Infinitely variable speed transmission system with uniform clamping actuation

Abstract

A uniformly clamped actuated infinitely variable speed transmission system is provided, comprising a drive clutch and a driven clutch. Both the drive clutch and the driven clutch include torque-sensitive components. Specifically, the drive clutch includes a drive torque-sensitive component that is operatively connected to a movable drive sheave member of the drive clutch. The drive torque-sensitive component is configured to move the movable drive sheave member relative to a fixed drive sheave member based at least on a torque applied to the drive torque-sensitive component. The driven clutch includes a driven torque-sensitive component that is operatively connected to a movable driven sheave member of the driven clutch. The driven torque-sensitive component is configured to move the movable driven sheave member relative to the fixed driven sheave member based at least on a torque applied to the driven torque-sensitive component.

Description

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority to U.S. Provisional Application Serial No. 62 / 869,181, filed on July 1, 2019, having the same title as hereof, which is incorporated herein by reference in its entirety.

[0003] background

[0004] Continuously variable transmission (CVT) or infinitely variable transmission (IVT) systems, such as those used in off-road utility vehicles, on-road vehicles, golf carts, snowmobiles, industrial machinery, energy conversion / storage equipment, and the like, include a drive clutch (sheave) and a driven clutch (sheave) with torque transmitted between them via a flexible, endless, ring-shaped member (e.g., a belt). In a typical system, the drive clutch utilizes a speed (RPM)-sensitive (centrifugal) drive clutch in operative communication with the engine and a torque-sensitive driven clutch in operative communication with the transmission. These systems are typically balanced so that the belt clamping force generated by the speed-sensitive element in the drive clutch opposes the belt clamping force generated by the torque-sensitive element in the driven clutch.

[0005] Overview

[0006] The following overview is presented by way of example and not by way of limitation. It is provided solely to aid the reader in understanding some aspects of the described subject matter. One embodiment provides a CVT / IVT system that includes torque-sensitive components in both the drive clutch and the driven clutch. Other embodiments provide a sheave having a torque-sensitive component and an actuator arrangement.

[0007] In one embodiment, a UCAS IVT system including a driving clutch and a driven clutch is provided. The driving clutch includes a driving column, a movable drive sheave member, a fixed drive sheave member, and a drive torque-sensitive assembly. The driving column is operably coupled to a motor. The movable drive sheave member is slidably mounted on the driving column. The fixed drive sheave member is axially fixedly mounted on the driving column. The drive torque-sensitive assembly is in operative communication with the movable drive sheave member. The drive torque-sensitive assembly is configured to move the movable drive sheave member relative to the fixed drive sheave member based on at least a torque applied to the drive torque-sensitive assembly. The driving clutch and the driven clutch are configured to transmit torque and rotation between each other using an endless annular member. The driven clutch includes a driven column, a movable driven sheave member, a fixed driven sheave member, and a drive torque-sensitive assembly. The driven column is operably coupled to a powertrain. The movable driven sheave member is slidably mounted on the driven column. The fixed driven sheave member is mounted on the driven post in an axially fixed configuration. The driven torque-sensitive assembly is in operative communication with the movable driven sheave member. The driven torque-sensitive assembly is configured to move the movable driven sheave member relative to the fixed driven sheave member based at least on a torque applied to the driven torque-sensitive assembly.

[0008] In another embodiment, a sheave assembly for an infinitely variable speed shift transmission system with uniform clamping actuation is provided. The sheave assembly includes a sheave, a post, a movable sheave member, a fixed sheave member, a torque-sensitive component, and an actuator. The movable sheave member is slidably mounted on the post. The fixed sheave member is mounted on the post in an axially fixed configuration. The torque-sensitive component is operatively connected to the movable sheave member. The torque-sensitive component is configured to move the movable drive sheave member relative to the fixed sheave member based on a torque applied to a drive torque-sensitive component. The actuator is operably coupled to the movable sheave member to selectively move the movable sheave member independently of the drive torque-sensing component.

[0009] In yet another embodiment, a vehicle having a uniform clamping actuated infinitely variable speed transmission (UCAS IVT) system is provided. The vehicle includes a motor, a powertrain, and a UCAS IVT system. The motor is configured to generate engine torque and rotation. The UCAS IVT system includes a circulating annular member, a driving clutch, a driven clutch, and at least one actuator. The driving clutch includes a drive column, a movable drive sheave member, a fixed drive sheave member, and a drive torque-sensitive assembly. The drive column is operably coupled to the motor. The movable drive sheave member is slidably mounted on the drive column. The fixed drive sheave member is mounted on the drive column in an axially fixed configuration. The drive torque-sensitive assembly is in operative communication with the movable drive sheave member. The drive torque-sensitive assembly is configured to move the movable drive sheave member relative to the fixed drive sheave member based, at least in part, on torque applied to the drive torque-sensitive assembly. The driving clutch and the driven clutch are configured to transmit torque and rotation between each other using the circulating annular member. The driven clutch includes a driven column, a movable driven sheave member, a fixed driven sheave member, and a driven torque-sensitive component. The driven column is operably coupled to a powertrain. The movable driven sheave member is slidably mounted on the driven column. The fixed driven sheave member is mounted on the driven column in an axially fixed configuration. The driven torque-sensitive component is operatively connected to the movable driven sheave member. The driven torque-sensitive component is configured to move the movable driven sheave member relative to the fixed driven sheave member based on a torque applied to the driven torque-sensitive component. At least one actuator is operably coupled to one of the driving clutch and the driven clutch to selectively move one of the movable driving sheave member and the movable driven sheave member independently of the corresponding driving torque sensing component and the driven torque component to achieve at least one of uniform clamping of the cyclic annular member and a ratio change across the entire UCAS IVT system. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] The embodiments may be more readily understood and further advantages and uses of the embodiments will become more apparent when considered in light of the detailed description and the following drawings, in which:

[0012] Figure 1A is a side perspective view of a uniform clamp actuated infinitely variable speed shift transmission (UCASIVT) system according to an exemplary embodiment;

[0013] Figure 1B yes Figure 1A An unassembled side perspective view of the UCAS IVT system;

[0014] Figure 2 yes Figure 1A A cross-sectional top view of the UCAS IVT system in a low-ratio configuration.

[0015] Figure 3 yes Figure 1A A cross-sectional top view of the UCAS IVT system in a high-ratio configuration.

[0016] Figure 4 yes Figure 1A Cross-sectional top view of the UCAS IVT system in the clamping force configuration;

[0017] Figure 5 is a side perspective view of a torque-sensitive assembly of a drive clutch and a driven clutch in a low ratio configuration according to an exemplary embodiment;

[0018] Figure 6 is a side view of a torque-sensitive assembly of a drive clutch and a driven clutch in a high ratio configuration according to an exemplary embodiment;

[0019] Figure 7 is a side view of a torque-sensitive assembly of a driving clutch and a driven clutch in a torque-reversing configuration according to an exemplary embodiment;

[0020] Figure 8 is a graph of conveyor belt forces of a UCAS IVT system according to an exemplary embodiment;

[0021] Figure 9 is a side perspective view of another UCAS IVT system according to an exemplary embodiment;

[0022] Figure 10 yes Figure 9 A cross-sectional top view of the UCAS IVT system;

[0023] Figure 11 yes Figure 9 an unassembled side perspective view of a drive clutch of a UCAS IVT system; and

[0024] Figure 12 is a block diagram of a vehicle incorporating a UCAS IVT system according to an exemplary embodiment.

[0025] According to common practice, the various described features are not drawn to scale but are drawn to emphasize specific features relevant to the subject matter being described. Reference characters denote like elements throughout the figures and text.

[0026] Detailed description

[0027] In the detailed description below, reference is made to the accompanying drawings, which form a part of this detailed description, and wherein the specific embodiments in which the present invention can be put into practice are shown by way of illustration. These embodiments are described in sufficient detail to enable those skilled in the art to put them into practice, and it should be understood that other embodiments can be utilized and can be changed without departing from the spirit and scope of the present invention. Therefore, the following detailed description is not to be considered as having a limiting meaning, and the scope of the present invention is limited only by the claims and their equivalents. Terms such as, but not limited to, "operably coupled" or "operationally connected" used herein relate to the connection between elements and / or components. These terms include both the direct connection between elements and / or components and the connection that occurs by providing one or more elements and / or components of a cause-and-effect reaction between elements and / or components.

[0028] Embodiments provide a Uniform Clamping Actuated Infinitely Variable Speed ​​Transmission (UCAS IVT) system that utilizes torque elements in both the drive and driven clutches of the IVT. The UCAS IVT system provides a dual torque sensitive system that reduces / eliminates the need for actuators to provide full belt clamping force in order to transfer or couple torque / power between sheaves in some cases in the IVT system. Advantages of this design include the ability to use smaller actuators to selectively control shifting of the IVT, lower force requirements that allow the actuators to complete shift sequences more quickly, and less energy required to power the actuators. Additionally, some embodiments of the UCAS IVT system are capable of sensing torque in both directions, capable of driving (from the drive clutch to the driven clutch) and reverse driving (from the driven clutch to the drive clutch).

[0029] Figures 1A to 3 An embodiment of the UCAS IVT system 100 is shown. In particular, Figure 1A shows a side perspective view of the UCAS IVT system 100, Figure 1B shows an unassembled side view of the UCAS IVT system 100, and Figure 2 A cross-sectional side view of the UCASIVT system is shown.

[0030] In this exemplary embodiment, the UCAS IVT system 100 includes a drive clutch 102 and a driven clutch 140 (or variable diameter pulley or sheave) that are rotatably coupled to transmit torque via an endless endless member 130. The endless endless member 130 can be, but is not limited to, a conveyor belt. Each sheave (or pulley) 102 and 140 includes its own torque-sensitive assembly (200 and 240, respectively), which will be discussed in further detail below. The drive clutch 102 is configured to be operably coupled to a motor (e.g., Figure 11502 ), and the driven clutch 140 is configured to be operatively coupled to a vehicle (e.g. Figure 12 The UCAS IVT system 100 further includes an actuator 120 operatively coupled to the drive clutch 102. The drive clutch 102 and the driven clutch 140 each include a pair of fixed sheave members and a movable sheave member (as discussed below) that selectively change the position of the recirculating annular member 130 relative to the central axes 121 and 157 (as discussed below) of the respective clutches 102 and 140. Figure 3 ) to selectively change the gear ratio of the corresponding clutches 102 and 140. In an embodiment, the actuator 120 is used to control the gear ratio of the driving clutch 102 and the driven clutch 140 independently of the torque forces experienced by the driving clutch 102 and the driven clutch 140.

[0031] The drive clutch 102 includes a movable drive sheave member 101 and a fixed drive sheave member 103. A drive cam 104 (a cam sensitive to drive torque) is axially and rotationally fixed (coupled) to the movable drive sheave member 101. The drive cam 104 is also axially and rotatably free about a central axis 106 (or drive post 106) of the drive clutch 102. The fixed drive sheave member 103 is coupled to the drive post 106. In one embodiment, the fixed drive sheave member 103 (the stationary drive sheave member) is axially fixed, but rotationally free about the drive post 106. In another embodiment, in which the fixed drive sheave member 103 is not coupled to the movable drive sheave member 101, the fixed drive sheave member 103 can be rotatably fixed to the drive post 106. Furthermore, in embodiments where the fixed drive sheave member 103 is rotatably coupled to the movable drive sheave member 101, tie drive rollers 109 are used that are mounted on a portion of the movable drive sheave member 101 via a mounting rod 107 and a retaining pin 111 arrangement. The tie drive rollers 109 are received in retaining tracks 180 of the fixed drive sheave member 103. The retaining tracks 180 associated with the fixed drive sheave member 103 can be straight, angled, or curved. This exemplary embodiment of a sheave tie-down configuration increases torque sensitivity and facilitates conversion of forward and reverse torques.

[0032] The movable drive sheave member 101 driving the clutch 102 is slidably mounted on the drive column 106 while being free to rotate about the drive shaft 106. In this example, an actuator 120 is coupled to the actuator cup 117. The actuator 120 is configured to selectively push the drive cam 104 to move the movable drive sheave member 101 closer to the fixed drive sheave member 103, thereby engaging (clamping) the conveyor belt 130, as discussed below.

[0033] In the exemplary embodiment, the drive clutch 102 also includes a bearing 124 positioned between an end portion of the drive post 106 and an opening in an end hub portion of the fixed drive sheave member 103. A retaining clip 123 positioned within a recess in the drive post partially holds the bearing 124 in a desired position on the drive post 106. Spacer members 125 and 126 are used to establish a preset minimum spacing between the fixed drive sheave member 103 and the movable drive sheave member to establish a sheave travel limit under high-ratio conditions. In embodiments where tension on the conveyor belt 130 is maintained at full low-ratio, the spacer members 125 and 126 are not required.

[0034] The drive torque-sensitive assembly 200 of the drive clutch 102 includes the drive cam 104, a drive biasing seat member 132, a drive biasing member 116, and a drive spoke 114. The drive biasing seat member 132 is received within the hub portion of the movable drive sheave member 101 around the drive post 106 and is positioned to engage a first end of the drive biasing member 116. In this embodiment, the drive biasing member 116 is a spring. The second end of the drive biasing member 116 is positioned to engage the center ring portion of the drive spoke 114. The drive biasing member 116 provides a selective biasing force on the drive spoke 114 away from the end of the hub portion of the movable drive sheave member 101. The drive spoke 114 includes arms extending in opposite directions from the center ring portion. The drive cam rollers 112 are rotatably mounted on the arms of the drive spoke 114. In this exemplary embodiment, the drive cam rollers 112 are mounted to the arms via a C-clip 113 and washer 115 arrangement. The retaining clip 133 at least partially prevents the drive spoke 114 from moving axially along the drive post 106. Additionally, the spline arrangement between the inner surface of the center ring portion of the drive spoke 114 and the drive post 105 locks the rotation of the drive spoke 114 to the rotation of the drive post 106.

[0035] The drive cam 104 is coupled to the movable drive sheave member 101 via fasteners 134. As discussed above, the actuator cup 117 engages the drive cam 104 and is used by the actuator 120 to selectively move the movable drive sheave member 101 closer to the fixed drive sheave member 103. In this embodiment, a bearing 136 is positioned around a portion of the actuator cup 117 and an interior portion of the drive cam 104 to allow rotation between the actuator cup 117 and the drive cam 104. Retaining members 137 and 138 serve, in part, to maintain the position of the bearing 136 in a desired position.

[0036] The driven clutch 140 has a similar construction to the driving clutch 102, including a movable driven sheave member 143 and a fixed driven sheave member 141 mounted on a driven post 146. The fixed driven sheave member 141 is axially fixed to the driven post 146, while the movable driven sheave member 143 is axially movable on the driven post 146. The movable driven sheave member 143 of the driven clutch 140 is slidably mounted on the driven post 146. In one embodiment, the movable driven sheave member 143 is also free to rotate about the driven post 146.

[0037] The driven clutch 140 includes a driven torque-sensitive assembly 240, which includes a driven cam 144, a driven spoke 150, a driven biasing member 160, and a driven biasing seat member 164. The driven cam 144 (torque-sensitive cam) is axially and rotatably fixed (coupled) to the movable driven sheave member 143 via fasteners 161. The driven cam 144 is also axially and rotatably free about the central driven post 146. The driven biasing seat member 164 is received in the hub portion of the movable driven sheave member 143 around the driven post 146 and is positioned to engage a first end of the driven biasing member 160. In this embodiment, the driven biasing member 160 is a spring. The second end of the driven biasing member 160 is positioned to engage the central ring portion of the driven spoke 150. The driven biasing member 160 provides a selective biasing force on the driven spoke 150 away from the end of the hub portion of the movable driven sheave member 143. The driven spoke 150 includes arms extending in opposite directions from the center ring portion. The driven cam rollers 152 are rotatably mounted on the arms of the driven spoke 150. In the exemplary embodiment, these driven cam rollers 152 are mounted on the arms via a C-clip 151 and washer 155 arrangement. The retaining clip 162 at least partially prevents the driven spoke 150 from axial movement along the driven post 146. In addition, the spline arrangement between the inner surface of the center ring portion of the driven spoke 150 and the driven post 146 locks the rotation of the driven spoke 150 with the rotation of the driven post 146.

[0038] Similar to the drive clutch 102 discussed above, in an embodiment, the fixed driven sheave member 141 of the driven clutch 140 is axially fixed to the central shaft 146, but is rotationally free. In another embodiment where the fixed driven sheave member 141 is not coupled to the movable driven sheave member 143, the fixed driven sheave member 141 is rotationally fixed to the driven post 146. In one embodiment where the fixed driven sheave member 141 is rotationally coupled to the movable driven sheave member 143, tie rollers 166 are used, which are mounted on a portion of the movable driven sheave member 141 via a mounting rod 167 and a retaining pin 168 arrangement. The tie rollers 166 are received in corresponding retaining tracks 169 of the fixed driven sheave member 141. Also included in the driven clutch 140 is a bearing 174 that is mounted around an end portion of the driven post 146 and is positioned to engage a portion of the hub portion of the fixed driven sheave member 141. The bearing 174 is axially secured in position on the driven post 146 by at least one retaining member 176. Spacer members 170 and 172 are used to establish a predetermined minimum spacing between the fixed driven sheave member 141 and the movable driven sheave member 143. The spacer members 170 and 172 are only required when the system is configured so that the conveyor belt 130 can be completely disengaged from the clutch 102.

[0039] Figure 2 The cross-sectional view of FIG1 shows the UCAS IVT system 100 at a low ratio. In this configuration, the movable drive sheave member 101 of the drive clutch 102 is spaced apart from the fixed drive sheave member 103, allowing the conveyor belt 130 to operate at a small effective diameter around the central axis 121 of the drive clutch 102 on the sheave faces 101a and 103a of the respective drive sheave members 101 and 103. The magnitude of the force exerted between the sheave faces 101a and 103a and the conveyor belt sides 130a and 130b varies with the magnitude of the torque applied to the drive column 106 and the magnitude of the torque resisted by the driven clutch 140. When no torque is supplied to the system, the only force supplied to the sides 130a and 130b of the conveyor belt 130 is a result of the drive biasing member 116 and the driven biasing member 160 (compression springs) in the respective drive torque sensing assembly 200 and driven torque sensing assembly 240 (discussed below) in each respective drive clutch 102 and driven clutch 140.

[0040] The function of the biasing members 116 and 160 is to induce a clamping force between the sheave faces 101a and 103a of the driving clutch 102 and the belt faces 141a and 143a of the driven clutch 140 until the torque elements in each sheave 102 and 140 (the driving torque sensing assembly 200 and the driven torque sensing assembly 240, respectively) are able to synchronize and transmit the clamping force. In embodiments, it may be desirable to minimize the biasing force provided by the biasing members 116 and 160. In a particular application, the biasing member (compression spring) may be omitted entirely from the clutch 102 and / or 140 to which the actuator 120 is connected. Thus, although Figure 2 The embodiment shown in FIG. 1 shows the actuator 120 being used to operate the torque sensing assembly 200 of the driving clutch 102 , but in another embodiment, the actuator may be applied to the driven clutch 104 .

[0041] Figure 3 The UCAS IVT system 100 is shown in a high-ratio configuration. In a typical drive clutch, the high-ratio configuration is achieved by a torque force that causes the movable drive sheave member 101 to move closer to the fixed drive sheave member 103, which causes the conveyor belt 130 to travel upward along the sheave faces 101a and 103a of the respective movable drive sheave members 101 and 103, so that the conveyor belt 130 is positioned further away from the center axis 121 of the drive clutch 102. In an embodiment, the torque force in the UCAS IVT system 100 does not necessarily cause the movable sheave member of either sheave to move. The overall goal of this configuration is to balance the clamping loads of the drive clutch 102 and the driven clutch 140, regardless of the position of the movable sheave member or the effective conveyor belt winding diameter (ratio) around either sheave. The sheave movement (shifting) is intended to be controlled by the actuator 120. Some residual shift bias / clamping force bias may exist or even be designed into the system to preset the UCAS IVT system 100 to a desired position.

[0042] Furthermore, there are times when the motor does not provide sufficient engine torque to the drive column 106 to move its corresponding movable sheave member 101 toward the fixed sheave member 103 and thereby provide a clamping force on the conveyor belt 130. In such situations, it may be desirable to utilize the drive clutch 102 to introduce a clamping force on the conveyor belt 130. For example, in the event of engine braking of an associated vehicle while traveling down a steep hill with the motor at idle, the coupling torque between the driven clutch 140 and the drive clutch 102 may be advantageous in slowing the vehicle. In engine braking situations, the torque from the drive train is greater than the torque provided by the motor. Because embodiments include a dual torque sensing system, at least a portion of the clamping force is provided by the torque sensing assembly 200 (discussed below) of the drive clutch 102 as a result of the torque received from the conveyor belt 130.

[0043] Figure 4 The engine braking condition is shown. The actuator 120 of the UCAS IVT system 100 can be actuated to generate an actuation force, thereby pushing the movable drive sheave member 101 of the drive clutch 102 toward the fixed drive sheave member 103 to generate a drive clutch clamping force on the endless ring member 130. Figure 4 As shown, once an initial clamping force is established to establish torque transmission between clutches 102 and 140, the driving clutch clamping force can be further generated as a result of the torque received from the driven clutch 140 via the transmission belt. Therefore, in this exemplary embodiment, the clamping force provided by the driven clutch 140 can be added to the clamping force provided by the actuator 120. This allows the force required to be provided by the actuator 120 to be relatively small.

[0044] As discussed above, the torque forces in the UCAS IVT system of the embodiment do not necessarily cause the movable sheave members of the drive clutch 102 or the driven clutch 140 to move. The overall goal of this configuration is to balance the clamping loads of the drive clutch 102 and the driven clutch 140, regardless of the position of the associated movable sheave members or the effective belt winding diameter (ratio) around either sheave. Sheave movement (shifting) is intended to be controlled by the actuator. Some residual shift bias / clamping force bias may exist or even be designed into the system to preset the UCAS IVT system 100 to a desired position.

[0045] refer to Figure 5, provides an illustration of how the torque sensing assemblies 200 and 240 of the respective drive clutch 102 and driven clutch 140 operate. As shown and described above, the drive torque sensing assembly 200 of the drive clutch 102 includes the drive cam 104. The drive cam 104 includes a cam hub portion 104a having cutout portions 205 that define cam profile surfaces 207a and 207b. The drive cam roller 112, which is rotatably mounted on the arms of the drive spoke 114, is positioned within corresponding cutout portions 205 in the drive cam 104 to engage corresponding cam profile surfaces 207a and 207b of the drive cam 104. Rotation and torque are input into the cam profile surfaces via the drive cam roller 112.

[0046] Similarly, the driven cam 144 of the driven torque sensing assembly 240 of the driven clutch 140 includes a cutout portion 245 ( Figure 5 The cam hub portion 144a (only one cutout portion is shown) defines cam profile surfaces 247a and 247b. The driven cam roller 152 of the driven spoke 150 engages the cam profile surfaces 247a and 247b. Rotation and torque are input into the cam profile surfaces through the driven cam roller 152 of the driven spoke 150.

[0047] As discussed above, the driven biasing member 160 (compression spring) provides an initial clamping force between the sheave face and the conveyor belt face to allow synchronization of torque-sensitive components. The large clamping load is generated by the torque sensing assemblies 200 and 240. Also as discussed above, in some embodiments, both torque sensing assemblies 200 and 240 include biasing members 116 and 160, while in other embodiments, only one torque sensing assembly includes a biasing member because the initial force can be provided by the actuator 120 if desired. Therefore, in some embodiments, a compression spring is used in only one of the torque sensing assemblies that is not in operative communication with the actuator.

[0048] Figure 5 A low-ratio configuration is shown, in which torque and speed (rotation) are introduced into the drive post 106 of the driving clutch 102 via the motor. The torque and rotation, indicated by arrow 220, are then transmitted to the cam assembly 104 via the drive cam roller 112 of the driving spoke 110. The torque and rotation are then transmitted via the transmission belt 130 to the driven cam 144 of the driven torque sensing assembly 240 of the driven clutch 140. The driven cam 144, in turn, transmits the torque and rotation (as indicated by arrow 242) to the spoke 150, which is coupled to the driven post 146, which transmits the torque and speed to the driveline.

[0049] Figure 6The high-ratio configuration of the torque-sensing assemblies 200 and 240 of the respective driving clutch 102 and driven clutch 140 is shown. As with the low-ratio configuration examples discussed above, torque and rotation are introduced into the drive post 106 of the driving clutch 102 via a motor or power source. The torque and rotation, indicated by arrow 222, are then transmitted to the driving cam 104 via the drive cam roller 112 of the drive spoke 114. In this high-ratio configuration, the drive cam roller 112 has already moved along the cam profile surface 207a. The torque and rotation are then transmitted via the endless ring member 130 to the driven cam 144 of the driven torque-sensing assembly 240 of the driven clutch 140. The driven cam 144 of the driven clutch 140, in turn, transmits the torque and rotation, indicated by arrow 244, to the driven spoke 150, which is coupled to the driven post 146 of the driven clutch 140 to transfer the torque and rotation to the driveline.

[0050] exist Figure 6 In a high ratio configuration, the drive biasing member 116 of the drive torque sensing assembly 200 is shown. The drive biasing member 116 provides a force load that is in addition to the clamping load generated by the torque cam element of the drive torque sensing assembly 200. The biasing member 116 provides an initial clamping force between the sheave face and the belt face in each clutch to allow synchronization of torque-sensitive elements. However, large clamping loads can be generated by the torque cam element of the drive torque sensing assembly 200. As discussed above, in one embodiment, only the clutch 102 or 140 that is not in communication with the actuator 120 requires a biasing member or compression spring.

[0051] Figure 7The figure shows a reverse torque configuration for the torque sensing assemblies 200 and 240 of the respective driving clutches 102 and 140. In this reverse torque configuration, torque and rotation are transferred from the powertrain to the driven post 146 of the driven torque sensing assembly 240 of the driven clutch 140. For this reverse drive to occur, the rotational speed of the driven post 146 divided by the belt contact diameter (CVT ratio) of the driving clutch 102 and the driven clutch 140 must be greater than the rotational speed of the driving post 106. As shown, the torque and rotation transferred to the driven post 146 of the driven clutch 140 causes the driven spoke 150 to rotate its arms toward the cam profile surface 247b, thereby causing the driven cam roller 152 to engage the cam profile surface 247b. This is indicated by arrow 246. The torque and rotation of the driven cam 144, via the driven cam roller 152, are then transferred to the driving cam 104 of the driving torque sensing assembly 200 of the driving clutch 102 via the endless ring member 130. This torque and rotation causes the drive cam 104 to rotate so that the cam profile surface 207b will engage the drive cam roller 112 of the drive spoke 114 of the torque sensing assembly 200. This is indicated by arrow 222. The drive cam roller 112 engaging the cam profile surface 107b of the drive cam 104 will exert a force on the drive spoke 114 and the drive post 106 to rotate as shown.

[0052] The angled cam profile surfaces 247a and 247b in each cutout portion 245 of the driven cam 144 of the driven clutch 140 act on the associated driven cam roller 152 of the driven spoke 150 to generate a belt clamping force in the driven clutch 140. Based on the torque input provided on the UCAS IVT system 100, the driving torque sensitive components 200 and the driven torque sensitive components 240 in the respective driving clutch 102 and the driven clutch 140 generate variable clamping loads in the respective driving clutch 102 and the driven clutch 140.

[0053] In an embodiment, the cam angles of the angled cam profile surfaces 207a, 207b, 247a, and 247b of each respective drive cam 104 and driven cam 144 are variable based on the corresponding operating diameter of the endless ring member 130 (conveyor belt). Furthermore, the cam angles of the angled cam profile surfaces 207a, 207b, 247a, and 247b of each cam 104 and 144 are configured to produce equivalent conveyor belt clamping loads on each of the drive clutch 102 and the driven clutch 140 for all relative conveyor belt operating diameter / IVT ratios. In an embodiment, the effective "shift force" in each clutch 102 and 140 is equal for all relative conveyor belt operating diameter / IVT ratios and torque inputs. Furthermore, to change the conveyor belt operating diameter / IVT ratio, a supplemental force must be provided by an external actuator (e.g., actuator 120). The actuator 120 may include electric actuation, hydraulic actuation, pneumatic actuation, magnetic actuation, and the like.

[0054] Embodiments of the UCAS IVT system 100 are useful because they employ a simple, elegant approach to generating the correct belt clamping load between each clutch assembly 102 and 140 and the conveyor belt 130. The required belt clamping load on each clutch 102 and 140 is directly proportional to the torque being carried / transmitted by the sheaves (pulleys). As the torque on each clutch 102 and 140 increases, the torque-sensitive components 200 and 240 generate more belt clamping load. As the torque on each clutch 102 and 140 decreases, the associated torque-sensitive components 200 and 240 generate less belt clamping load. The torque-sensitive components 200 and 240 in each clutch 102 and 140 can be customized to precisely generate the correct belt clamping load. The belt clamping load in each clutch 102 and 140 is maintained at an optimal level for any torque transmitted by the sheaves / belt. Furthermore, due to the optimized belt clamping load, heat generated by the belt / sheave assembly interface is kept as low as possible. The belt clamping load in each clutch 102 and 140 can be tailored to produce a net-zero or balanced level of shift force. For any belt run diameter combination and transmitted torque level, neither clutch 102 or 140 necessarily tends to overpower the other, forcing a change in belt run diameter across clutch 102 or 140. The belt clamping required to transmit power across each clutch 102 and 140 is generated by the associated torque-sensitive components 200 and 240. If an actuator 120 (electronic, hydraulic, pneumatic, or magnetic) is used to facilitate the shift function (a change in belt run diameter across either pulley), the force required by the actuator 120 is significantly reduced. If speed-sensitive (centrifugal) components (e.g., flyweights) are used to facilitate the shift function, the size of these components can be significantly reduced.

[0055] refer to Figure 8 , a graph 300 of forces for a UCAS IVT system is shown. Graph 300 illustrates sheave displacements of driven clutch 140 and drive clutch 102 for a given conveyor belt force in an exemplary embodiment.

[0056] In another embodiment, a large clamping load of the IVT is mechanically achieved using a predetermined configuration of a speed-sensitive element (such as, but not limited to, a flyweight) in the drive clutch and a torque-sensitive element in the driven clutch. The clamping load generated by the speed-sensitive element in the drive clutch opposes the clamping load generated by the torque-sensitive element in the driven clutch. In a dual torque-sensitive embodiment in both the drive and driven clutches, the driven clutch can be configured to bias to a low ratio (wherein the driven clutch clamping force is greater than the drive clutch clamping force for any magnitude of torque transmitted across the IVT). In yet another embodiment, the torque-sensitive element in the drive clutch is used to reduce the clamping requirements of the speed-sensitive element. This embodiment allows for a reduction in the size of the speed-sensitive element, a reduction in the radial arrangement of the speed-sensitive element, and a reduction in the overall packaging requirements of the speed-sensitive element.

[0057] Figures 9 to 11 Another embodiment of the UCAS IVT 400 is shown. In particular, Figure 9 shows a side perspective view of the UCAS IVT 400, and Figure 10 A cross-sectional top view of a UCAS IVT 400 is shown. Figure 11 Further shown is an unassembled side view of a drive clutch 402 of the UCAS IVT 400. Similar to the UCAS IVT 100 discussed above, the UCAS IVT 400 includes a drive clutch 402 and a driven clutch 440 that are operatively connected to transmit torque and rotation via an endless endless member (e.g., a conveyor belt 431).

[0058] The driven clutch 440 includes a fixed driven sheave member 442 that is mounted in an axially and rotationally fixed connection on a driven post 446. A movable driven sheave member 444 is slidably mounted on the driven post 446. As with the above-described embodiments, the driven clutch 440 also includes a driven torque-sensitive assembly that includes a driven cam 460 and a driven spoke 450 arrangement. Similar to the embodiments discussed above, a driven cam roller 452 mounted on an arm of the driven spoke 450 engages an angled cam profile surface 462 formed in the driven cam 460. The driven spoke 450 is rotationally locked to the rotation of the drive post 433. The driven torque-sensitive assembly also includes a biasing member 464 (compression spring) similar to the biasing members described in the above-described embodiments.

[0059] The drive clutch 402 includes a fixed drive sheave member 410 mounted in an axially and rotationally fixed connection on a drive post 433. A movable drive sheave member 412 is slidably mounted on the drive post 433. An idler bearing 407 is mounted on the drive post 433 between the fixed drive sheave member 410 and the movable drive sheave member 412. Positioned between the movable drive sheave member 412 and the drive post 433 is a spacer 409 that allows the movable drive sheave member 412 to slide axially out of contact with the idler bearing 407. The spacer 409 abuts against a shoulder of the drive post 433 via a drive spider 430 having a lock nut 421.

[0060] The movable drive sheave member 412 in this embodiment includes two cam assemblies. The first cam assembly is part of a drive torque-sensitive assembly (which operates similarly to the torque-sensitive assembly described above). The drive torque-sensitive assembly includes a drive spoke 430 and a drive cam 406. The drive spoke 430 is rotatably fixed to the drive post 433. The roller 420 is rotatably coupled to the end of the arm of the drive spoke 430 and is positioned within the cutout section 425 of the drive cam 406. As in the above embodiment, the roller 420 of the drive spoke 430 selectively engages the angled cam profile surface of the cutout section 425 of the drive cam to transmit torque and rotation. The drive cam 406 is coupled to the movable drive sheave member 412 via fasteners 417.

[0061] The second cam assembly is part of the actuation system to selectively move the movable drive sheave member 412 independently of the drive torque-sensitive assembly. The actuation assembly includes an actuation cam 404. The actuation cam 404 has a cutout section 411 or portion and a roller-guide cutout section 405. A roller 428 rotatably mounted on an arm of an actuation spoke 426 is positioned within the roller-guide cutout section 405 of the actuation cam 404. A bearing 432 is positioned between the post extension end portion 406a of the drive cam 404 and the actuation spoke 426 to allow the actuation spoke to rotate relative to the drive cam 404. The bearing 432 and the actuation spoke 426 are retained on the post extension end portion 406a of the drive cam 406 via retaining members 427 and 429.

[0062] The spoke guide 435 having extended spoke guide arms 435a and 435b is rotatably and axially locked to the chassis (not shown) using fasteners. The center portion of the spoke guide 435 is mounted on the post extension end portion 404a of the actuator cam 404 via retaining members 436 and 437. The spoke guide arms 435a and 435b are received in the cutout section 411 of the actuator cam 404 to reach the actuator spoke 426. The sleeve bushing 423 in the channel of the actuator spoke 426 receives the ends of the spoke guide arms 435a and 435b. When the actuator cam 404 pivots (rotates) due to the travel of the actuator 470, the spoke guide 435 prevents the actuator spoke 427 from rotating. The actuator spoke 426 is limited to axial travel and transmits axial force (originating from the actuator 470 ) to the actuator cam 404 (which rotates at a high speed) via bearings 432 . The axial travel of the actuator spoke 426 is transferred to the movable drive sheave member 412 .

[0063] As discussed, the torque-sensitive components in the drive clutch 402 and the driven clutch 440 operate similarly to the torque-sensitive components 200 and 240 described above. However, in this embodiment of the UCAS IVT 400, a different actuation arrangement is used in the drive clutch 402. The actuation arrangement includes an actuator 470 and an actuation cam 404 arrangement. An elongated actuation member 472 having an attachment member 474 is operably coupled to the actuator 470. The attachment member 474 is pivotally coupled to an actuation bracket 466. The actuation bracket 466 is connected to the actuation cam 404, which pivots relative to the actuation cam spoke 426 to convert the rotational torque from the actuation cam 404 into a linear force on the actuation spoke 426, and ultimately, into a linear force on the movable drive sheave member 412 of the drive clutch 402. The actuation bracket 466 rotates the actuation cam 404 via rotational movement of the actuator 470. As the actuator 470 rotates the actuation cam 404, the cam roller 428 of the actuation spoke 426 seats in the angled roller guide cutout section 405 of the actuation cam 404. Rotation of the actuation cam 404 causes the actuation spoke 426 and the actuator bearing 432 to move axially. Because the movable drive sheave member 412 is in operative communication with the actuation spoke 426 via the drive cam 406, axial movement of the actuation spoke 426 causes axial movement of the movable drive sheave member 412. Thus, in this embodiment, in addition to the high clamping force generated by the torque load on the drive cam 406 and the drive spoke 430, rotation of the drive cam 404 via the actuator 470 serves to achieve a desired supplemental clamping pressure on the conveyor belt 431 at the drive clutch 402.

[0064] As described above, the actuator can be operably coupled to its associated sheave in either a direct or indirect connection configuration. In the indirect connection configuration, an intermediate mechanical system between the actuator and the associated sheave can be used to achieve the desired mounting position of the actuator, to convert the linear actuator motion into rotational motion or vice versa, and to utilize a mechanical advantage (force multiplier) between the actuator and the associated sheave.

[0065] As discussed above, in some embodiments, the actuator can be coupled to either the drive clutch or the driven clutch. In embodiments where one of the drive clutch or the driven clutch does not have an associated actuator, a biasing member (compression spring) is used to induce the belt clamping load. In embodiments that include actuators for both the drive clutch and the driven clutch, a biasing member may not be included.

[0066] In embodiments, a large clamping load on any sheave (only the minimum clamping load required to transmit power—no shift loads and no actuator loads) can be achieved via the belt through one or more torque-sensitive elements, speed-sensitive elements, and biasing / spring elements. Furthermore, embodiments allow the large clamping load in each clutch on the UCAS IVT to be balanced (large drive clutch clamping = large driven clutch clamping) or biased (large drive clutch clamping < large driven clutch clamping or large drive clutch clamping > large driven clutch clamping) compared to the other clutches.

[0067] refer to Figure 12 , shows a vehicle 500 using an exemplary embodiment of a UCAS IVT. The vehicle is shown as including a motor 502 that provides engine torque and rotation. The drive column of the UCAS IVT's drive clutch 102 is operably coupled to the motor 502. A transmission belt 130 transmits torque and rotation between the drive clutch and a driven clutch 140. The driven clutch 140 includes a driven column that is operably coupled to transmit torque and rotation to the powertrain. The powertrain in this example includes a transmission 510, a rear drive shaft 522, a rear differential 524, rear half shafts 526a and 526b, and wheels 528a and 528b. In this example, the powertrain also includes a front drive shaft 516, a front differential 521, front half shafts 518a and 518b, and front wheels 520a and 520b.

[0068] As described above, the actuator 120 controls the drive clutch 102 to achieve ratio changes on the system 100 or 400. The controller 504 controls the actuator 120 based on operating instructions stored in memory and sensor information received by the sensors 506. The sensors 506 may include motor sensors, transmission sensors, brake sensors, gear selection sensors, throttle position sensors, ground speed sensors, inclination sensors, temperature sensors, suspension travel sensors, and the like.

[0069] Typically, the controller 504 may include any one or more of a processor, a microprocessor, a digital signal processor (DSP), an application specific integrated circuit (ASIC), a field programmable gate array (FPGA), or equivalent discrete or integrated logic circuits. In some exemplary embodiments, the controller 504 may include multiple components, such as any combination of one or more microprocessors, one or more controllers, one or more DSPs, one or more ASICs, one or more FPGAs, and other discrete or integrated logic circuits. The functions attributed to the controller 504 herein may be embodied as software, firmware, hardware, or any combination thereof. The controller 504 may be part of a system controller, such as an engine control unit or a transmission control unit, or a component controller. The memory may include computer-readable operating instructions that, when executed by the controller, provide the functionality of the UCAS IVT system. The computer-readable instructions may be encoded in the memory 507. Memory 507 may include computer-readable storage media, including any volatile, non-volatile, magnetic, optical, or electronic media, such as, but not limited to, random access memory (RAM), read-only memory (ROM), non-volatile RAM (NVRAM), electrically erasable programmable ROM (EEPROM), flash memory, or any other storage media.

[0070] Exemplary embodiments

[0071] Example 1 includes a UCAS IVT system comprising a driving clutch and a driven clutch. The driving clutch includes a driving column, a movable drive sheave member, a fixed drive sheave member, and a drive torque-sensitive assembly. The driving column is operably coupled to a motor. The movable drive sheave member is slidably mounted on the driving column. The fixed drive sheave member is mounted on the driving column in an axially fixed configuration. The drive torque-sensitive assembly is in operative communication with the movable drive sheave member. The drive torque-sensitive assembly is configured to move the movable drive sheave member relative to the fixed drive sheave member based on at least a torque applied to the drive torque-sensitive assembly. The driving clutch and the driven clutch are configured to transmit torque and rotation between each other using an endless annular member. The driven clutch includes a driven column, a movable driven sheave member, a fixed driven sheave member, and a drive torque-sensitive assembly. The driven column is operably coupled to a powertrain. A movable driven sheave member is slidably mounted on the driven post. A fixed driven sheave member is mounted on the driven post in an axially fixed configuration. A driven torque-sensitive assembly is in operative communication with the movable driven sheave member. The driven torque-sensitive assembly is configured to move the movable driven sheave member relative to the fixed driven sheave member based on at least a torque applied to the driven torque-sensitive assembly.

[0072] Example 2 includes the UCAS IVT system of Example 1, further comprising at least one actuator operably coupled to one of the drive clutch and the driven clutch to selectively move one of the movable drive sheave member and the movable driven sheave member independently of the corresponding drive torque sensing assembly and the driven torque assembly to achieve at least one of uniform clamping of the cyclic annular member and a ratio change on the system.

[0073] Example 3 includes the UCAS IVT system of Example 2, wherein at least one of the driving clutch and the driven clutch further comprises an actuating spoke and an actuating cam. The actuating spoke includes an actuating roller. The actuating spoke is configured to move axially. The actuating cam has a roller guide cutout section. The actuating roller is received within the roller guide cutout section of the actuating cam. The actuator is operably coupled to the actuating cam to selectively rotate the actuating cam so that the actuating spoke moves an associated one of the movable drive sheave member and the movable driven sheave member independently of an associated one of the corresponding driving torque sensing assembly and the driven torque assembly.

[0074] Example 4 includes the UCAS IVT system of Example 3, further comprising an actuating elongated member, an attachment member, and an actuating bracket. The actuating elongated member is operably coupled to the actuator. The attachment member is operably coupled to an end of the actuating elongated member. The actuating bracket is operably coupled to the actuating cam. The attachment member is pivotally coupled to the actuating bracket.

[0075] Example 5 includes the UCAS IVT system of Example 2, wherein the at least one actuator is configured to urge one of the movable drive sheave member and the movable driven sheave member to achieve uniform clamping of the endless ring member.

[0076] Example 6 includes the UCAS IVT system of Example 2, further comprising at least one sensor, at least one memory, and at least one controller. The at least one sensor is configured to generate sensor information. The at least one memory is configured to store at least operating instructions. The controller is configured to control the actuator based on the stored operating instructions and the sensor information.

[0077] Example 7 includes the UCAS IVT system of any of Examples 1-6, wherein the drive torque-sensitive component further comprises a drive spoke, a drive cam roller, and a drive cam. The drive spoke is coupled to the drive post. The rotation of the drive spoke is fixed to the rotation of the drive post. The drive spoke includes at least one drive spoke arm. The drive cam roller is rotatably coupled to each drive spoke arm. The drive cam is coupled to a movable drive sheave member. The drive cam has at least one cutout portion that forms a drive cam profile surface. Each drive cam roller is positioned within a cutout portion of at least one cutout portion. Each drive cam roller is configured to engage an associated drive cam profile surface to transmit torque and rotation between the drive spoke and the drive cam.

[0078] Example 8 includes the UCAS IVT system of any of Examples 1-7, wherein the drive torque-sensitive component further comprises a drive biasing member configured to apply a selective biasing force on the movable drive sheave member to induce a clamping force on the endless ring member.

[0079] Example 9 includes the UCAS IVT system of any of Examples 1-8, wherein the component sensitive to driven torque includes a driven spoke, a driven cam roller, and a driven cam. The driven spoke is coupled to the driven post. The rotation of the driven spoke is fixed to the rotation of the driven post. The driven spoke includes at least one driven spoke arm. The driven cam roller is rotatably coupled to each driven spoke arm. The driven cam is coupled to a movable driven sheave member. The driven cam has at least one cutout portion that forms a driven cam profile surface. Each driven cam roller is positioned within a cutout portion of at least one cutout portion. Each driven cam roller is configured to engage an associated driven cam profile surface to transmit torque and rotation between the driven spoke and the driven cam.

[0080] Example 10 includes the UCAS IVT system of any of Examples 1-9, wherein the driven torque-sensitive assembly further comprises a driven biasing member configured to exert a selective biasing force on the movable driven sheave member to induce a clamping force on the endless ring member.

[0081] Example 11 includes a clutch assembly for an infinitely variable speed transmission system with uniform clamping actuation. The clutch assembly includes a clutch, a column, a movable sheave member, a fixed sheave member, a torque-sensitive component, and an actuator. The movable sheave member is slidably mounted on the column. The fixed sheave member is mounted on the column in an axially fixed configuration. The torque-sensitive component is operatively connected to the movable sheave member. The torque-sensitive component is configured to move the movable drive sheave member relative to the fixed sheave member based on torque applied to the drive torque-sensitive component. The actuator is operatively coupled to the movable sheave member to selectively move the movable sheave member independently of the drive torque-sensing component.

[0082] Example 12 includes the clutch assembly of Example 11, wherein the clutch is a drive clutch, and further wherein the column is configured to be in operative communication with a motor.The movable sheave member and the fixed sheave member are configured to be in operative communication with an endless endless member.

[0083] Example 13 includes the clutch assembly of Example 11, wherein the clutch is a driven clutch, and further wherein the column is configured to be in operative communication with a powertrain. The movable sheave member and the fixed sheave member are configured to be in operative communication with an endless endless member.

[0084] Example 14 includes the clutch assembly of any of Examples 11-13, wherein the torque-sensitive assembly further comprises a spoke, a cam roller, and a cam. The spoke is coupled to the post. The rotation of the spoke is fixed to the rotation of the post. The spoke includes at least one arm. A cam roller is rotatably coupled to each arm. The cam is coupled to a movable sheave member. The cam has at least one cutout portion that forms a cam profile surface. Each cam roller is positioned within a cutout portion of the at least one cutout portion. Each cam roller is configured to engage an associated cam profile surface to transmit torque and rotation between the spoke and the cam.

[0085] Example 15 includes the clutch assembly of Example 11, further comprising an actuating spoke and an actuating cam. The actuating spoke includes an actuating roller. The actuating spoke is configured to move axially. The actuating cam has a roller guide cutout section. The actuating roller is received within the roller guide cutout section of the actuating cam. An actuator is operably coupled to the actuating cam to selectively rotate the actuating cam, thereby causing the actuating spoke to move the movable sheave member independently of the torque sensing assembly.

[0086] Example 16 includes the clutch assembly of Example 15, comprising an actuating elongated member, an attachment member, and an actuating bracket. The actuating elongated member is operably coupled to the actuator. The attachment member is operably coupled to an end of the actuating elongated member. The actuating bracket is operably coupled to the actuating cam. The attachment member is pivotally coupled to the actuating bracket.

[0087] Example 17 includes the clutch assembly of any of Examples 11-14, wherein the at least one actuator is configured to urge the movable sheave member to move the movable sheave member.

[0088] Example 18 includes a vehicle having a uniform clamping actuated infinitely variable speed transmission (UCAS IVT) system. The vehicle includes a motor, a powertrain, and a UCAS IVT system. The motor is configured to generate engine torque and rotation. The UCAS IVT system includes a circulating annular member, a driving clutch, a driven clutch, and at least one actuator. The driving clutch includes a drive column, a movable drive sheave member, a fixed drive sheave member, and a drive torque-sensitive assembly. The drive column is operably coupled to the motor. The movable drive sheave member is slidably mounted on the drive column. The fixed drive sheave member is mounted on the drive column in an axially fixed configuration. The drive torque-sensitive assembly is in operative communication with the movable drive sheave member. The drive torque-sensitive assembly is configured to move the movable drive sheave member relative to the fixed drive sheave member based, at least in part, on torque applied to the drive torque-sensitive assembly. The driving clutch and the driven clutch are configured to transmit torque and rotation between each other using the circulating annular member. The driven clutch includes a driven column, a movable driven sheave member, a fixed driven sheave member, and a driven torque-sensitive component. The driven column is operably coupled to a powertrain. The movable driven sheave member is slidably mounted on the driven column. The fixed driven sheave member is mounted on the driven column in an axially fixed configuration. The driven torque-sensitive component is operatively connected to the movable driven sheave member. The driven torque-sensitive component is configured to move the movable driven sheave member relative to the fixed driven sheave member based on a torque applied to the driven torque-sensitive component. At least one actuator is operably coupled to one of the driving clutch and the driven clutch to selectively move one of the movable driving sheave member and the movable driven sheave member independently of the corresponding driving torque sensing component and the driven torque component to achieve at least one of uniform clamping of the cyclic annular member and generating a ratio change on the UCAS IVT system.

[0089] Example 19 includes the vehicle of Example 18, further comprising at least one sensor, at least one memory, and a controller. The at least one sensor is configured to generate sensor information. The at least one memory is configured to store at least operating instructions. The controller is configured to control the actuator based on the stored operating instructions and the sensor information.

[0090] Example 20 includes the vehicle of any of Examples 17-19, wherein the at least one actuator is configured to urge one of the movable drive sheave member and the movable driven sheave member to selectively move the one of the movable drive sheave member and the movable driven sheave member.

[0091] Although specific embodiments have been shown and described herein, it will be understood by those skilled in the art that any arrangement intended to achieve the same purpose may be substituted for the specific embodiments shown. This application is intended to cover any modifications or variations of the present invention. It is, therefore, intended that the present invention be limited only by the claims and their equivalents.

Claims

1. A uniform clamp actuated infinitely variable speed transmission (UCAS IVT) system, the UCAS IVT system comprising: Drive clutch, including: a drive column operatively coupled to the motor, a movable drive sheave member slidably mounted on the drive column, a fixed drive sheave member mounted on the drive post in an axially fixed configuration, and a drive torque-sensitive component in operative communication with the movable drive sheave member, the drive torque-sensitive component being configured to move the movable drive sheave member relative to the fixed drive sheave member based at least on a torque applied to the drive torque-sensitive component; The driven clutch is configured to transmit torque and rotation between each other using an endless annular member, the driven clutch comprising: a driven column operatively coupled to the driveline, a movable driven sheave member slidably mounted on the driven post, a fixed driven sheave member mounted on the driven post in an axially fixed configuration, and a driven torque-sensitive component in operative communication with the movable driven sheave member, the driven torque-sensitive component being configured to move the movable driven sheave member relative to the fixed driven sheave member based at least on a torque applied to the driven torque-sensitive component, wherein the driven torque-sensitive component comprises: ---a driven spoke coupled to the driven post, the rotation of the driven spoke being fixed to the rotation of the driven post, the driven spoke comprising at least one driven spoke arm; --- a driven cam roller rotatably coupled to each driven spoke arm; and a follower cam coupled to the movable follower sheave member, the follower cam having at least one cutout portion, the at least one cutout portion forming a follower cam profile surface, each follower cam roller positioned within a cutout portion of the at least one cutout portion, each follower cam roller configured to engage an associated follower cam profile surface to transmit torque and rotation between the follower spider and the follower cam; and At least one actuator operably coupled to one of the drive clutch and the driven clutch to selectively move one of the movable drive sheave member and the movable driven sheave member independently of corresponding drive torque sensitive components and driven torque sensitive components to achieve at least one of uniform clamping of the recirculating annular member and a ratio change on the UCAS IVT system.

2. The UCAS IVT system according to claim 1, wherein: At least one of the driving clutch and the driven clutch further comprises: an actuation spoke comprising an actuation roller, the actuation spoke being configured to move axially; and an actuating cam having a roller guide cutout section, the actuating roller being received within the roller guide cutout section of the actuating cam, the actuator being operably coupled to the actuating cam to selectively rotate the actuating cam, thereby causing the actuating spoke to move the movable drive sheave member and the associated one of the movable driven sheave members independently of the associated one of the drive torque sensitive component and the driven torque sensitive component.

3. The UCAS IVT system according to claim 2, further comprising: an actuation elongate member operably coupled to the actuator; an attachment member operably coupled to an end of the actuation elongated member; and An actuation bracket is operably coupled to the actuation cam, and the attachment member is pivotally coupled to the actuation bracket.

4. The UCAS IVT system according to claim 1, wherein: The at least one actuator is configured to urge one of the movable drive sheave member and the movable driven sheave member to achieve one of uniform clamping of the endless ring member and producing a ratio-variable clamping bias on the UCAS IVT system.

5. The UCAS IVT system according to claim 1, further comprising: at least one sensor for generating sensor information; at least one memory for storing at least operating instructions; and A controller is configured to control the actuator based on stored operating instructions and the sensor information.

6. The UCAS IVT system according to claim 1, wherein: The component sensitive to driving torque also includes: a drive spoke coupled to the drive post, the drive spoke rotation being fixed to the drive post rotation, the drive spoke comprising at least one drive spoke arm; a drive cam roller rotatably coupled to each drive spoke arm; a drive cam coupled to the movable drive sheave member, the drive cam having at least one cutout portion forming a drive cam profile surface, each drive cam roller positioned within a cutout portion of the at least one cutout portion, each drive cam roller configured to engage an associated drive cam profile surface to transmit torque and rotation between the drive spoke and the drive cam.

7. The UCAS IVT system according to claim 1, wherein: The component sensitive to driving torque also includes: A drive biasing member is configured to exert a selective biasing force on the movable drive sheave member to induce a clamping force on the endless ring member.

8. The UCAS IVT system according to claim 1, wherein: The component sensitive to driven torque also includes: A driven biasing member is configured to exert a selective biasing force on the movable driven sheave member to induce a clamping force on the endless ring member.

9. A clutch assembly for an infinitely variable speed transmission system with uniform clamp actuation, the clutch assembly comprising: A clutch comprising: --column; a movable sheave member slidably mounted on the column; a fixed sheave member mounted on the column in an axially fixed configuration; a torque-sensitive assembly in operative communication with the movable sheave member, the torque-sensitive assembly being configured to move the movable sheave member relative to the fixed sheave member based on a torque applied to the torque-sensitive assembly, wherein the torque-sensitive assembly comprises: --- a spoke coupled to the column, the rotation of the spoke being fixed to the rotation of the column, the spoke comprising at least one arm; --- a cam roller rotatably coupled to each arm; and a cam coupled to the movable sheave member, the cam having at least one cutout portion forming a cam profile surface, each cam roller positioned within a cutout portion of the at least one cutout portion, each cam roller configured to engage an associated cam profile surface to transmit torque and rotation between the spider and the cam; and An actuator is operably coupled to the movable sheave member to selectively move the movable sheave member independently of the torque sensitive assembly.

10. The clutch assembly of claim 9, wherein: The clutch is a driving clutch, further wherein: The post is configured to be in operative communication with a motor; and The movable sheave member and the fixed sheave member are configured to be in operative communication with an endless endless member.

11. The clutch assembly of claim 9, wherein: The clutch is a driven clutch, further wherein: The column is configured to be in operative communication with a powertrain; and The movable sheave member and the fixed sheave member are configured to be in operative communication with an endless endless member.

12. The clutch assembly of claim 9, further comprising: an actuation spoke comprising an actuation roller, the actuation spoke being configured to move axially; and an actuating cam having a roller guide cutout section, the actuating roller being received within the roller guide cutout section of the actuating cam, the actuator being operably coupled to the actuating cam so as to selectively rotate the actuating cam, thereby causing the actuating spoke to move the movable sheave member independently of the torque-sensitive component.

13. The clutch assembly of claim 12, further comprising: an actuation elongate member operably coupled to the actuator; an attachment member operably coupled to an end of the actuation elongated member; and An actuation bracket is operably coupled to the actuation cam, and the attachment member is pivotally coupled to the actuation bracket.

14. The clutch assembly of claim 9, wherein: The actuator is configured to push the movable sheave member to move the movable sheave member.

15. A vehicle having a Uniform Clamp Actuated Infinitely Variable Speed ​​Transmission (UCAS IVT) system, the vehicle comprising: a motor that generates engine torque and rotation; powertrain; The UCAS IVT system includes: --Circulating annular components; --Driving clutch, the driving clutch comprising: --- a drive column, which is operably coupled to the motor, ---A movable drive sheave member slidably mounted on the drive column, --- a fixed drive sheave member mounted on the drive post in an axially fixed configuration, and a drive torque-sensitive component in operative communication with the movable drive sheave member, the drive torque-sensitive component being configured to move the movable drive sheave member relative to the fixed drive sheave member based at least in part on a torque applied to the drive torque-sensitive component; a driven clutch, the driving clutch and the driven clutch being configured to transmit torque and rotation between each other using the recirculating annular member, the driven clutch comprising: --- a driven column operatively coupled to the powertrain, ---A movable driven sheave member slidably mounted on the driven post, --- a fixed driven sheave member mounted on the driven post in an axially fixed configuration, and a driven torque-sensitive component in operative communication with the movable driven sheave member, the driven torque-sensitive component being configured to move the movable driven sheave member relative to the fixed driven sheave member based at least in part on a torque applied to the driven torque-sensitive component, wherein the driven torque-sensitive component comprises: a driven spoke coupled to the driven column, wherein the rotation of the driven spoke is fixed to the rotation of the driven column, the driven spoke comprising at least one driven spoke arm; a driven cam roller rotatably coupled to each driven spoke arm; and a follower cam coupled to the movable follower sheave member, the follower cam having at least one cutout portion, the at least one cutout portion forming a follower cam profile surface, each follower cam roller positioned within a cutout portion of the at least one cutout portion, each follower cam roller configured to engage an associated follower cam profile surface to transmit torque and rotation between the follower spider and the follower cam; and and at least one actuator operably coupled to one of the drive clutch and the driven clutch to selectively move one of the movable drive sheave member and the movable driven sheave member independently of corresponding drive torque sensitive components and driven torque sensitive components to achieve at least one of uniform clamping of the recirculating annular member and producing a ratio change on the UCAS IVT system.

16. The vehicle according to claim 15, further comprising: at least one sensor for generating sensor information; at least one memory for storing at least operating instructions; as well as A controller is configured to control the actuator based on stored operating instructions and the sensor information.

17. The vehicle according to claim 15, wherein: The at least one actuator is configured to urge one of the movable drive sheave member and the movable driven sheave member to selectively move the one of the movable drive sheave member and the movable driven sheave member.

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