patch 146 to the output rotary shaft 48. The construction and arrangement of various components of the continuously variable transmission 40 is such that the sum of the length of the first input contact patch vector 154 and the length of the first output contact patch vector 158 is equal to the sum of the length of the first input contact patch vector 156 Length and the length of the second output contact patch vector 160. The following relationship applies to all speed ratios:

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)

A similar relationship applies to the second input contact patch 142 and the second output contact patch 144 as well. For example, the length of the first input contact patch vector extending from the second input contact patch 142 to the disk rotation axis 66 and substantially perpendicular to the second input contact patch 142, The sum of the lengths of the first output contact patch vectors extending from the patches 146 to the disk rotational axis 66 and aligned substantially perpendicular to the second output contact patches 146 is greater than the sum of the lengths of the first output contact patch vectors from the second input contact patches 146, The length of the second input contact patch vector extending to the first output contact patch 46 and substantially perpendicular to the second output contact patch 142 and the length of the second input contact patch vector extending from the second output contact patch 146 to the output rotary shaft 48, Is greater than at least one of the length of the second output contact patch vector that is substantially perpendicular to the contact patch (146).

Referring 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. Fig. The speed ratio selector 60 may have any of a wide variety of configurations. The speed ratio selector 60 adjusts the position of the first and second output discs 84 and 86 relative to the first and second input discs 62 and 64 and the output ring 118 for the input ring 102 Any of which can be employed. This can be achieved, for example, by selectively adjusting the position of the disk rotation axis 66 relative to the input rotation axis 46 and / or the output rotation axis 48. [ An example of one possible configuration of the speed ratio selector 60 is shown in the figure. The speed ratio selector 60 may include an external shaft 80 and correspondingly an internal shaft 72, first and second input disks 62 and 64, first and second output disks < RTI ID = 84 and 84 to the housing 52. In this embodiment, The speed ratio selector 60 operates to change the position of the disk rotation axis 66 with respect to the input rotation axis 46 and the output rotation axis 48, and accordingly the speed ratio. The speed ratio selector 60 includes 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 point of the speed ratio selector 60. [ The speed ratio is determined by the distance between the disk rotational axis 66 and the housing 52 and the position of the disk rotational axis 66 relative to the input rotational axis 46 and the output rotational axis 48, 2 links 148 and 150 in alternating fashion.

Figures 1 and 3 illustrate a speed ratio selector 60 disposed at a first speed ratio position where the first and second links 148, 150 are fully extended. In this position, the input ring member 102 engages the first and second input discs 62 and 64 near the respective outer edges 67 and 74 and the output ring member 118 engages the disc rotation axis 66, To the first and second output discs 84, 86, respectively. This configuration produces the lowest speed ratio (e.g., speed ratio = (rotational speed of output shaft 44) / (rotational speed of input shaft 42)), where output shaft 44 is an input shaft (42).

Figures 4 and 5 illustrate a speed ratio selector 60 disposed at a second speed ratio position where the first and second links 148, 150 are fully folded. In this position, the output ring member 118 engages the first and second output discs 84, 86 near respective outer edges 88, 94 and the input ring member 102 engages the disc rotation axis 66, To the first and second input discs 62 and 64, respectively. This configuration produces the highest speed ratio, where the output shaft 44 has a lower rotational speed than the input shaft 42. [ 4 and 5) and a second speed ratio position (e. G., As shown in FIGS. 4 and 5) Can be adjusted infinitely.

The speed ratio selector 60 shown in the figure is merely one example of various types and configurations of actuators that can be used to selectively adjust the speed ratio of the continuously variable transmission. Other types and configurations of actuating mechanisms may be employed. For example, the speed ratio selector 60 may include electromechanical, hydraulic, pneumatic and mechanical actuators as well as combinations thereof. In order to selectively adjust the speed ratio of the continuously variable transmission 40, the radial position of the first and second input discs 62 and 64 with respect to the input ring member 102 and the radial position of the input ring member 102 with respect to the output ring member 118 Other mechanisms capable of selectively adjusting the radial position of the first and second output disks 84 and 86 may also be employed.

Referring to FIG. 6, there is shown a continuously variable transmission 200 configured to be alternately operable to transmit rotational energy between an input shaft 42 and an output shaft 44. The input shaft 42 is rotatable with respect to the input rotary shaft 46, and the output shaft 44 is rotatable with respect to the output rotary shaft 48. The input rotary shaft 46 may be disposed substantially parallel to the output rotary shaft 48. [ The input rotary shaft 46 can be offset from the output rotary shaft 48 by a distance 50. [ The input and output shafts 42 and 44 may each be rotatably supported within the housing 52 by bearings 54, respectively. The position and orientation of the input shaft 42 is generally fixed relative to the output shaft 44. The offset distance 50 can be used to compensate for changes in the working fluid viscosity.

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 operate in conjunction with each other to transmit rotational torque from the input shaft 42 to the output shaft 44, respectively. The input and output drive mechanisms 202 and 204 may be arranged in series. The input and output drive mechanisms 202 and 204 change the speed ratio of the continuously variable transmission 200 (for example, the speed ratio = (the rotational speed of the output shaft 44) / (the rotational speed of the input shaft 42) As shown in FIG. The continuously variable transmission 200 may be operable to employ a speed ratio selector 60 to selectively adjust the speed ratio.

The input drive mechanism 202 may employ a first input disc 206 and a second input disc 208 positioned adjacent to the first input disc 206. The first and second input disks 206 and 208 are rotatable about a disk rotation axis 210, respectively. The disk rotation axis 210 may be aligned substantially parallel to the input rotation axis 46 and / or the output rotation axis 48. The position of the disk rotation axis 210 may be selected for the input rotation axis 46 and / or the output rotation axis 48 while maintaining the orientation of the disk rotation axis 210 with respect to the input rotation axis 46 and / Lt; / RTI > In other words, the disk rotating shaft 210 is substantially parallel to the input rotating shaft 46 and the output rotating shaft 48 when adjusting the position of the disk rotating shaft 210 with respect to the input rotating shaft 42 and / or the output rotating shaft 46 Lt; / RTI >

The first and second input discs 206 and 208 extend radially outwardly from the disc rotation axis 210 generally. The edge 212 defines the outer circumference of the first input disc 206. The first input disc 206 may include a first convex conical first input disc traction surface 214 located opposite the input shaft 42 and adjacent the second input disc 208. There is an outer surface 216 located adjacent to the input shaft 42, opposite the input disk traction surface 214. The outer surface 216 of the first input disc 206 may have a generally planar surface contour as shown, for example, in FIG. 6, or may include various other contours and / or contours. For example, the inner surface 216 may include one or more recessed regions to help minimize the weight and / or rotational inertia of the first input disc 206.

The first input disc 206 may be fixedly attached to an inner shaft 218 that extends laterally outward from the first input disc traction surface 214 of the first input disc 206. Alternatively, the first input disc 206 may be formed integrally with the inner shaft 218. The longitudinal axis of the inner shaft 218 substantially coincides with the disk rotational axis 210.

6, the edge 220 defines the outer circumference of the second input disc 208. As shown in FIG. The second input disc 208 includes a second input disc traction surface 222 that is positioned adjacent to the first input disc 206 and a second input disc traction surface 222 that is generally convex conical in shape, May include a surface 224. The second input disc 208 may generally be comprised of a mirror image of the first input disc 206 in view of FIG. Similar to the first input disc 206, the outer surface 224 of the second input disc 208 may have a generally planar surface contour as shown, for example, in FIG. 6, / / ≪ / RTI > For example, the outer surface 224 may include one or more recessed regions to help minimize the weight and / or rotational inertia of the second input disc 208.

The second input disc 208 may be fixedly attached to an outer shaft 226 of hollow cylindrical shape extending laterally backward from the outer surface 224 of the second input disc 208. Alternatively, the second input disc 208 may be formed integrally with the outer shaft 226. [ The longitudinal axis of the outer shaft 226 substantially coincides with the disk rotational axis 210. The outer shaft 226 includes a elongated outer shaft passage 228 for receiving the inner shaft 218. The outer shaft passage 226 extends longitudinally along the disk rotation axis 210. The inner shaft 218 and the outer shaft 226 are configured to rotate the disk rotational axis 210 so that the distance D1 between the first input disk traction surface 214 and the second input disk traction surface 22 can be selectively changed. And are thus axially movable relative to each other. The inner shaft 218 and the outer shaft 226 may be configured to be rotatable relative to each other, or alternatively may be rotatably secured to one another. The latter can be achieved, for example, through the use of splines that allow axial movement of the inner and outer shafts 218, 226 while preventing the inner and outer shafts 218, 226 from rotating relative to each other . In either case, the inner shaft 218 and the outer shaft 226 are generally free to move axially relative to each other.

The output drive mechanism 204 may be configured similar to the input drive mechanism 202 and may include a first output disk 230 and a second output disk 230 positioned adjacent the first output disk 230, 232). The first and second output discs 230 and 232 are rotatable about a disc rotation axis 210, respectively. The first and second output discs 230 and 232 extend radially outwardly from the disc rotation axis 210 generally.

The edge 234 defines the outer circumference of the first output disc 230. The first output disc 230 may include a first convexly shaped first output disc traction surface 236 disposed opposite the output shaft 44 and the adjacent second output disc 232. The outer surface 238 of the first output disc 230 may have a generally planar surface contour as shown, for example, in FIG. 6, or may include various other contours and / or contours. For example, the outer surface 238 may include one or more recessed regions to help minimize the weight and / or rotational inertia of the first output disc 230.

The first output disc 230 may be fixedly attached to the end 240 of the inner shaft 218 opposite the first input disc 206 such that the first input disc 206 and the first output disc 230 To be operatively rotated simultaneously with the disk rotation axis 210 as a center. The end 240 of the inner shaft 218 and the first output disc 230 may have a connecting thread to allow the first output disc 230 to be threaded onto the inner shaft 218 . Other fixing mechanisms may be used to attach the first output disc 230 to the end 240 of the inner shaft 218, such as bolts, rivets, screws, adhesives, brazing, and welding. Alternatively, the first output disc 230 may be formed integrally with the inner shaft 218.

6, the edge 242 defines the outer periphery of the second output disc 232. The second output disc 232 may include a second convexly shaped second input disc traction surface 244 positioned adjacent to the first output disc 230 and positioned opposite the outer surface 246. The second output disc 232 may generally consist of a mirror image of the first output disc 230 in view of FIG. Similar to the first output disc 230, the outer surface 246 of the second input disc 232 may have a generally planar surface contour as shown, for example, in FIG. 6, / / ≪ / RTI > For example, the outer surface 246 may include one or more recessed regions to help minimize the weight and / or rotational inertia of the second output disc 232.

The second output disc 232 may be fixedly attached to the end 248 of the outer shaft 226 such that the second input disc 208 and the second output disc 232 are simultaneously It is possible to rotate it operatively. To facilitate assembly, the outer shaft 226 and the end 248 of the second output disc 232 include a connecting thread to allow the second output disc 232 to be threaded onto the outer shaft 226 can do. Other fixing mechanisms may also be used to attach the second output disc 232 to the end 248 of the outer shaft 226, such as bolts, rivets, screws, adhesives, brazing, and welding, . Alternatively, the second output disc 232 may be formed integrally with the outer shaft 226. [

Similar to the first input disk 206 and the second input disk 208, the first output disk 230 and the second output disk 232 are axially movable relative to each other along the disk rotational axis 210 Do. This allows the distance D2 between the first output disk traction surface 236 and the second output disk traction surface 244 to be selectively varied.

The input drive mechanism 202 may include an input ring member 250 that is fixedly connected to the input shaft 42 for simultaneous rotation. The input ring member 250 is operative to rotatably couple the first input disc 206 and the second input disc 208 to the input shaft 42. The position and orientation of the input ring member 250 remain substantially fixed with respect to the input shaft 42. [ The input ring member 250 may have a generally C-shaped configuration with an open end 254 disposed opposite the closed end 256. [ Closure end 256 may be fixedly attached to input shaft 42 or integrally formed therewith. A generally circular opening 252 in the open end 254 of the input ring member 250 is formed by the circumferential edge 258.

The first input disc 206 can be positioned within the inner cavity 260 of the input ring member 250 and the inner shaft 218 extends through the opening 252 of the input ring member 250. The aperture 252 may be set larger than the first input disc 206 to facilitate positioning of the disc within the inner cavity 260 of the input ring member 250. The second input disc 208 may be located outside of the input ring member 250 adjacent the opening 252.

The input ring member 250 includes an input ring first traction surface 262 and a second input disc traction surface 222 that can engage the first input disc traction surface 214 of the first input disc 206, And may include an input ring second traction surface 264 that can be engaged. The input ring first and second traction surfaces 262 and 264 may be configured as continuous rings. The input ring first and second traction surfaces 262 and 264 may be located at a radius 265 from the input rotational axis 46. [ The input ring first and second traction surfaces 262 and 264 may be disposed immediately adjacent the opening 252 of the input ring member 250. The input ring first and second traction surfaces 262 and 264 face generally opposite directions and the first input ring traction surface 262 extends generally inward toward the inner cavity 260, (264) extends generally outwardly from the inner cavity (260).

The output drive mechanism 204 may include an output ring member 266 fixedly connected to the output shaft 44 for simultaneous rotation. The output ring member 266 operates to rotatably couple the first and second output discs 230, 232 to the output shaft 44. The position and orientation of the output ring member 266 remains substantially fixed with respect to the output shaft 44. The output ring member 266 may have a generally C-shaped configuration with an open end 268 disposed opposite the closed end 270. [ The closed end 270 may be fixedly attached to the output shaft 44 or integrally formed therewith. A generally circular opening 272 in the open end 270 of the output ring member 266 is defined by the circumferential edge 274.

The first output disc 230 can be positioned within the inner cavity 276 of the output ring member 266 and the inner shaft 218 extends through the opening 268 of the output ring member 266. The opening 268 may be set larger than the first output disc 230 to facilitate positioning of the disc within the inner cavity 276 of the output ring member 266. [ The second output disc 232 may be located outside the output ring member 266 adjacent the opening 268. [

The output ring member 266 includes an output ring first traction surface 278 and a second output disc traction surface 244 that can engage the first output disc traction surface 236 of the first output disc 230 And an output ring second traction surface 280 that can be engaged. The output ring first and second traction surfaces 278, 280 may be configured as continuous rings. The output ring first and second traction surfaces 278,280 may be located at a radius 281 from the input rotational axis 46. [ The output ring first and second traction surfaces 278 and 280 may be disposed immediately adjacent to the opening 268 of the output ring member 266. [ The output ring first and second traction surfaces 278 and 280 are generally oriented in opposite directions and the first output ring traction surface 278 extends generally inward toward the inner cavity 276, The surface 280 extends generally outwardly from the inner cavity 276.

Referring to Fig. 6, the continuously variable transmission 200 operates to transmit torque from the input shaft 42 to the output shaft 44. As shown in Fig. The torque from the input shaft 42 is transmitted from the input ring member 250 to the first input disc 206 and the first input traction surface 262 is coupled to the first input disc traction surface 214 A second input contact patch 284 is formed across the contact patch 282 and into the second input disc 208 such that the input ring second traction surface 264 engages the second input disc traction surface 222, Lt; / RTI > The first and second input contact patches 282 and 284 are located at a radius 285 from the disk rotational axis 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 changes. The inner shaft 218 transfers torque from the first input disc 206 to the first output disc 230. The outer shaft 226 transfers torque from the second input disc 208 to the second output disc 232. The torque is transmitted from the first output disc 230 to the output ring member 266 and the first output contact patch 286 in which the output ring first traction surface 278 engages the first output disc traction surface 236 It can be passed on. The torque is transmitted across the second output contact patch 288 from the second output disc 232 to the output ring member 266 and the output ring second traction surface 280 engages the second output disc traction surface 244 Can be delivered. The first and second output contact patches 286 and 288 are located at a radius 289 from the disk rotational axis 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 changes. The output ring member 266 is operative to transmit torque from the first and second output discs 230, 232 to the output shaft 44.

The speed ratio of the continuously variable transmission 200 is determined by the radial position 285 of the first and second input contact patches 282 and 284 and the radial position 289 of the first and second output contact patches 286 and 288, . The speed ratio of the continuously variable transmission 200 is set such that the input ring first and second traction surfaces 262 and 264 are in a radial position in which they engage the first and second input disk traction surfaces 214 and 222 respectively And the radial position 285 of the second input contact patch 282, 284). As the radial position 285 of the first and second input contact patches 282 and 284 increases, the rotational speed of the output shaft 44 decreases relative to the rotational speed of the input shaft 42. [ On the other hand, the rotational speed of the output shaft 44 increases as the radial position 285 of the first and second input contact patches 282, 284 decreases. The output ring first and second traction surfaces 278 and 280 are in radial positions (i.e., the first and second output contact patches 286 and 286) that engage the first and second output disc traction surfaces 236 and 244, 288) have opposite effects. As the radial position 289 of the first and second output contact patches 286 and 288 decreases, the rotational speed of the output shaft 44 increases relative to the rotational speed of the input shaft 42. On the other hand, the rotational speed of the output shaft 44 decreases as the radial position 289 of the first and second output contact patches 286, 288 increases.

The speed ratio may be selectively adjusted by moving the position of the disk rotational axis 210 relative to the input rotational axis 46 and / or the output rotational axis 48, thereby causing the input ring member 250 to move relative to the first and second input disks < A radial position 285 in which the output ring member 266 engages the first and second output discs 230 and 232 is formed. The first input disc 206 is connected to the first output disc 230 via the inner shaft 218 and the second input disc 208 is connected to the second output disc 232 via the outer shaft 226 Any movement of the first and second input discs 206 and 208 results in a corresponding movement of the first and second output discs 230 and 232. For example, moving the first and second input discs 206 and 208 radially upward (as viewed in view of FIG. 6) also moves the first and second output discs 230 and 232 in the radial direction As shown in FIG. On the other hand, moving the first input disk 206 and the second input disk 208 radially downward (as viewed in view of FIG. 6) also allows the first and second output disks 230 and 232 to move radially .

Referring to Figure 7, the second input contact patch 284 is arranged substantially perpendicular to the first input contact patch vector 290 extending from the second input contact patch 284 to the disk rotation axis 210, Is substantially perpendicular to the second input contact patch vector 292 extending from the two-input contact patch 284 to the input rotational axis 46. [ Similarly, the second output contact patch 286 is arranged substantially perpendicular to the second output contact patch vector 294 extending from the first output contact patch 286 to the disk rotation axis 210, And is arranged substantially perpendicular to the second output contact patch vector 296 extending from the contact patch 286 to the output rotary shaft 48. The construction and arrangement of the various components of the continuously variable transmission 200 are such that the sum of the length of the first input contact patch vector 290 and the length of the first output contact patch vector 294 is equal to the sum of the length of the second input contact patch vector 292 Length and the length of the second output contact patch vector 296. The following relationship applies for all speed ratios.

(Length of the first input contact patch vector 290) + (length of the first output contact patch vector 294)) (length of the 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)

A similar relationship is also applied to the first input contact patch 282 and the first output contact patch 288. For example, the length of the first input contact patch vector length extending from the first input contact patch 282 to the disk rotational axis 210 and substantially perpendicular to the first input contact patch 282, The sum of the lengths of the first output contact patch vector lengths extending from the contact patch 288 to the disk rotational axis 66 and substantially perpendicular to the first output contact patch 288 is greater than the sum of the lengths of the first output contact patch vector length from the first input contact patch 282 The length of the second input contact patch vector length extending to the input rotary shaft 46 and substantially perpendicular to the first input contact patch 282 and the length of the second input contact patch vector length extending from the first output contact patch 288 to the output rotary shaft 48 And the length of the second output contact patch vector length, which is substantially perpendicular to the first output contact patch 288.

The speed ratio selector 60 can 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 with reference to Figures 1 and 3-5. 6 and 8 illustrate a speed ratio selector 60 disposed at a second speed ratio position in which the first and second links 148, 150 are fully extended. In this position, the input ring member 250 engages the first and second input discs 206 and 208 near the respective outer edges 212 and 220, and the output ring member 266 engages the disc rotation axis 210, To the first and second output discs 230 and 232, respectively. This configuration produces a maximum speed ratio (e.g., speed ratio = (rotational speed of output shaft 44) / (rotational speed of input shaft 42)), (42).

Figures 9 and 10 illustrate a speed ratio selector 60 disposed at a first speed ratio position where the first and second links 148, 150 are fully folded. In this position, the output ring member 266 engages the first and second output discs 230, 232 near the respective outer edges 234, 242 and the input ring member 250 engages the disc rotation axis 210, To the first and second input discs 206, 208, respectively. This arrangement produces the lowest speed ratio, in which case the output shaft 44 has a lower rotational speed than the input shaft 42. The speed ratio selector 60 may be configured to select a first speed ratio position (e.g., as shown in Figures 6 and 8) and a second speed ratio position (e.g., as shown in Figures 9 and 10) Lt; / RTI > can be infinitely adjustable.

Referring to Fig. 11, there is shown a continuously variable transmission 300 configured to be alternately operable to transmit rotational energy between an input shaft 42 and an output shaft 44. As shown in Fig. The input shaft 42 is rotatable with respect to the input rotary shaft 46, and the output shaft 44 is rotatable with respect to the output rotary shaft 48. The input rotary shaft 46 may be disposed substantially parallel to the output rotary shaft 48. [ The position and orientation of the input shaft 42 is generally fixed relative to the output shaft 44.

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 operate in conjunction with each other to transmit rotational torque from the input shaft 42 to the output shaft 44, respectively.

The input drive mechanism 302 may employ a first input disc 306 and a second input disc 308 located adjacent to the first input disc 306. The first input disc 306 may be fixedly attached to the input shaft 42. The second input disc 308 may be fixedly attached to a hollow cylindrical shaped input outer shaft 326 that extends laterally outward from the second input disc 308. The first and second input discs 306 and 308 are rotatable about the input disc rotation axis 310, respectively. The input disk rotational axis 310 substantially coincides with the longitudinal axis of the input shaft 42 and the input outer shaft 326. The input shaft 42 and the input outer shaft 326 may be rotatably supported within the housing 52 by one or more bearings 54.

The first and second input discs 306, 308 extend generally radially outwardly from the input disc rotational axis 310. The edge 312 defines the outer circumference of the first input disk 306. The first input disc 306 may include a first convexly conical first input disc traction surface 314 located adjacent to the second input disc 308. The edge 320 defines an outer perimeter of the second input disc 308. The second input disc 308 may include a second convex conical shaped second input disc traction surface 322 positioned adjacent the first input disc 306. The second input disc 308 can generally be configured as a mirror image of the first input disc 306 in view of FIG.

The axial position of the input outer shaft 326 and the second input disc 308 may be axially fixed relative to the housing 52. [ The input shaft 42 and the first input disc 306 may be axially movable along the input disc rotational axis 310 relative to the second input disc 306 such that the first input disc traction surface 314, So that the distance D1 between the two input disk traction surfaces 322 can be selectively changed. Alternatively, the axial position of the input shaft 42 and the first input disc 306 may be axially fixed relative to the input outer shaft 326 and the second input disc 308, 326 and the second input disc 308 may be axially movable along the input disc rotational axis 310 relative to the input shaft 42 and the first input disc 306.

The input biasing mechanism 329 may be operatively connected to the input shaft 42. The input biasing mechanism 329 is actuated to urge the first input disc 306 toward the second input disc 308. Various biasing mechanisms may be employed, which may include, for example, a spring, such as a coil spring, and a variety of hydraulic, mechanical, and electromechanical devices capable of generating a biasing force.

The input shaft 42 and the input outer shaft 326 may be configured to be rotatable relative to each other or alternatively fixed to rotate with respect to each other. The latter allows axial movement of the input shaft 42 and the input outer shaft 326 relative to each other, for example, while preventing the input shaft 42 and the input outer shaft 326 from rotating relative to each other By using a spline which makes it possible Either the input shaft 42 and the input outer shaft 326 are generally free to move axially relative to each other.

The output drive mechanism 304 may be configured similar to the input drive mechanism 302 and may include a first output disk 330 and a second output disk 330 positioned adjacent the first output disk 330, 332). The first and second output discs 330 and 332 are rotatable about the output disc rotation axis 328, respectively. The first output disc 330 may be fixedly attached to the output shaft 44. The second output disc 332 may be fixedly attached to a hollow, cylindrical, shaped output outer shaft 333 that extends laterally rearward from the second output disc 332. The output disk rotational axis 328 substantially coincides with the 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.

The first and second output discs 330, 332 extend outward generally radially from the output disc rotational axis 328. The edge 334 defines the outer circumference of the first output disc 330. The first output disc 330 may include a first convexly shaped first output disc traction surface 336 disposed adjacent to the second output disc 332. [ The edge 338 defines the outer circumference of the second output disc 332. The second output disc 332 may include a second convexly shaped second output disc traction surface 340 disposed adjacent the first input disc 330. The second output disc 332 may generally be configured as a mirror image of the first output disc 330 in view of FIG.

The axial position of the second output disc 332 may be substantially fixed relative to the housing 52. The output shaft 44 includes an output outer shaft 333 and a second output disc traction surface 342 such that the distance D2 between the first output disc traction surface 336 and the second output disc traction surface 340 can be selectively changed. And may be axially movable along the output disk rotational axis 328 with respect to the output shaft 330. Alternatively, the axial position of the output shaft 44 may be fixed axially relative to the housing 52, and the output outer shaft 333 and the second output disc 332 may be fixed to the output shaft 44 and 1 output disk 330 along the output disk rotational axis 328. The output disk 330 can be moved along the output disk rotational axis 328 in the axial direction.

The output biasing mechanism 341 may be operatively connected to the output shaft 44. The output biasing mechanism 341 operates to urge the first output disc 330 toward the second output disc 332. Various biasing mechanisms may be employed, which may include, for example, a spring, such as a coil, and various hydraulic, mechanical, electromechanical devices capable of generating a biasing force.

The output shaft 44 and the output outer shaft 333 can be configured to be rotatable relative to each other or alternatively rotatably fixed to each other. The latter allows axial movement of the output shaft 44 and the input outer shaft 333 relative to each other, for example, while allowing the output shaft 44 and the output outer shaft 333 to rotate relative to each other, By using a spline which is formed by a plurality of springs. In either case, the output shaft 44 and the output outer shaft 333 are generally free to move axially relative to each other.

The endless drive mechanism 300 may include a ring member 342 operatively connecting the input drive mechanism 302 to the output drive mechanism 304. The ring member 342 can be moved radially with respect to the input drive mechanism 302 and the output drive mechanism 304. [ The radial position of the ring member 342 is selectively adjusted with respect to the input and output drive mechanisms 302 and 304 so that the speed ratio of the continuously variable transmission 300 (e.g., speed ratio = (rotation of the output shaft 44) Speed) / (rotational speed of the input shaft 42)) can be changed.

The speed ratio selector 344 may be operatively 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 position of the ring member 342 relative to the input and output drive mechanisms 302 and 304 to achieve the selected speed ratio. The speed ratio selector 344 may have any of a wide variety of configurations. The speed ratio selector 344 is coupled to the first and second input disks 306 and 308 of the input drive mechanism 302 and to the first and second output disks 330 and 332 of the output drive mechanism 304, Any device capable of adjusting the position of the member 342 may be employed.

The ring member 342 may include a pair of interconnected co-rotating rings. The co-rotating ring includes an input traction ring 346 that engages the first and second input discs 306 and 308 and an output traction ring 348 that engages the first and second output discs 330 and 332 can do. The connecting ring 350, which is generally cylindrical in shape, may rigidly connect the input traction ring 346 to the output traction ring 348. The input and output traction rings 346 and 348 may be disposed substantially perpendicular to the input and output disk rotational accesses 328 and 310.

The input traction ring 346 includes a first traction surface 352 engageable with the first input disc traction surface 314 of the first input disc 306 and a second traction surface 352 engageable with the second input disc traction surface 308. [ Traction surface 354 as shown in FIG. The input traction ring first and second traction surfaces 352 and 354 may be configured as continuous rings. The input traction ring first and second traction surfaces 352 and 354 may be located at a radius 356 from the ring member rotational axis 355. The input traction ring first and second traction surfaces 352 and 354 are disposed on opposite sides of the input traction ring 346 and the first traction surface 352 faces the first input disc 306, The surface 354 faces the second input disc 308.

The output traction ring 348 includes a first traction surface 358 that can engage the first output disc traction surface 336 of the first output disc 330 and a second traction surface 358 that is coupled to the second output disc traction surface 340 And a second traction surface 360, which may be substantially planar. The output traction ring first and second traction surfaces 358, 360 may be configured as continuous rings. The output traction ring first and second traction surfaces 358 and 360 may be located at a radius 362 from the ring member rotational axis 355. [ The output traction ring first and second traction surfaces 358 and 360 are disposed on opposite sides of the output traction ring 348 and the first traction surface 358 faces the first output disc 330, The surface 360 faces the second output disc 332.

The continuously variable transmission 300 is operative to transmit torque from the input shaft 42 to the output shaft 44. The torque from the input shaft 42 is transmitted from the first input disc 306 to the ring member 342 and the first traction ring first traction surface 352 is coupled to the first input disc traction surface 314 And can be transmitted across the contact patch 364. For example, in the configuration in which the input shaft 42 is rotatably fixed to the input outer shaft 326 by a spline, the torque from the input shaft 42 is transmitted to the ring member 342, The traction surface 354 may be passed across the second input contact patch 366 that 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 rotational axis 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 changes.

The ring member 342 transmits torque from the input drive mechanism 302 to the output drive mechanism 304. [ The torque is transmitted from the ring member 342 to the first output disc 330 through the first output contact patch 370 where the output traction ring first traction surface 358 engages the first output disc traction surface 336 Can be delivered. The torque is transmitted from the ring member 342 to the second output disc 332 through the second output contact patch 372 where the output traction ring second traction surface 360 engages the second output disc traction surface 340 Can be delivered. The first and second output contact patches 370 and 372 are located at a radius 374 from the output disk rotational axis 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 changes. The torque transmitted from the ring member 342 to the first output disc 330 may be output through the output outer shaft 333. [

For an arrangement in which the output shaft 44 is rotatably secured to the output outer shaft 333 by, for example, a spline, the torque from the output outer shaft 333 is transmitted across the connection between the two shafts, 44). Alternatively, the torque from the output shaft 44 may be transmitted to the output outer shaft 333 across the connection between the two shafts.

The speed ratio of the continuously variable transmission 300 is selected such that the radial position 368 of the first and second input contact patches 364 and 366 and the radial position 374 of the first and second output contact patches 370 and 372 ) ≪ / RTI > The speed ratio of the continuously variable transmission 300 is determined in part by the radial position of the input traction ring first and second traction surfaces 352 and 354 coupling with the first and second input disk traction surfaces 314 and 322, And the radial position 368 of the first and second input contact patches 364 and 366). As the radial position 368 of the first and second input contact patches 364 and 366 increases, the rotational speed of the output shaft 44 increases with respect to the rotational speed of the input shaft 42. On the other hand, the rotational speed of the output shaft 44 decreases as the radial position 368 of the first and second input contact patches 364, 366 decreases. The output traction ring first and second traction surfaces 370 and 372 are positioned at radial positions that engage the first and second output disc traction surfaces 336 and 340 (i.e., the first and second output contact patches 370, 372) have opposite effects. As the radial position 374 of the first and second output contact patches 370 and 372 decreases, the rotational speed of the output shaft 44 increases relative to the rotational speed of the input shaft 42. On the other hand, the rotational speed of the output shaft 44 decreases as the radial position 374 of the first and second output contact patches 370 and 372 increases.

The speed ratio can be selectively adjusted by shifting the position of the ring member rotational axis 355 relative to the input disk rotational axis 310 and / or the output disk rotational axis 328 such that the ring member 342 is rotated in the first and second A radial position 368 in which the input discs 306 and 308 engage and a radial position 374 in which the ring member 342 engages the first and second output discs 330 and 332. Moving the ring member 342 radially relative to the first and second input discs 304 and 306 results in a corresponding movement of the ring member 342 relative to the first and second output discs 330 and 332 . For example, moving the ring member 342 radially outwardly relative to the first and second input discs 306, 308 may cause the ring member 342 to move to the first and second output discs 330, 332 In the radial direction. Moving the ring member 342 radially inward relative to the first and second input discs 306 and 308 also causes the ring member 342 to move relative to the first and second output discs 330 and 332 Radially outward.

11, the first input contact patch 364 is arranged substantially perpendicular to the first input contact patch vector 376 extending from the first input contact patch 364 to the input disk rotational axis 310 And is arranged substantially perpendicular to the second input contact patch vector 378 extending from the first input contact patch 364 to the ring member rotational axis 355. Similarly, the first output contact patch 370 is arranged substantially perpendicular to the first output contact patch vector 380 extending from the first output contact patch 370 to the output disk rotational axis 328, And is arranged substantially perpendicular to the second output contact patch vector 282 extending from the contact patch 370 to the ring member rotational axis 355. The construction and arrangement of the various components of the continuously variable transmission 300 is such that the sum of the length of the first input contact patch vector 376 and the length of the first output contact patch vector 380 is equal to the length of the contact patch vector 378 And the length of the second output contact patch vector 382 is greater than the length of the second output contact patch vector 382. The following relationship applies 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)

A similar relationship applies to the second input contact patch 366 and the second output contact patch 372 as well. For example, the length of the first input contact patch vector length extending from the second input contact patch 366 to the input disk rotational axis 310 and substantially perpendicular to the second input contact patch 366, The sum of the lengths of the first output contact patch vector length extending from the output contact patch 372 to the output disk rotational axis 328 and substantially perpendicular to the second output contact patch 372 is greater than the sum of the lengths of the first input contact patch vector 366 The length of the second input contact patch vector length extending from the second output contact patch 372 to the ring member rotational axis 355 and substantially perpendicular to the second input contact patch 366, Is greater than at least one of the length of the second output contact patch vector length extending to the first output contact patch (355) and substantially perpendicular to the second output contact patch (372).

11 and 12, the speed ratio selector 344 may be used to selectively adjust the speed ratio of the continuously variable transmission 300. [ Figure 11 shows a speed ratio selector 344 disposed at a first speed ratio position. In this position the ring member 342 engages the first and second output discs 330 and 332 near the respective outer edges 334 and 338 and the ring member 342 engages the input disc rotational axis 310 To the first and second input discs 306 and 308, respectively. This configuration produces the lowest speed ratio (e.g., speed ratio = (rotational speed of output shaft 44) / (rotational speed of input shaft 42)), And has a rotation speed lower than that of the shaft 42.

Figure 12 shows a speed ratio selector 344 disposed at a second speed ratio position. In this position, the ring member 342 engages the first and second input discs 306, 308 near the respective outer edges 312, 320 and the ring member 346 engages the output disc rotational axis 328 To the first and second output discs 330 and 332, respectively. This configuration produces the highest speed ratio, in which case the output shaft 44 has a higher rotational speed than the input shaft 42. The speed ratio selector 60 may be infinitely adjusted between the first speed ratio position (e.g., as shown in Figure 11) and the second speed ratio position (as shown, for example, in Figure 12) .

As previously described, the input biasing mechanism 329 and the output biasing mechanism 341 may include various configurations. One example of such an arrangement is shown in Figures 13 and 14 which is shown between ring member 342 and first and second input discs 306 and 308 and between first and second output discs 330 and 332 And a hydraulic system used to generate a biasing force to control the generated traction force. This particular configuration of the input and output biasing mechanisms 329 and 341 uses hydraulic pressure to move the second input disk 308 toward the first output disk 306 and the second output disk 332 to the first output disk & To generate a biasing force for biasing the biasing member 330 toward the biasing force. The input biasing mechanism 329 may include a hydraulic reservoir 384 configured to apply a biasing force to the second input disc 308. The hydraulic reservoir 384 may be defined by a rear surface 385 of the second input disc 308 and a cover 386 located adjacent to the second input disc 308. The second input disc 308 may be slidably coupled to the input shaft 42. The cover 386 may include a generally cylindrical shaped flange 387 that slidably engages a generally cylindrical shaped flange 388 extending from the rear surface 385 of the second input disk 308. A seal 389 such as an O-ring is provided between the flange 387 of the cover 386 and the flange 388 of the second input disc 308 to prevent the hydraulic fluid from escaping the hydraulic reservoir 384. [ . Seal 390 may be employed to seal openings that may occur between cover 386 and input shaft 42 and openings that may occur between second input disc 308 and input shaft 42.

The output biasing mechanism 341 may be configured similar to the input biasing mechanism 329. [ For example, the output biasing mechanism 341 may include a hydraulic reservoir 391 configured to apply a biasing force to the second output disc 332. The hydraulic reservoir 391 may be defined by a rear surface 392 of the second output disc 330 and a cover 393 located adjacent to the second output disc 330. The second input disc 330 may be slidably engaged with the output shaft 44. The cover 393 may include a generally cylindrical shaped flange 394 that slidably engages a generally cylindrical shaped flange 395 extending from the rear surface 392 of the second output disk 330. A seal 389 such as an O-ring is provided between the flange 394 of the cover 393 and the flange 395 of the second output disc 330 to prevent the hydraulic fluid from escaping the hydraulic reservoir 391 . Seal 390 may be employed to seal openings that may occur between cover 393 and output shaft 44 and openings that may occur between second output disc 330 and output shaft 44.

The fluid passageway 396 may fluidly connect the hydraulic reservoir 384 of the input biasing mechanism 329 to the hydraulic reservoir 391 of the output biasing mechanism 341. The hydraulic pump 397 may be fluidly connected to the fluid passageway 396. The hydraulic pump 397 controls the pressure of the hydraulic fluid present in the system and thus the ring member 342 and the first and second input discs 306 and 308 and the first and second output discs 330 and 332, In order to control the traction force generated between them.

The input and output biasing mechanisms 329 and 341 generally operate in conjunction with each other to provide a coherent biasing force. The volume of the hydraulic reservoir 384, 391 may vary as the speed ratio of the continuously variable transmission 300 changes. For example, FIG. 13 illustrates a continuously variable transmission 300 disposed at a first speed ratio position, and FIG. 14 illustrates a speed ratio selector 344 disposed at a second speed ratio position. When the speed ratio selector 342 is placed in the first speed ratio position (i.e., FIG. 13), the ring member 342 is rotated about the respective outer edges 334 and 338 to the first and second output discs 330 and 332 And the ring member 342 engages the first input disc 306 and the second input disc 308 closer to the input disc rotational axis 310. [ This arrangement creates a maximum spacing between the first input disc 306 and the second input disc 308 and a minimum spacing between the first output disc 330 and the second output disc 332. [ When the speed ratio selector 342 is placed in the second speed ratio position (i.e., Fig. 14), the ring member 342 is rotated about the respective outer edges 312 and 320 to the first and second input discs 306 and 308 And the ring member 346 engages the first and second output discs 330, 332 closer to the output disc rotational axis 328. This arrangement creates a minimum spacing between the first input disc 306 and the second input disc 308 and a maximum spacing between the first output disc 330 and the second output disc 332.

13) to the second speed ratio position (e.g., FIG. 14), the second input disc 308 is moved to the first input disc (not shown) 306 so that the volume of the hydraulic reservoir 384 is increased and the second output disc 332 is moved away from the first output disc 330 so that the volume of the hydraulic reservoir 391 Can be reduced. On the other hand, when the ring member 342 is moved from the second speed ratio position (i.e., Fig. 14) toward the first speed ratio position (i.e., Fig. 13), the second input disc 308 moves to the first input disc 306 The volume of the hydraulic reservoir 384 is increased and the second output disk 332 is moved toward the first output disk 330 so that the volume of the hydraulic reservoir 391 can be reduced have. When the ring member 342 is circulated between various speed ratio positions, the hydraulic fluid may be transmitted back and forth through the fluid passage 396 between the hydraulic reservoir 384 and the hydraulic reservoir 391.

Referring to FIG. 15, an alternatively configured exemplary continuously variable transmission 400 is operable to transmit rotational energy between the input shaft 42 and the output shaft 44. The input shaft 42 is rotatable with respect to the input rotary shaft 46, and the output shaft 44 is rotatable with respect to the output rotary shaft 48. The input rotary shaft 46 may be disposed substantially parallel to the output rotary shaft 48. The input rotary shaft 46 can be offset from the output rotary shaft 48 by a distance 50. [ The input and output shafts 42 and 44 may each be rotatably supported within the housing 52 by bearings 54, respectively. The position and orientation of the input shaft 42 is generally fixed relative to the output shaft 44.

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 operate in conjunction with each other to transmit rotational torque from the input shaft 42 to the output shaft 44, respectively.

The input drive mechanism 402 may employ an input disk 406 that is rotatable relative to the input rotational shaft 46. The input disk 406 may be fixedly attached to the input shaft 42 or formed integrally therewith. The input disk 406 extends generally radially outward from the input rotational axis 46. [ The edge 408 defines the outer circumference of the input disk 406. The input disk 406 may include a first traction surface 410, which is a generally convex conical shaped input disk, and an opposing input disk second traction surface 412. The input disk first and second traction surfaces 410, 412 may generally be mirror-facing in the view of FIG.

The output drive mechanism 404 may be configured similar to the input drive mechanism 402 and may include an output disk 414 that is rotatable relative to the output rotary shaft 48, for example. The output disk 414 may be fixedly attached to the output shaft 48 or formed integrally therewith. The output disk 414 extends radially outwardly from the output rotation axis 48 of the rotation generally. The edge 416 defines the outer periphery of the output disk 414. The output disk 414 may include a generally convex conical shaped output disk first traction surface 418 and an opposing output disk second traction surface 420. The output disc first and second traction surfaces 418 and 420 may generally be mirror-facing in the view of FIG.

The continuously variable transmission 400 may include a ring member 422 operatively connecting the input drive mechanism 402 to the output drive mechanism 404. The ring member 422 can be moved radially with respect to the input drive mechanism 402 and the output drive mechanism 404. The radial position of the ring member 422 is selectively adjusted with respect to the input and output drive mechanisms 402 and 404 so that the speed ratio (for example, the speed ratio = (rotational speed of the output shaft 44) (The rotational speed of the rotor 42)).

The ring member 422 may include a pair of interconnected co-rotating rings. The co-rotating ring 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 connection ring 430 may be used to rigidly connect the input traction ring 426 to the output traction ring 428. The input and output traction rings 426 and 428 may be disposed substantially parallel to one another and substantially perpendicular to the input and output rotational shafts 46 and 48.

The input traction ring 426 may include an input ring traction surface 432 that can engage 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 the ring member rotational axis 436. [

The output traction ring 428 may include an output ring traction surface 438 that can be engaged with the output disc 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 rotational axis 436. The output ring traction surface 438 and the input ring traction surface 432 may be disposed at opposite axial ends of the ring member 422 and the input ring traction surface 432 may generally be disposed at the output ring traction surface 438, .

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 generally be configured as an annular disc having an outer periphery 444 and an inner periphery 446. [ The intermediate traction ring 442 may be arranged substantially parallel to the input and output traction rings 426 and 428 and may be substantially perpendicular to the ring member rotational axis 436. The outer periphery 446 includes a helical spline 448 or similar coupling mechanism that slidably engages a corresponding coupling mechanism, for example, a helical spline 450, located on the inner periphery 452 of the coupling ring 430 can do. The helical splines 448 and 450 are configured so that the intermediate traction ring 442 is coupled 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 rotational axis 436 (That is, along the ring member rotational axis 436) in the axial direction. The helical splines 448 and 450 act to rotatably secure the intermediate traction ring 442 to the ring member 422 such that the intermediate traction ring rotates substantially simultaneously with the input and output traction rings 426 and 428 do.

15 and 17, moving the ring member 422 radially along the radial travel path 455 causes the ring member 422 and the intermediate traction member 422 to move in the opposite direction along the axial travel path 451, Causing a corresponding axial movement of the ring 442. For example, the input ring traction surface 432 is moved radially outward along the input disk first traction surface 410 and the output ring traction surface 438 is moved along the output disk first traction surface 418 in the radial direction Moving inwardly, moving the ring member 422 radially upwardly from the radial position shown in Fig. 17 to the radial position shown in Fig. 15 (as viewed from the perspective of Figs. 15 and 17) Causing the traction ring 426 to move to the right (as viewed from the perspective of Figures 15 and 17). This also allows the intermediate input traction surface 454 to move radially outward along the input disk second traction surface 412 and the intermediate output traction surface 456 to move radially inward along the output disk second traction surface 420 When moving, it causes the intermediate traction ring 442 to move to the left (as viewed from the perspective of FIGS. 15 and 17). Moving the ring member 422 radially downward (as viewed from the perspective of FIGS. 15 and 17) causes the input traction ring 426, the output traction ring 438 and the intermediate traction ring 442 to move Causing the member 422 to move axially along the axial travel path 451 in a direction opposite to the direction when moving the member 422 radially upward.

The intermediate traction ring 442 may include an intermediate input traction surface 454 that can be engaged with the input disc 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 rotational axis 436.

The intermediate traction ring 442 may include an intermediate output traction surface 456 that can be engaged with the output disc 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 a radius 458 from the ring member rotational axis 436. Intermediate output traction surface 458 and intermediate input traction surface 454 may be disposed on opposite sides of intermediate traction ring 442 and intermediate input traction surface 454 may be disposed on opposite sides of intermediate output traction surface 456, Direction.

The ring member 422 can be moved radially along the radial travel path 455 relative to the input drive mechanism 402 and the output drive mechanism 404. The radial position of the ring member 422 is selectively adjusted with respect to the input and output drive mechanisms 402 and 404 so that the speed ratio of the continuously variable transmission 400 (e.g., speed ratio = (rotation of the output shaft 44) Speed) / (rotational speed of the input shaft 42)).

The speed ratio selector 460 may be operatively 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 position of the ring member 422 relative to the input and output drive mechanisms 402 and 404 to achieve the selected speed ratio. The speed ratio selector 460 may have any of a wide variety of configurations. The speed ratio selector 460 employs any device capable of adjusting the position 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 can do.

The continuously variable transmission 400 is operative to transmit torque to the output shaft 44 from the input shaft 42. The torque from the input shaft 42 is transmitted from the input disc 406 to the ring member 422 and the input disc traction surface 432 is coupled to a first input contact patch 462 that engages the input disc first traction surface 410. [ Lt; / RTI >

The torque can be transmitted across the first output contact patch 468 from the ring member 422 to the output disc 414 where the output ring traction surface 438 engages the output disc first traction surface 418 . The torque transmitted from the ring member 422 to the output disk 414 may be output through the output shaft 44. [

Torque from the input shaft 42 may also be transmitted from the input disk 406 through the intermediate traction ring 442 to the output disk 414. [ The torque from the input disc 406 can be transmitted across the second input contact patch 474 where the intermediate input traction surface 454 of the intermediate traction ring 442 engages the input disc second traction surface 412 have. Torque is transmitted from the intermediate traction ring 442 to the output disc 414 while the intermediate output traction surface 456 of the intermediate traction ring 442 is coupled to the second output contact patch 476 ). ≪ / RTI > The first and second input contact patches 462 and 474 are located at a radius 478 from the input rotational axis 46. The first and second output contact patches 468 and 476 are located at a radius 480 from the output rotary shaft 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 change as the speed ratio of the continuously variable transmission 400 changes .

The input and output shafts 42 and 44 apply respective torques to 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 torque produces the same opposing forces at the first input and output contact patches 462 and 468 and the second input and output contact patches 474 and 476. [ Force can 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. [

The traction force generated in the first input contact patch 462 and the first output contact patch 468 includes a radial component that urges the ring member 422 into tight contact with the input and output disks 406 and 414 Helping to maintain the position of the ring member 422 relative to the input and output disks 406 and 414. The tangential component transfers a tractive force between the ring member 422 and the input and output discs 406 and 414. The vertical component depends on the geometry of the input disk 406 and the output disk 414 and the circumferential position of the contact patches 462 and 468 relative to each other and the input and output disks 406 and 414 and the ring member 422 Lt; RTI ID = 0.0 > a < / RTI > The input disk second traction surface 412 and the output disk second traction surface 420 are configured to provide a set of forces that balance the forces on opposing input disk first traction surface 410 and output disk first traction surface 418 .

The vector component forces acting on the first and second input contact patches 462 and 474 and the first and second output contact patches 468 and 476 (i.e., radial, tangential, and vertical directions) Is balanced to produce force. The opposing force is generated by the ring member 422 and the intermediate traction ring 442 to pinch the input and output discs 406 and 414 to achieve traction without slippage, 442 and the input and output disks 406 and 414, respectively.

The speed ratio of the continuously variable transmission 400 is selected such that the radial position 478 of the first and second input contact patches 462 and 474 and the radial position 480 of the first and second output contact patches 468 and 476 ) ≪ / RTI > The speed ratio of the continuously variable transmission 400 is such that the input ring traction surface 432 has a radial position in which it engages the input disk first traction surface 410 and that the intermediate input traction surface 454 is in contact with the input disk second traction surface 412, (I. E., The radial position 478 of the first and second input contact patches 462 and 474). ≪ / RTI > As the radial position 478 of the first and second input contact patches 462 and 474 increases, the rotational speed of the output shaft 44 increases relative to the rotational speed of the input shaft 42. [ On the other hand, the rotational speed of the output shaft 44 decreases as the radial position 478 of the first and second input contact patches 462, 474 decreases.

The radial position at which the output ring traction surface 438 engages the output disc first traction surface 418 and the radial position at which the intermediate output traction surface 456 engages the output disc second traction surface 420 And the radial position 480 of the first and second output contact patches 468, 476) have a complex effect on the speed ratio. As the radial position 480 of the first and second output contact patches 468 and 476 decreases, the rotational speed of the output shaft 44 increases with respect to the rotational speed of the input shaft 42. [ On the other hand, the rotational speed of the output shaft 44 decreases as the radial position 480 of the first and second output contact patches 468, 476 increases.

The speed ratio may be selectively adjusted by moving the position of the ring member rotational axis 436 relative to the input rotational axis 46 and / or the output rotational axis 48 such that the ring member 422 is engaged with the input disc 406 And a radial position 480 in which the ring member 422 engages with the output disc 414. When the ring member 422 is moved radially with respect to the input disk 406, a corresponding movement of the ring member 422 relative to the output disk 414 is generated. For example, moving the ring member 422 radially outwardly with respect to the input disk 406 also moves the ring member 422 radially inward relative to the output disk 414. [ Moving the ring member 422 radially inward with respect to the input disk 406, on the other hand, moves the ring member 422 radially outward relative to the output disk 414. [

15, the first input contact patch 462 is arranged substantially perpendicular to the first input contact patch vector 482 extending from the first input contact patch 462 to the input rotational axis 46 And a second input contact patch vector 484 extending from the first input contact patch 462 to the ring member rotational axis 436. Similarly, the first output contact patch 468 is substantially vertically aligned with respect to the first output contact patch vector 486 extending from the first output contact patch 468 to the output rotary shaft 48, And is substantially vertically aligned with respect to the second output contact patch vector 488 extending from the contact patch 468 to the ring member rotational axis 436. The construction and arrangement of the various components of the continuously variable transmission 400 is such that the sum of the length of the first input contact patch vector 482 and the length of the first output contact patch vector 486 is equal to the sum of the length of the first input contact patch vector 484 Length and the length of the second output contact patch vector 488. The following relationship applies 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)

A similar relationship is also applied to the second input contact patch 474 and the second output contact patch 476. For example, the length of the first input contact patch vector length extending from the second input contact patch 474 to the input rotary shaft 46 and aligned substantially perpendicular to the second input contact patch 474, The sum of the lengths of the first output contact patch vector lengths extending from the contact patches 476 to the output rotary shaft 48 and aligned substantially perpendicular to the second output contact patches 476 is taken from the second input contact patches 474 The length of the second input contact patch vector length extending to the ring member rotational axis 436 and substantially perpendicular to the second input contact patch 474 and the length of the second input contact patch vector from the second output contact patch 476 to the ring member rotational axis 436 And the length of the second output contact patch vector length that is substantially perpendicular to the second output contact patch 476. [

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 shows a speed ratio selector 460 disposed at a first speed ratio position. In this position, the ring member 422 is coupled to the input disc 406 near its respective outer edge 408 and the ring member 422 is coupled to the output disc 414 . This configuration produces the highest speed ratio (e.g., speed ratio = (rotational speed of output shaft 44) / (rotational speed of input shaft 42)), And has a rotation speed higher than that of the shaft 42.

Figure 17 shows a speed ratio selector 460 disposed at a second speed ratio position. In this position, the ring member 422 engages the output disc 414 near its outer edge 416 and the ring member 422 engages the input disc 406 closer to the input rotational axis 46 . This arrangement produces the lowest speed ratio, in which case the output shaft 44 has a lower rotational speed than the input shaft 42. The speed ratio selector 460 can be infinitely adjusted between the first speed ratio position (e.g., as shown in FIG. 15) and the second speed ratio position (e.g., as shown in FIG. 17) .

Referring to Fig. 18, an alternate exemplary continuously variable transmission 700 is operable to transmit rotational energy between the input shaft 42 and the output shaft 44. As shown in Fig. The continuously variable transmission 700 is configured similar to the continuously variable transmission 400 but is of an alternative type for controlling the alignment of the intermediate traction ring 702 and the ring member 706 with respect to the input disk 406 and the output disk 414. [ Use a device. Intermediate traction ring 702 and ring member 706 operatively connect input drive mechanism 402 to output drive mechanism 404. The ring member 706 and the intermediate traction ring 702 can be selectively moved in the radial direction simultaneously with respect to the input drive mechanism 402 and the output drive mechanism 404. The radial position of the ring member 706 and the intermediate traction ring 702 is selectively adjusted with respect to the input and output drive mechanisms 402 and 404 so that the speed ratio of the continuously variable transmission 700 (Rotational speed of the output shaft 44) / (rotational speed of the input shaft 42)).

Ring member 706 may comprise a pair of interconnected co-rotating rings. The co-rotating ring 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 disposed substantially parallel to each other and substantially perpendicular to the input and output rotary shafts 46 and 48.

The input traction ring 708 may include an input traction ring support 712 of generally cylindrical shape extending laterally outward from the input traction ring 708. The output traction ring 710 may include an output traction ring support 714 that extends laterally outward from the output traction ring 710. The output traction ring support 714 can be set larger than the input traction ring support 712 (i.e., it can have a larger diameter). Output traction ring support 714 extends around and at least partially overlies input traction ring support 712. The inner periphery 716 of the output traction ring support portion 714 may have a diameter greater than the diameter of the outer periphery 718 of the input traction ring support portion 712 so that the input traction ring support portion 712 and the output traction ring support portion 712 714 are formed. The input and output traction ring supports 712 and 714 are fixedly connected to each other by a radial connector 722 to allow the input traction ring 708 and the output traction ring 710 to be rotated simultaneously.

The input traction ring 708 may include an input ring traction surface 724 that can engage the input disk first traction surface 410. The input ring traction surface 724 may be configured as a continuous ring.

Output traction ring 710 may include an output ring traction surface 726 that can engage output disc 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 to face generally opposite each other.

15 and 16, the continuously variable transmission 700 may include an intermediate traction ring 702 disposed between the input traction ring 708 and the output traction ring 710. The intermediate traction ring 702 can generally be configured as an annular disc having an outer periphery 728 and an inner periphery 730. [ The intermediate traction ring 702 may be generally parallel to the input and output traction rings 708 and 710 and may be substantially perpendicular to the ring member rotational axis 732. The outer periphery 728 may include an input traction ring support 734 of generally cylindrical shape extending laterally outward from the intermediate traction ring 702. An intermediate traction ring support 734 extends at least partially into the ring 720 formed between the output traction ring support 714 and the input traction ring support 712. The outer periphery 736 of the middle traction ring support portion 734 is slidably engageable with the inner periphery 716 of the output traction ring support portion 714. This arrangement allows the intermediate traction ring 702 to move relative to the ring member 706 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, 710 and the ring member rotational axis 732. [ (I.e., along the rotational member rotational axis 732). Alternatively, the inner circumference 738 of the intermediate traction ring support 734 may be slidably engaged with the outer circumference 718 of the input traction ring support 712.

The intermediate traction ring 702 may include an intermediate input traction surface 740 that can be engaged with the input disc second traction surface 412. The intermediate input traction surface 740 may be configured as a continuous ring.

The intermediate traction ring 702 can include an intermediate output traction surface 742 that can be engaged with the output disc second traction surface 420. The intermediate output traction surface 742 may be configured as a continuous ring. Intermediate output traction surface 742 and intermediate input traction surface 740 may be disposed on opposite sides of intermediate traction ring 702 and intermediate input traction surface 740 may be disposed on opposite sides of intermediate output traction surface 742, Direction.

18 and 19, the movement of the ring member 706 in the radial direction along the radial movement path 455 causes the ring member 422 and the intermediate traction member 452 to move in the opposite direction along the axial movement path 451, Causing a corresponding axial movement of the ring 442. For example, the input ring traction surface 724 moves radially outward along the input disk first traction surface 410 and the output ring traction surface 726 extends along the output disk first traction surface 418 in the radial direction Moving the ring member 422 radially upwardly from the radial position shown in FIG. 19 to the radial position shown in FIG. 18 (as viewed in FIGS. 18 and 19) Causing the ring 708 to move to the right (as viewed from the perspective of FIGS. 18 and 19). This also means that the intermediate input traction surface 740 moves radially outward along the input disc second traction surface 412 and the intermediate output traction surface 742 extends radially inward along the output disc second traction surface 420 As it moves, it causes the intermediate traction ring 702 to move to the left (as viewed from the perspective of FIGS. 18 and 19). Moving the ring member 706 radially downward (as viewed from the perspective of FIGS. 18 and 19) causes the input traction ring 708, the output traction ring 710 and the intermediate traction ring 702 to engage the ring member 706 To move in the axial direction along the axial movement path 451 in the direction opposite to the direction when moving upward in the radial direction.

The ring member 706 can be moved in the radial direction along the movement path 455 with respect to the input drive mechanism 402 and the output drive mechanism 404. The radial position of the ring member 706 is selectively adjusted with respect to the input and output drive mechanisms 402 and 404 so that the speed ratio of the continuously variable transmission 700 (e.g., speed ratio = (rotation of the output shaft 44) Speed) / (rotational speed of the input shaft 42)) can be changed.

The speed ratio selector 460 may be operatively connected to the ring member 706 to selectively adjust the speed ratio of the continuously variable transmission 700. [ The speed ratio selector 460 operates to adjust the radial position of the ring member 706 relative to the input and output drive mechanisms 402 and 404 to achieve the selected speed ratio. The speed ratio can be selectively adjusted by moving the position of the ring member rotational axis 473 relative to the input rotational axis 46 and / or the output rotational axis 48, thereby causing the ring member 706 to be rotated relative to the input disk 406 and output A radial position to engage the disc 414 is achieved. Moving the ring member 706 radially with respect 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 moves the ring member 706 radially inward relative to the output disk 414. [ Moving the ring member 706 radially inward with respect to the input disc 406, on the other hand, moves the ring member 706 radially outward relative to the output disc 414.

In particular, a common feature among the various exemplary configurations of the continuously variable transmission is that the input contact patch vector length (e.g., the first input contact patch vector 154 and the first output contact patch vector 154, (The length of the input ring member 158) is greater than the length of the corresponding ring member vector 156, 160 (e.g., the input ring member 102 as shown in FIG. 2). In addition, each exemplary configuration illustrates a ring member having a respective traction surface (e.g., input ring first traction surface 112 as shown in FIG. 1) located at a fixed radius, The radius of the disc traction surface (e.g., the first input disc traction surface 68, as shown in FIG. 1) varies, as this arrangement generally provides the greatest range of drive ratios to be. Alternatively, the radial position of the disk traction surface may be fixed, and the radial position of the ring traction surface may be allowed to vary as a means for adjusting the drive ratio.

20 and 21, an exemplary two-stage continuously variable transmission 500 is operable to transmit rotational energy between the input shaft 42 and the output shaft 44. The two-stage continuously variable transmission 500 may include a first driving mechanism 502 and a second driving mechanism 504. The first and second driving mechanisms 502 and 504 may be arranged in series. The first and second drive mechanisms (502, 504) operate to transmit rotational torque from the input shaft (42) to the output shaft (44). The first and second driving mechanisms 502 and 504 are driven by the speed ratio of the toe-stage continuously variable transmission 500 (for example, the speed ratio = (rotation speed of the output shaft 44) (E.g., the rotational speed of the motor). The two-stage continuously variable transmission 500 may employ a speed ratio selector 506 that can be operated to selectively adjust the speed ratio.

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. The intermediate shaft 508 operatively connects the first drive mechanism 502 to the second drive mechanism 504. [ The input shaft 42 and the output shaft 44 are rotatable with respect to the common rotation axis 510. The position and orientation of the input shaft 42 is generally fixed relative to the output shaft 44.

The first drive mechanism 502 may employ a first input disc 512 and a first output disc 514 located adjacent to the first input disc 512. The first input and output disks 512 and 514 are rotatable about a rotational axis 510, respectively. The first input and output disks 512 and 514 extend generally radially outward from the rotational axis 510. The edge 516 defines the outer circumference of the first input disk 512. The first input disk 512 may include a first input disk traction surface 520 positioned adjacent the input shaft 42 and an opposing inner surface 522 located adjacent the first output disk 514. [ have. The inner surface 522 of the first input disc 62 may have a generally planar surface contour as shown, for example, in FIG. 20, or may include various other contours and / or contours.

Continuing with FIG. 20, edge 524 defines the outer circumference of first output disc 514. The first output disk 514 may include an inner surface 526 located adjacent the first input disk 512 and a first output disk traction surface 528 located opposite the inner surface 526 . The first output disc 514 may generally be configured as a mirror image of the first input disc 512 in view of FIG. Similar to the first input disk 512, the inner surface 526 of the first output disk 514 may have a generally planar surface contour as shown, for example, in FIG. 20, / / ≪ / RTI > The first output disc 514 may be fixedly attached to the intermediate shaft 508.

The first input disc 512 and the first output disc 514 may be rotatably supported relative to each other. For example, the bearing 530 may be disposed between the inner surface 522 of the first input disc 512 and the inner surface 526 of the first output disc 514. The bearing 530 may be integrally formed with the first input disc 512 and the first output disc 514 as shown for example in Figure 20 or may be formed integrally with the inner surface of the first input disc 512 522 and the inner surface 526 of the first output disk 514. The first output disk 514 may be a single disk.

The second drive mechanism 504 may be configured similar to the first drive mechanism 502 and may include a second input disc 532 and a second output disc 532 positioned adjacent to the second input disc 532, Disk 534 as shown in FIG. The second input disc 532 and the second output disc 534 are rotatable relative to the rotational axis 510, respectively. The second input and output disks 532 and 534 extend generally radially outward from the axis of rotation 510.

The edge 536 defines the outer circumference of the second input disc 532. The second output disc 534 may include a second input disc traction surface 538 and an opposing inner surface 540 located adjacent the second output disc 534. [ The inner surface 540 of the second input disc 532 may have a generally planar surface contour as shown, for example, in FIG. 20, or may include various other contours and / or contours. The second input disc 532 may be fixedly attached to the intermediate shaft 508.

The second output disk 534 may be fixedly attached to the output shaft 44. The edge 542 defines the outer circumference of the second output disc 534. The second output disc 534 may include an inner surface 544 positioned adjacent the second input disc 532 and a second output disc traction surface 546 positioned opposite the inner surface 544 . The second output disc 534 may generally consist of a mirror image of the second input disc 532 in view of FIG. Similar to the second input disc 532, the inner surface 544 of the second output disc 534 may have a generally planar surface contour as shown, for example, in FIG. 20, / / ≪ / RTI >

The second input disc 532 and the second output disc 534 may be rotatably supported relative to each other. For example, the bearing 530 may be disposed between the inner surface 540 of the second input disc 532 and the inner surface 544 of the second output disc 534. The bearing 530 may be integrally formed with the second input disc 532 and the second output disc 534 as shown in Figure 20 or may be formed integrally with the inner surface of the second input disc 532 540 and the inner surface 544 of the second output disc 534. In this embodiment,

The first drive mechanism 502 may include a first ring member 548 that is operable to rotatably couple the first input disc 512 to the first output disc 514. The first ring member 548 is rotatable with respect to the first ring member rotational shaft 549. The first ring member rotational shaft 549 is oriented substantially perpendicular to the plane extending through the bearing 588 for rotatably supporting the first ring member 548. [ The first ring member 548 can be moved radially relative to the first input disc 512 and the first output disc 514. [ The radial position of the first ring member 548 is determined by the speed ratio of the first drive mechanism 502 (for example, the first drive mechanism speed ratio = (rotation speed of the output shaft 44) ) Of the first input disk 512 and the first output disk 514 to vary the rotational speed of the first input disk 512 and the first output disk 514.

The second drive mechanism 504 may include a second ring member 550 that is operable to rotatably couple the second input disc 532 to the second output disc 534. The second ring member 550 is rotatable with respect to the second ring member rotational shaft 551. The second ring member rotational shaft 551 is arranged substantially perpendicular to a plane extending through the bearing 588 that rotatably supports the second ring member 550. The second ring member 550 can be moved radially with respect to the second input disc 532 and the second first output disc 534. [ The radial position of the second ring member 550 is set such that the speed ratio of the second drive mechanism 504 (for example, the second drive mechanism speed ratio = (rotation speed of the intermediate shaft 508) (E.g., the rotational speed of the first input disk 532 and the second input disk 532).

The first ring member 548 may comprise a pair of interconnected co-rotating rings. The co-rotating ring includes an input traction ring 552 that engages the first input disc 512 and an output traction ring 554 that engages the first output disc 514 away from the input traction ring 552 . A generally cylindrical connection ring 556 may be used to rigidly connect the input traction ring 552 to the output traction ring 554. The input and output traction rings 552 and 554 generally extend radially inward from the connecting ring 556.

The input traction ring 552 may include a first ring member input traction surface 558 that can engage the first input disc traction surface 520 of the first input disc 512. The output traction ring 554 may include a first ring member output traction surface 560 that can engage the first output disc traction surface 528 of the first output disc 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 the ring member effective rotational axis 566. [ The ring member effective rotation shaft 566 may not coincide with the first ring member rotation shaft 549 or the second ring member rotation shaft 551 depending on the orientation of the bearing 588. [ Rather, the first and second ring member rotary shafts 549, 551 may be oriented at an oblique angle with respect to the ring member effective rotary shaft 566. [ The ring member effective rotational shaft 566 is aligned substantially parallel to the rotational axis 510 of the input shaft 42 and the output shaft 44. The first ring member output traction surface 560 may be located at a radius 564 from the ring member effective rotational axis 566. The first ring member input and output traction surfaces 558 and 560 are disposed on opposite sides of the first ring member 548 and the first ring member input traction surface 558 faces the first input disc 512 The first ring member output traction surface 560 faces the first output disc 514.

The second ring member 550 may be configured similar to the first ring member 548. [ The second ring member 550 may comprise a pair of interconnected co-rotating rings. The co-rotating ring includes an input traction ring 568 that engages a second input disc 532 and an output traction ring 570 that is spaced from the input traction ring 568 and engages a second output disc 534 . A generally cylindrical connecting ring 572 may be used to rigidly connect the input traction ring 568 to the output traction ring 570. The input and output traction rings 568, 570 generally extend radially inward from the connecting ring 572.

The input traction ring 568 may include a second ring member input traction surface 574 that can engage a second input disc traction surface 538 of the second input disc 532. The output traction ring 570 may include a second ring member output traction surface 576 that can engage the second output disc traction surface 546 of the second output disc 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 the ring member effective rotational axis 566. [ The second ring member output traction surface 576 may be located at a radius 580 from the ring member effective rotational axis 566. The first ring member input and output traction surfaces 574 and 576 are disposed on opposite sides of the second ring member 550 and the second ring member input traction surface 574 faces the second input disc 532 The second ring member output traction surface 576 faces the second output disc 534.

The speed ratio selector 506 may be operatively 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 adjusts the radial position of the first ring member 548 relative to the first input disc 512 and the first output disc 514 and adjusts the radial position of the second input disc 532 and the second output disc 534 in the radial direction of the second ring member 550.

The speed ratio selector 506 may have any of a wide variety of configurations. The speed ratio selector 506 includes a first ring member 548 for the first input and output disks 512 and 514 and a second ring member 550 for the second input and output disks 532 and 534, ) Can be adjusted by adjusting the position of the light source (not shown). One example of such a configuration is shown in Figs. 20 to 22. Fig.

20 and 21, the velocity ratio selector 506 may include an actuator 582 having a hollow interior region 584 defined by an interior surface 586 of a generally circular cylindrical shape. The longitudinal axis of the inner surface 586 substantially coincides with the ring member effective rotational axis 566. The first and second ring members 548 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 an interior surface 586 of the actuator 582 using a second bearing 588. [ The bearing 588 may be configured as a separate component or may be formed at least partially integrally with the actuator 582 and / or the first and second ring members 548 and 550.

The actuator 582 may be rotatably attached to the housing 55 using, for example, one or more bearings 590. The bearing 590 may be mounted to the outer periphery 592 of the actuator 582 and the housing 55. The outer periphery 592 of the actuator 582 may have a generally circular shape with a central axis coinciding with the rotational axis 594 of the actuator 582. [ The rotational axis 594 of the actuator 582 may be offset from the ring member effective rotational axis 566 by a distance 596. [ As a result, the thickness T of the actuator 582 is changed in the circumferential direction, for example, as shown in Fig. 19, and the minimum and maximum thicknesses T of the actuators are different from each other in the radially opposite side of the actuator 582 Occurs. The eccentricity between the inner surface 586 and the outer circumference 592 of the actuator 582 causes the radial position of the first and second ring members 548 and 550 to rotate the actuator 582 about its rotational axis 594 To selectively change to the first input and output disks 512 and 514 and the second input and output disks 532 and 534, respectively.

Stage continuously variable transmission 500 operates to transmit torque from the input shaft 42 to the output shaft 44. [ The torque from the input shaft 42 is transmitted from the first input disc 512 to the first ring member 548 and the first ring member input traction surface 558 is coupled to the first input disc traction surface 520 1 < / RTI > input contact patches 598, as shown in FIG. The torque is transmitted from the first ring member 548 to the first output disc 514 via the first output contact patch 600 where the first ring member output traction surface 560 engages the first output disc traction surface 528 Lt; / RTI > The first input contact patch 598 is located at a radius 602 from the input and output shaft rotational axis 510 and the first output contact patch 600 is positioned at a radius 604 from the input and output shaft rotational axis 510 do. The radius 602 of the first input contact patch 598 and the radius 604 of the first output contact patch 600 are changed as the speed ratio of the two-stage continuously variable transmission 500 is changed.

The torque from the first output disc 514 is transmitted to the second input disc 532 along the intermediate shaft 508. The torque from the second input disc 532 is transmitted to the second ring member 550 and the second input contact patch 606 (the second ring member input traction surface) is coupled to the second input disc traction surface 538 by the second ring member input traction surface 574 ). ≪ / RTI > The torque is transmitted from the second ring member 550 to the second output disc 534 and the second output contact patch 608 where the second ring member output traction surface 576 engages the second output disc traction surface 546. [ Lt; / RTI > The second input contact patch 606 is located at a radius 610 from the input and output shaft rotational axis 510 and the second output contact patch 608 is positioned at a radius 612 from the input and output shaft rotational axis 510. [ do. The radius 610 of the second input contact patch 606 and the radius 612 of the second output contact patch 608 vary as the speed ratio of the two-stage continuously variable transmission 500 changes. The torque transmitted from the second ring member 550 to the second output disc 534 may be output through the output shaft 44. [

The speed ratio of the two-stage continuously variable transmission 500 is selected such that the radial positions 602 and 604 of each of the first input and output contact patches 598 and 600 and the radial position 602 and 604 of each of the second input and output contact patches 606 and 608 Lt; / RTI > is a function of the radial positions 610 and 612. The rotational speed of the output shaft 44 increases with respect to the rotational speed of the input shaft 42 as the radial positions 602 and 610 of the first and second input contact patches 598 and 606 increase respectively, The radial positions 604 and 612 of the first and second output contact patches 608 and 612 decrease, respectively. On the other hand, as the radial positions 602 and 610 of the first and second input contact patches 598 and 606 respectively decrease, the rotational speed of the output shaft 44 decreases and the rotational speed of the output contact 44 The radial positions 604 and 612 of the first and second arms 608 and 612 increase, respectively.

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. [ Figure 20 shows a speed ratio selector 506 located at a first speed ratio position. In this position, the first and second ring members 548, 550 engage the first and second output discs 514, 534 near their respective outer edges 524, 542 and the input and output rotary shafts 510 To the first and second input discs 512 and 532, respectively. This configuration produces the lowest speed ratio (e.g., speed ratio = (rotational speed of output shaft 44) / (rotational speed of input shaft 42)), And has a rotation speed lower than that of the shaft 42.

Figure 22 shows a speed ratio selector 506 disposed at a second speed ratio position. In this position, the first and second ring members 548, 550 engage the first and second output discs 514, 534 near their respective outer edges 524, 542 and the input and output rotary shafts 510 To the first and second input discs 512 and 532, respectively. This configuration produces the lowest speed ratio (e.g., speed ratio = (rotational speed of output shaft 44) / (rotational speed of input shaft 42)), And has a rotation speed lower than that of the shaft 42. The speed ratio selector 506 may be configured to select the speed ratio selector 506 between the first speed ratio position (e.g., as shown in Figures 20 and 21) and the second speed ratio position (as shown in Figure 22 for example) Lt; / RTI > The illustrated speed selectors 506 are configured to provide a speed ratio of 1: 1, but may also be configured to provide different speed ratios depending on the design and performance requirements of a particular application.

The configuration of the first drive mechanism 502 of the continuously variable transmission 500 is such that the sum of the radial position 602 of the first input contact patch 598 and the radial position 604 of the first output contact patch 600 is 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 applies to all speed ratios.

A. ((radius 602) + (radius 604)) > (radius 562)

B. ((radius 602) + (radius 604)) > (radius 564)

A similar relationship is also applied to the second driving mechanism 504. For example, the configuration of the second drive mechanism 504 of the continuously variable transmission 500 is configured such that the radial position 610 of the second input contact patch 606 and the radial position 612 of the second output contact patch 608 ) Is made larger than 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 applies to all speed ratios.

A. ((radius 610) + (radius 612)) > (radius 578)

B. ((radius 610) + (radius 612)) > (radius 580)

The scope of the present methods and apparatus is intended to be defined by the following claims. It should be understood, however, that the various disclosed configurations and operations of the continuously variable transmission may be practiced otherwise than as specifically described and illustrated without departing from the spirit or scope thereof. Those skilled in the art will appreciate that various alternatives to the arrangements described herein may be employed in practicing the claims without departing from the spirit and scope of the following claims. The scope of the disclosed systems and methods should not be determined with reference to the above description, but should be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled. Future developments will be made in the industry discussed herein, and the disclosed systems and methods are anticipated and intended to be incorporated into such future examples. Furthermore, all terms used in the claims are intended to be accorded the broadest and most reasonable construc- tion and ordinary meaning that can be understood by those skilled in the art, unless the context clearly indicates otherwise. In particular, the use of a singular article such as "a", "the", "said", etc. should be read to cite one or more of the indicated elements, unless the claim cites the explicit limitations of the contrary. It is intended that the following claims define the scope of the apparatus, and that methods and apparatus within the scope of these claims and their equivalents be covered thereby. In brief, it should be understood that the apparatus is susceptible to modification and variation and is limited only by the following claims.

Claims (29)

In the continuously variable transmission,
An input drive member rotatable relative to an input rotational axis, the input drive member including an input drive member traction surface;
An output drive member rotatable relative to an output rotation axis, the output drive member including an output drive member traction surface;
A ring member rotatable with respect to a ring member rotary shaft
Lt; / RTI >
The ring member
An input ring traction surface located at an input ring traction surface radial distance from the ring member rotational axis, the input ring traction surface having a first input contact patch vector length extending from the input contact patch to the input rotational axis, An input ring traction surface coupled to the input drive member traction surface in the input contact patch oriented perpendicular to a second input contact patch vector length extending to the ring member rotational axis;
An output ring traction surface located at an output ring traction surface radial distance from the ring member rotational axis, the output ring traction surface having a first output contact patch vector length extending from the output contact patch to the output rotation axis, Wherein the output engagement surface engages the output drive member traction surface in the output contact patch oriented perpendicular to a second output contact patch vector length extending to the ring member rotational axis.
/ RTI >
Wherein the sum of the length of the first input contact patch vector and the length of the first output contact patch vector is greater than at least one of the length of the second input contact patch vector and the length of the second output contact patch vector. The method according to claim 1,
Wherein the input drive member includes a first input member and a second input member positioned adjacent the first input member and the second input member is axially spaced relative to the first input member along the input rotational axis Movable,
Wherein the output drive member includes a first output member and a second output member positioned adjacent the first output member and the second output member is axially spaced relative to the first output member along the output rotation axis Continuously variable transmission 3. The method of claim 2,
A speed ratio selector connected to the second input member and the second output member,
And wherein the speed ratio selector is operable to simultaneously move the second input member and the second output member axially along the output rotation axis. The method of claim 3,
The speed ratio selector being operative to simultaneously move the second input member and the second output member in opposite directions. The method according to claim 1,
Wherein the input ring traction surface radial distance is substantially equal to the output ring traction surface radial distance. The method according to claim 1,
Wherein the input drive member is attached to the input shaft for simultaneous rotation with the input shaft and the output drive member is attached to the output shaft for simultaneous rotation with the output shaft. The method according to claim 1,
And the input rotary shaft is displaced from the output rotary shaft. The method according to claim 1,
And the input rotation axis substantially coincides with the output rotation axis. The method according to claim 1,
And the ring member rotation axis is aligned substantially parallel to at least one of the input rotation axis and the output rotation axis. The method according to claim 1,
Wherein a position of the ring member rotation axis is adjustable with respect to at least one of the input rotation axis and the output rotation axis. The method according to claim 1,
And the ring member is axially movable along the ring member rotation axis. In the continuously variable transmission,
An input disk rotatable relative to a disk rotational axis, the input disk comprising an input disk traction surface;
An output disk rotatable relative to a disk rotational axis, the output disk comprising an output disk traction surface;
Wherein the input ring member comprises an input ring traction surface located at an input ring traction surface radial distance from the input rotation axis, the input ring traction surface comprising: And a second input contact patch vector extending from the input contact patch to a second input contact patch vector extending from the input contact patch to a rotational axis, absence;
Wherein the output ring member includes an output ring traction surface located at an output ring traction surface radial distance from the output rotation axis, the output ring traction surface comprising: A first output contact patch vector extending to the rotation axis and a second output contact patch vector extending from the output contact patch to a second output contact patch vector extending in the output contact patch, The output ring member < RTI ID = 0.0 >
Lt; / RTI >
Wherein the sum of the length of the first input contact patch vector and the length of the first output contact patch vector is greater than the length of at least one of the second input contact patch vector and the second output contact patch vector. 13. The method of claim 12,
Wherein the input disk comprises a first input disk and a second input disk positioned adjacent to the first input disk and the second input disk is moved axially with respect to the first input disk along the disk rotation axis, Yes,
Wherein the output disk comprises a first output disk and a second output disk located adjacent to the first output disk and the second output disk is movable in the axial direction along the disk rotation axis, Is attached to the transmission. 14. The method of claim 13,
Wherein the second output disc is axially movable relative to the first output disc along the disc rotation axis. 14. The method of claim 13,
An inner intermediate shaft connecting the first input disc to the first output disc;
An outer intermediate shaft connecting the second input disc to the second output disc,
Further comprising: a continuously variable transmission. 16. The method of claim 15,
A speed ratio selector having a proximal end attached to said outer intermediate shaft and an opposite distal end,
Wherein the speed ratio selector is operable to selectively adjust the position of the disk rotational axis relative to at least one of the input rotational axis and the output rotational axis. 13. The method of claim 12,
Wherein the input ring traction surface radial distance is substantially equal to the output ring traction surface radial distance. 13. The method of claim 12,
Wherein the input ring member is attached to the input shaft for co-rotation with the input shaft, and wherein the output ring member is attached to the output shaft for co-rotation with the output shaft. 13. The method of claim 12,
And the input rotary shaft is displaced from the output rotary shaft. 13. The method of claim 12,
Wherein the disc rotation axis is aligned substantially parallel to at least one of the input rotation axis and the output rotation axis. 13. The method of claim 12,
Wherein the input disk is interconnected to the output disk for simultaneous rotation with the output disk. 13. The method of claim 12,
Wherein the position of the disk rotation axis is adjustable with respect to at least one of the input rotation axis and the output rotation axis. In the continuously variable transmission,
An input disk rotatable relative to a disk rotational axis, the input disk comprising an input disk traction surface;
An output disk rotatable relative to a disk rotational axis, the output disk comprising an output disk traction surface;
A ring member rotatable with respect to a ring member effective rotation shaft
Lt; / RTI >
The ring member
An input ring traction surface located at an input ring traction surface radial distance from the input rotation axis, the input ring traction surface coupling with the input disc traction surface at an input contact patch radial distance from the disc rotation axis; Ring traction surface;
An output ring traction surface located at an output ring traction surface radial distance from the output rotation axis, the output ring traction surface having an output contact traction surface in an output contact patch located at an output contact patch radial distance from the disk rotation axis, The output ring traction surface < RTI ID = 0.0 >
/ RTI >
Wherein the sum of the input contact patch radial distance and the output contact patch radial distance is greater than at least one of the input ring traction surface radial distance and the output ring traction surface radial distance. 24. The method of claim 23,
A speed ratio selector connected to the ring member
And the speed ratio selector is operable to selectively adjust the position of the ring member effective rotation axis relative to at least one of the input rotation axis and the output rotation axis. 25. The method of claim 24,
Wherein the speed ratio selector is rotatably connected to the housing such that the speed ratio selector is rotatable relative to the ring member effective rotation axis, and the ring member is rotatably connected to the speed ratio selector. 26. The method of claim 25,
The speed ratio selector including a circumferentially varying radial offset. 24. The method of claim 23,
Wherein the input drive member is attached to the input shaft for simultaneous rotation with the input shaft and the output drive member is attached to the output shaft for simultaneous rotation with the output shaft. 24. The method of claim 23,
Wherein the ring member effective rotation axis is aligned substantially parallel to at least one of the input rotation axis and the output rotation axis. 24. The method of claim 23,
Wherein the position of the ring member effective rotation axis is adjustable with respect to at least one of the input rotation axis and the output rotation axis.

Images