HK1180382A - Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor - Google Patents

Description

Infinitely variable transmission, continuously variable transmission, methods, assemblies, subassemblies, and components therefor

Cross Reference to Related Applications

This application claims the benefit of U.S. provisional patent application No. 61/310,224, filed 3/2010, which is incorporated herein by reference in its entirety.

Background

Technical Field

The field of the invention relates generally to transmissions, and more particularly, the inventive embodiments relate to Continuously Variable Transmissions (CVTs) and Infinitely Variable Transmissions (IVTs).

Description of the Related Art

In some systems, power is characterized by torque and speed. More specifically, in these systems, power is generally defined as the product of torque and rotational speed. Typically, the transmission is connected to a power input that provides input torque at an input speed. The transmission is also connected to a load that requires an output torque and an output speed, which may be different from the input torque and the input speed. Typically, and in general terms, a prime mover provides the power input to the transmission, and a driven device or load receives the power output from the transmission. The primary function of the transmission is to modulate the power input by delivering a power output to a driven device at a desired ratio of input speed to output speed ("speed ratio").

Some mechanical drives include a variety of transmissions of the type known as stepped, discontinuous, or fixed ratio. These transmissions are configured to provide discrete or stepped speed ratios within a given range of speed ratios. For example, such transmissions may provide a speed ratio of 1:2, 1:1, or 2:1, but such transmissions may not provide an intermediate speed ratio, such as 1:1.5, 1:1.75, 1.5:1, or 1.75: 1. Other drive arrangements include a transmission, commonly referred to as a continuously variable transmission ("CVT"), which includes a continuously variable variator. Compared to a step-variable transmission, a CVT is configured to provide a ratio per fraction within a given range of ratios. For example, within the given speed ratio ranges described above, a CVT can generally provide any desired speed ratio between 1:2 and 2:1, which would include, for example, 1:1.9, 1:1.1, 1.3:1, 1.7:1, and so forth. Still other drives use an infinitely variable transmission ("IVT"). Similar to a CVT, an IVT is capable of producing each speed ratio within a given range of speed ratios. However, in contrast to CVTs, IVTs are configured to provide zero output speed at a steady input speed ("powered zero speed" condition). Thus, an IVT can provide an infinite set of speed ratios with the speed ratios defined as the ratio of input speed to output speed, and thus the IVT is not limited to a given range of speed ratios. It should be noted that some transmissions use a continuously variable transmission that is connected to other gears and/or clutches in a split power arrangement to produce IVT functionality. However, as used herein, the term IVT should be understood primarily to encompass an infinite continuously variable variator that produces IVT functionality without the need for additional gears and/or clutches.

Various types of stepless or infinite stepless variator are known in the field of mechanical power transmission. For example, a well-known class of continuously variable transducers is the belt-variable radius pulley transducer. Other known transducers include hydrostatic transducers, toroidal transducers and cone-ring transducers. In some cases, these variators are connected to other gears to provide IVT functionality. Some hydromechanical variators may provide infinite ratio variability without additional gears. Certain stepless and/or infinite variators are classified as friction or traction variators because they rely on dry friction or elastohydrodynamic traction, respectively, to transmit torque through the variator. One example of a traction variator is a ball variator, in which a plurality of ball elements are sandwiched between torque transmitting elements, and a thin layer of elastohydrodynamic fluid acts as a torque transmission channel between the balls and the torque transmitting elements. The inventive embodiments disclosed herein are most relevant to the latter type of converter.

There is a continuing need in the CVT/IVT industry for improvements in transmissions and variators in, among other things, increasing efficiency and packaging flexibility, simplifying operation, and reducing cost, size and complexity. The inventive embodiments of the CVT and/or IVT methods, systems, subassemblies, components, etc., disclosed below address some or all aspects of this need.

Summary of The Invention

The systems and methods described herein have several features, no single one of which is solely responsible for its desirable attributes. Without intending to limit the scope as expressed by the claims that follow, its more prominent features will now be discussed briefly. After considering this discussion, and particularly after reading the section entitled "detailed description of certain inventive embodiments" one will understand how the features of the present systems and methods provide advantages over conventional systems and methods.

One aspect of the invention relates to a variator mechanism for an Infinitely Variable Transmission (IVT) having a longitudinal axis and a set of traction planet assemblies arranged angularly about the longitudinal axis. In one embodiment, the variator has a first carrier member coupled to each traction planet assembly. The first carrier member is configured to guide the traction planet assemblies. The variator has a second carrier member coupled to each of the traction planet assemblies. The second carrier member is configured to guide the traction planet assemblies. The first bearing member can rotate relative to the second bearing member. A carrier driver nut is coupled to the first carrier member. The carrier driver nut is adapted to translate axially. Axial translation of the carrier driver nut corresponds to rotation of the first carrier member relative to the second carrier member.

One aspect of the present invention relates to an Infinitely Variable Transmission (IVT) having a longitudinal axis. In one embodiment, the IVT has a plurality of traction planet assemblies arranged angularly about the longitudinal axis. The IVT is provided with a first carrier member connected to each traction planet assembly. The first carrier member is provided with a plurality of radially offset slots. The first carrier member is configured to guide the traction planet assemblies. The IVT can include a second carrier member connected to each traction planet assembly. The second carrier member is provided with a plurality of radial slots. The first and second carrier members are configured to receive a rotational power input. In one embodiment, the first carrier member is capable of rotating relative to the second carrier member. The IVT also includes a carrier driver nut coupled to the first carrier member. The carrier driver nut is adapted to translate axially. Axial translation of the carrier driver nut corresponds to rotation of the first carrier member relative to the second carrier member. In an alternative embodiment, the IVT has a main axis located along the longitudinal axis. The spindle is operatively connected to the first and second carrier members. The spindle may have a set of helical splines configured to couple to a carrier driver nut. In yet another alternative embodiment, the carrier driver nut is adapted to translate axially along the spindle. Axial translation of the carrier driver nut corresponds to rotation of the carrier driver nut. In some embodiments, the IVT has a first traction ring connected to each traction planet assembly. The first traction ring is substantially non-rotatable about the longitudinal axis. The IVT can be provided with a second traction ring connected to each traction planet assembly. The second traction ring is adapted to provide a power output from the IVT. In an alternative embodiment, the first and second carrier members are adapted to receive rotational power from the main shaft. In one embodiment, the IVT has a shift fork operatively connected to the carrier driver nut. The shift fork may have a pivot axis that is offset from the longitudinal axis. Pivoting of the shift fork corresponds to axial translation of the carrier driver nut. Axial translation of the carrier driver nut corresponds to rotation of the carrier driver about the longitudinal axis. In an alternative embodiment, the IVT is provided with a pump operatively connected to the main shaft. In yet another embodiment, the IVT has a ground ring connected to the first traction ring. The ground ring is connected to a housing of the IVT.

Another aspect of the present invention relates to an Infinitely Variable Transmission (IVT) having a longitudinal axis. The IVT includes a main shaft arranged along the longitudinal axis. The main shaft is provided with a set of helical splines. The IVT has a set of traction planet assemblies arranged angularly about the longitudinal axis. In one embodiment, the IVT has a first carrier member connected to each traction planet assembly. The first carrier member is provided with a plurality of radially offset slots. The first carrier member is configured to guide the traction planet assemblies. The IVT includes a second carrier member connected to each traction planet assembly. The second carrier member is provided with a plurality of radial slots. The first and second carrier members are connected to a source of rotational power. In one embodiment, the IVT includes a shift mechanism having a shift fork. The shift fork may have a pivot pin that is offset from the longitudinal axis. The shift mechanism includes a carrier driver nut operatively connected to the shift fork. The carrier driver nut has an inner bore configured to engage the helical splines of the spindle. The carrier driver nut is configured to rotate about the longitudinal axis. In one embodiment, movement of the shift fork about the pivot pin corresponds to axial movement of the carrier driver nut. Axial movement of the carrier driver nut corresponds to rotation of the first carrier member relative to the second carrier member. In some embodiments, the IVT has a first traction ring in contact with each traction planet assembly. The first traction ring is substantially non-rotatable about the main shaft. The IVT can have a second traction ring in contact with each traction planet assembly. The second traction ring is adapted to provide a power output from the IVT. In some embodiments, an output shaft is operatively connected to the second traction ring. In an alternative embodiment, a disengagement mechanism is operatively connected to the output shaft. In yet another embodiment, a torque limiter is connected to the second carrier member. The torque limiter may also be connected to the main shaft. In some embodiments, the torque limiter comprises a plurality of springs connected to the second carrier member and the main shaft.

One aspect of the invention relates to a variator mechanism for an Infinitely Variable Transmission (IVT) having a main shaft arranged along a longitudinal axis of the IVT and a set of traction planet assemblies arranged angularly about the longitudinal axis. The traction planet assemblies are coupled to first and second carrier members. The first carrier member is provided with a plurality of radially offset guide slots. The first and second carrier members are adapted to receive a rotational power. In one embodiment, the shifting mechanism includes a shift fork. The shift fork has a pivot pin that is offset from the longitudinal axis. The shift mechanism has a carrier driver nut operatively connected to the shift fork. The carrier driver nut has an inner bore configured to engage helical splines formed on the spindle. The carrier driver nut is configured to rotate about the longitudinal axis. The carrier driver nut is adapted for axial translation along the longitudinal axis. Movement of the shift fork about the pivot pin corresponds to axial movement of the carrier driver nut. Axial movement of the carrier driver nut corresponds to rotation of the first carrier member relative to the second carrier member. In an alternative embodiment, the shifting mechanism includes a shift collar operatively connected to the shift fork. A bearing may be connected to the shift collar and adapted to be connected to the carrier driver nut. In yet another embodiment, the shifting mechanism has a rocker arm connected to the shift fork.

Another aspect of the present invention relates to an Infinitely Variable Transmission (IVT) having a longitudinal axis. The IVT has a set of traction planets arranged angularly about the longitudinal axis. The IVT includes a first carrier member connected to each traction planet assembly. The first carrier member is provided with a plurality of radially offset slots. The first carrier member is configured to guide the traction planet assemblies. The IVT has a second carrier member connected to each traction planet assembly. The second carrier member is provided with a set of radial slots. The first and second carrier members are connected to a source of rotational power. In one embodiment, the IVT has a carrier drive located radially outward from the first and second carrier members. The carrier driver has a plurality of longitudinal grooves. At least one groove is aligned parallel to the longitudinal axis and said groove is connected to the first load bearing member. In one embodiment, at least one groove is aligned with respect to the longitudinal axis and said groove is connected to the second load bearing member. In other embodiments, the carrier drive is adapted to translate axially. In some embodiments, the axial translation of the carrier drive corresponds to rotation of the first carrier member relative to the second carrier member. In still other embodiments, the IVT has a pump connected to the first carrier member.

Another aspect of the present invention relates to an Infinitely Variable Transmission (IVT) having a longitudinal axis. In one embodiment, the IVT has a plurality of traction planets arranged angularly about the longitudinal axis. The IVT is provided with a first carrier member connected to each traction planet assembly. The first carrier member is provided with a plurality of radially offset slots. The radially offset slots are configured to guide the traction planet assemblies. The first carrier member is provided with longitudinal guide slots, and said longitudinal guide slots are formed at an angle relative to the longitudinal axis. In one embodiment, the IVT has a second carrier member connected to each traction planet assembly. The second carrier member is provided with a plurality of radial slots. The radial slots are configured to guide the traction planet assemblies. The second carrier member is provided with longitudinal guide slots, and said longitudinal guide slots are arranged parallel to the longitudinal axis. In one embodiment, the first and second carrier members are configured for connection to a source of rotational power. The IVT also has a carrier driver coupled to the first and second carrier members. The carrier drive is adapted to rotate about the longitudinal axis. The carrier drive is adapted to translate axially. In one embodiment, the axial translation of the carrier drive corresponds to a rotation of the first carrier member relative to the second carrier member. In some embodiments, the carrier drive has a set of shift pins extending radially outward from a central cylindrical hub. The cylindrical hub is coaxial with the longitudinal axis. In other embodiments, the IVT has a spring connected to the carrier driver. In still other embodiments, the axial translation of the carrier driver corresponds to a change in the transmission ratio of the IVT.

Another aspect of the invention relates to a variator for an Infinitely Variable Transmission (IVT) having a set of traction planet assemblies. In one embodiment, the shift mechanism has a first carrier member having a plurality of radially offset guide slots. The radially offset guide slots are arranged to guide the traction planet assemblies. The first carrier member has a plurality of longitudinal slots, and said longitudinal slots are angled relative to the longitudinal axis. The shift mechanism includes a second carrier member having guide slots arranged about the longitudinal axis. The guide slots are arranged to guide the traction planet assemblies. The second carrier member has a plurality of longitudinal slots, and said longitudinal slots are parallel to the longitudinal axis. The shifting mechanism has a carrier drive coupled to the first and second carrier members. The carrier drive has shift pins that extend from a central hub. The shift pins engage the longitudinal slots formed on the first and second carrier members. Axial translation of the carrier driver corresponds to rotation of the first carrier member relative to the second carrier member. In some embodiments, the carrier drive, first carrier member, and second carrier member are configured to rotate about the longitudinal axis at a speed substantially equal to an input speed of a power source connected to the IVT. In other embodiments, the shifting mechanism has a shift roller coupled to each shift pin. The shift roller is in contact with the longitudinal slots of the first carrier member.

Another aspect of the invention relates to a method for controlling an Infinitely Variable Transmission (IVT) having a longitudinal axis. The method comprises the following steps: a set of traction planet assemblies arranged angularly about the longitudinal axis is provided. The method may include providing a first carrier member coupled to each of the traction planet assemblies. The first carrier member has a plurality of radially offset guide slots arranged to guide the traction planet assemblies. In one embodiment, the method comprises the steps of: a second carrier member is provided that is connected to each of the traction planet assemblies. The second carrier member has radial guide slots arranged to guide the traction planet assemblies. The method may include the step of coupling the first and second carrier members to a source of rotational power. The method includes providing a carrier driver nut coupled to the first carrier member. The method also includes the step of translating the carrier driver nut along the longitudinal axis. In an alternative embodiment, the step of translating the carrier driver nut includes the step of rotating the first carrier member relative to the second carrier member. In some embodiments, the method includes the step of operatively connecting the carrier driver nut to a shift fork. In some embodiments, the method includes the step of coupling a torque limiter to the second carrier member. In still other embodiments, the method includes coupling the torque limiter to the source of rotational power. In some embodiments, the method includes the step of sensing the torque exerted on the second carrier member. The method may also include the step of rotating the second carrier member based at least in part on the sensed torque. Rotating the second carrier member may include the step of adjusting a gear ratio.

Brief description of the drawings

FIG. 1 is a cross-sectional view of a ball planetary Infinitely Variable Transmission (IVT) with a skewness-based control system.

Fig. 2 is a partially exploded cross-sectional view of the IVT of fig. 1.

Fig. 3 is a perspective view of the internal components of the IVT of fig. 1.

Fig. 4 is a plan view of the internal components of the IVT of fig. 1.

Fig. 5 is an exploded view of a shift component that may be used in the IVT of fig. 1.

Fig. 6 is a plan view of one embodiment of first and second carrier members that may be used in the IVT of fig. 1.

FIG. 7 is a cross-sectional view of an Infinitely Variable Transmission (IVT) having a skewness-based control system.

Fig. 8 is a cross-sectional perspective view of the IVT of fig. 7.

Fig. 9 is a cross-sectional view of one embodiment of a carrier driver ring that can be used in the IVT of fig. 7.

Fig. 10 is a perspective view of the carrier driver ring of fig. 9.

Fig. 11 is a cross-sectional plan view of the carrier driver ring of fig. 9.

Fig. 12 is a cross-sectional plan view of one embodiment of a carrier driver ring that can be used in the IVT of fig. 7.

Fig. 13 is a cross-sectional plan view of another embodiment of a carrier driver ring that can be used in the IVT of fig. 7.

Fig. 14 is a cross-sectional view of an IVT having a skew-based control system and a carrier driver ring.

Fig. 15 is a schematic view of one embodiment of an IVT having a skew-based control system and a linearly actuated carrier drive.

Fig. 16 is a cross-sectional view of one embodiment of an IVT having a skew-based control system and a linearly actuated carrier drive.

Fig. 17 is a partial cross-sectional perspective view of certain internal shift components of the IVT of fig. 16.

Fig. 18 is a plan view of the internal shift member of fig. 17.

FIG. 19 is a plan view A-A of the internal shift member of FIG. 18.

Fig. 20 is a partial, cross-sectional perspective view of an embodiment of an IVT having a skew-based control system.

Fig. 21 is a cross-sectional view of the IVT of fig. 20.

Fig. 22 is an exploded cross-sectional view of the IVT of fig. 20.

Fig. 23 is an exploded view of certain internal components of the IVT of fig. 20.

Fig. 24 is a cross-sectional view of a torque limiter that may be used in the IVT of fig. 20.

Fig. 25 is an exploded view of the torque limiter of fig. 24.

Fig. 26 is a partial cross-sectional view of a disengagement mechanism that can be used with the IVT of fig. 20.

Fig. 27 is a cross-sectional view of the disengagement mechanism of fig. 26.

Fig. 28 is another cross-sectional view of the disengagement mechanism of fig. 26.

Fig. 29 is a cross-sectional view of an embodiment of a disengagement mechanism that can be used in the IVT of fig. 1 or 20.

Fig. 30 is another cross-sectional view of the disengagement mechanism of fig. 29.

Fig. 31 is a perspective view of a disengagement mechanism that can be used with the IVT of fig. 20.

Fig. 32 is a cross-sectional view of the disengagement mechanism of fig. 31.

Fig. 33 is another perspective view of the disengagement mechanism of fig. 31.

Fig. 34 is yet another cross-sectional view of the disengagement mechanism of fig. 31.

Fig. 35 is a schematic diagram depicting one hydraulic system that may be used in the IVT of fig. 20.

Fig. 36 is a cross-sectional view of an embodiment of an IVT having a skewness-based control system.

Fig. 37 is a plan view B-B of certain components of the IVT of fig. 36.

Fig. 38 is a plan view of a carrier that may be used in the IVT of fig. 36.

Detailed description of certain inventive embodiments

The preferred embodiments will now be described with reference to the drawings, wherein like numerals refer to like elements throughout. The terminology used in the description presented below is not intended to be interpreted in any limited or restrictive manner, since it is being used in conjunction with a detailed description of certain specific embodiments of the invention. Moreover, embodiments of the invention may include inventive features, no single one of which is solely responsible for its desirable attributes or which is essential to practicing the inventions herein described. Certain Continuously Variable Transmission (CVT) and Infinitely Variable Transmission (IVT) embodiments described herein relate generally to the types disclosed in: U.S. Pat. nos. 6,241,636; 6,419,608; 6,689,012; 7,011,600; 7,166,052, respectively; U.S. patent application nos. 11/243,484 and 11/543,311; and patent Cooperation treaty patent applications PCT/IB2006/054911, PCT/US2008/068929, PCT/US2007/023315, PCT/US2008/074496, and PCT/US 2008/079879. The entire disclosure of each of these patents and patent applications is hereby incorporated by reference.

As used herein, the following terms "operatively connected," "operatively coupled," "operatively linked," "operatively connectable," "operatively coupled," "operatively linked," and similar terms refer to a relationship (mechanical, linkage, coupling, etc.) between elements such that operation of one element results in corresponding, subsequent, or simultaneous operation or actuation of a second element. It is noted that when the terminology is used to describe some inventive embodiments, it is typical that specific structures or mechanisms of linking or connecting elements are described. However, unless specifically stated otherwise, when one of the terms is used, it is intended that the actual link or connection may take a number of different forms, which in some cases will be readily apparent to those of ordinary skill in the relevant art.

For purposes of this description, the term "radial" is used herein to refer to a direction or position that is perpendicular relative to the longitudinal axis of the transmission or variator. The term "axial" is used herein to refer to a direction or position along an axis parallel to the main or longitudinal axis of the transmission or variator. For purposes of clarity and conciseness, similar components are sometimes similarly labeled.

It should be noted that reference herein to "traction" does not exclude applications in which the primary or sole mode of power transmission is by "friction". There is no attempt made to establish a category of differences between traction and friction drives, which in general can be understood as different power transmission schemes. Traction drives often involve transmitting power between two elements through shear forces trapped in a thin fluid layer between the two elements. Fluids used in these applications often exhibit a traction coefficient greater than conventional mineral oils. The traction coefficient (μ) represents the maximum available traction force that will be available at the interface of the contacting components and is a measure of the maximum available drive torque. Typically, friction drives generally involve transmitting power between two elements through friction between the two elements. For the purposes of this disclosure, it should be understood that the IVTs described herein may operate in both traction and friction applications. For example, in embodiments where the IVT is used in a bicycle application, the IVT may operate in a friction drive at times and a traction drive at other times, depending on the torque and speed conditions present during operation.

The embodiments of the invention disclosed herein relate to controlling a variator and/or IVT using generally spherical planets each having a tiltable axis of rotation (sometimes referred to herein as "planet axis of rotation") that can be adjusted to achieve a desired ratio of input speed to output speed during operation. In some embodiments, the adjustment of the axis of rotation involves angular misalignment of the planet axis in a first plane to effect angular adjustment of the planet axis of rotation in a second plane to thereby adjust the speed ratio of the variator. The angular deviation in this first plane is referred to herein as "skew" or "skew angle". This type of converter control is generally described in U.S. patent applications 12/198,402 and 12/251,325, the entire disclosures of each of which are incorporated herein by reference. In one embodiment, a control system coordinates the use of skew angles to generate forces between certain contacting components in the variator that will tilt the axis of rotation of the planet in this second plane. The inclination of the axis of rotation of the planet adjusts the speed ratio of the variator. Various embodiments of a skew control system (sometimes referred to herein as a "skew-based control system") and a skew angle actuation device for achieving a desired speed ratio of the variator will be discussed.

Embodiments of an Infinitely Variable Transmission (IVT) and its components and subassemblies will now be described with reference to fig. 1-38. Embodiments of the shifting mechanism for controlling the relative angular positions of two disc-shaped shifting members will also be explained. These shifting mechanisms can improve control over many types of infinitely variable transmissions, and are shown in certain embodiments herein for illustrative purposes. Fig. 1 illustrates an IVT100 that may be used in many applications including, but not limited to, human powered vehicles (e.g., bicycles), light electric vehicles, human powered, electric powered, or internal combustion engine powered hybrid vehicles, industrial equipment, wind turbine generators, and the like. Any technical application that requires modulation of mechanical power transmission between a power input and a power consumption (powersink) (e.g., a load) may implement the embodiments of the IVT100 in its powertrain.

Turning now to fig. 1 and 2, in one embodiment, the IVT100 includes a housing 102 coupled to a housing cap 104. The housing 102 and the housing cap 104 support a power input interface (e.g., pulley 106) and a control interface (e.g., actuator linkage 108). The pulley 106 may be connected to a belt driven by a source of rotational power, such as an internal combustion engine (not shown). In one embodiment, the IVT100 is provided with a main shaft 110 that substantially defines a longitudinal axis of the IVT 100. The main shaft 110 is connected to the pulley 106. The main shaft 110 is supported by a bearing 112 in the housing cap 104. The IVT100 includes a plurality of traction planet assemblies 114 arranged angularly about the main shaft 110. Each traction planet 114 is coupled to first and second carrier members 116, 118, respectively. The main shaft 110 is connected to a first carrier member 116. The first and second carrier members 116, 118 are coaxial with the main shaft 110. In one embodiment, each traction planet 114 is coupled to first and second traction rings 120, 122, respectively. Each traction planet assembly 114 contacts an idler assembly 121 at a radially inward location. The first traction ring 120 is coupled to a first axial force generator assembly 124. The first traction ring 120 and the first axial force generator assembly 124 are substantially non-rotatable relative to the housing 102. In one embodiment, the first axial force generator assembly 124 is connected to a ground ring 125. The ground ring 125 is attached to a shoulder 123 extending from the housing cap 104. The second traction ring 122 is coupled to a second axial force generator assembly 126. The second traction ring 122 and the second axial force generator assembly 126 are coupled to an output power interface 128. The output power interface 128 may be connected to a load (not shown). In one embodiment, the output power interface 128 includes a disengagement mechanism 130 configured to mechanically disengage the second traction ring 122 from the load.

Referring now to fig. 1-4, in one embodiment, the IVT100 can be used in a shift control mechanism 140. The shift control mechanism 140 may be used with other types of transmissions and is shown here for the IVT100 by way of example. The shift control mechanism 140 may include an actuator linkage 108 coupled to a rocker arm 142. The rocker arm 142 is connected to a shift fork 144 that is configured to rotate about a pivot pin 146. In one embodiment, the pivot pin 146 is offset from the longitudinal axis. The shift fork 144 is connected to a shift collar 148. The shift collar 148 supports a bearing 150. The bearing 150 is connected to a carrier driver nut 152. The carrier driver nut 152 is coupled to the main shaft 110 and the first carrier member 116.

Referring now to fig. 5 and still to fig. 1-4, in one embodiment the swing arm 142 is rotatably connected to a pivot 143. The pivot 143 may be a detent pin attached to the shift fork 144. The shift fork 144 can have a set of slots 154. The slots 154 guide a set of engagement dowels 156 attached to the shift fork 148. In one embodiment, the shift collar 148 is equipped with four engagement dowels 156. In some embodiments, two engagement dowels 156 are positioned to ride in the slots 154 and two engagement dowels 156 are positioned to ride in a set of slots 155 (fig. 2) formed in the shoulder 123 of the housing cap 104. In one embodiment, the carrier driver nut 152 has an internal bore 158 with helical splines formed therein. The internal bore 158 is connected to a plurality of mating helical splines 160 formed on the main shaft 110. The carrier driver nut 152 is provided with a plurality of guide surfaces 162 extending radially outwardly from the internal bore 158. These guide surfaces 162 are connected to mating guide surfaces 164 formed on the first carrier member 116.

Turning now to fig. 6, the second carrier member 118 can be provided with guide slots 170 arranged angularly about a central bore 171 in one embodiment. The guide slots 170 are aligned with a radial construction line 76 when viewed in the plane of the page of fig. 6. The guide slots 170 are adapted to receive an end of a planet shaft 115 (fig. 1). In some embodiments, a radially inward portion 172 of the guide slots 170 is formed with curved profiles sized to accommodate the traction planet shaft 115. In one embodiment, the first carrier member 116 is provided with a plurality of radially offset slots 174 arranged angularly about the central bore 175. Each radially offset guide slot 174 is sized to accommodate the connection of the first carrier member 116 to the planet shaft 115. The radially offset guide slots 174 are angularly offset from the radial build line 76 when viewed in the plane of the page of fig. 6. This angular offset may be approximated as an angle 88. The angle 88 is formed between the radial construction line 76 and a construction line 90. The construction line 90 substantially bisects the radially offset guide slot 174 when viewed in the plane of the page of fig. 6. In some embodiments, angle 88 is between 3 degrees and 45 degrees. A small angle 88 produces a highly responsive change in gear ratio but is potentially more difficult to control or stabilize, while a large angle may be less responsible for the change in gear ratio but is in contrast easier to control. In some embodiments where a high speed, fast shift rate is desired, the angle 88 may be, for example, 10 degrees. In other embodiments where a slower speed, precisely controlled gear ratio is desired, the angle 88 may be about 30 degrees. However, these values for angle 88 are provided as illustrative examples, and angle 88 may be varied in any manner desired by the designer. In some embodiments, angle 88 may be any angle in the range of 10 to 25 degrees including any angle therebetween or a fraction thereof. For example, the angle may be 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, or any portion thereof. In other embodiments, the angle 88 may be 20 degrees. In an embodiment, the radially offset guide slots 174 may be arranged such that the construction line 90 is radially offset from a construction line 91 by a distance 92. The construction line 91 is parallel to the construction line 90 and intersects the center of the body 116 of the first load bearing member.

During operation of the IVT100, a change in gear ratio is achieved by rotating the actuator linkage 108. In some embodiments, the actuator linkage 108 is attached to a user control (not shown), which may be a mechanical linkage actuated by a user's hand. In other embodiments, the actuator linkage 108 may be connected to an electrical or hydraulic actuator that can transmit rotational motion to the actuator linkage 108 that is indicative of a desired gear ratio of the IVT 100. Because the actuator linkage 108 is axially fixed relative to the longitudinal axis, rotation of the actuator linkage 108 tends to rotate the rocker arm 142, thereby rotating and axially translating the pivot 143. Movement of the pivot shaft 143 tends to rotate the shift fork 144 about the pivot pin 146. The pivot pin 146 is offset from the main axle 110 such that rotation of the shift fork 144 about the pivot pin 146 corresponds to axial translation of the slots 154. Axial movement of the slots 154 tends to move the shift collar 148 axially relative to the main shaft 110. Since the carrier driver nut 152 is operatively connected to the shift collar 148, axial translation of the shift collar 148 corresponds to axial translation of the carrier driver nut 152. The carrier driver nut 152 is connected to the helical splines 160 of the main shaft 110. This axial translation of carrier driver nut 152 facilitates relative rotation of carrier driver nut 152 with respect to spindle 110. Since the carrier driver nut 152 engages the guide surfaces 164 of the first carrier member 116, rotation of the carrier driver nut 152 relative to the spindle 110 corresponds to rotation of the first carrier member 116 relative to the spindle 110. Rotation of the first carrier member 116 relative to the second carrier member 118 tends to change the gear ratio of the IVT 100.

It should be noted that the designer may configure the positions of the rocker arms 142, pivot shafts 143, and pivot pins 146 relative to the slots 154 to achieve a desired relationship between the rotation imparted to the actuator linkage 108 and the axial translation of the carrier driver nut 152. In some embodiments, the designer may select the positions of the rocker arms 142, pivot shafts 143, and pivot pins 146 to provide a desired force or torque applied to the actuator linkage 108 to effect a change in gear ratio. Likewise, the designer may select the pitch and lead of the helical spline 160 to achieve a desired relationship between the axial translation of the carrier driver nut 152 and the rotation of the first carrier member 116.

Referring again to fig. 5 and 6, in one embodiment, the IVT100 can be provided with a pump assembly 180. The pump assembly 180 includes a pump driver 182 that is coupled to a boss 184 formed on the first carrier member 116. The pump assembly 180 includes a pump plunger 186 attached to the pump driver 182. The pump plunger 186 surrounds a valve body 188 and a valve plunger 190. In one embodiment, the projection 184 has a center 191 (fig. 6) that is offset from the center 192 of the first load bearing member 116. In some embodiments, the projection 184 can be formed on the main shaft 110 or on a retaining nut 193, and likewise, the pump assembly 180 is suitably axially positioned so that the pump driver 182 can engage the projection 184. During operation of the IVT100, the main shaft 110 rotates about the longitudinal axis and thereby drives the first carrier member 116. The projection 184 drives the pump driver 182 in a reciprocating motion as the first carrier member 116 rotates about the longitudinal axis. In one embodiment, the ground ring 125 is provided with a guide groove 194 adapted to receive the pump driver 182. The ground ring 125 may also be provided with a plurality of spacing reliefs 196 that are appropriately sized to provide clearance for the engagement locating pins 156 and the shift forks 144.

Turning now to fig. 7-10, an IVT 200 can include a plurality of traction planet assemblies 202 arranged angularly about a longitudinal axis 204. For clarity, the housing and some of the internal components of the IVT 200 are not shown. Each traction planet assembly 202 is provided with a ball axle 206. The ball axles 206 are operatively connected to first and second carrier members 208, 210, respectively. The first and second carrier members 208, 210 may be substantially similar to the first and second carrier members 116, 118, respectively. In one embodiment, the first and second carrier members 208, 210 are connected to a source of rotational power (not shown). The IVT 200 is provided with a carrier driver ring 212 located radially outward of each traction planet assembly 202. The carrier driver ring 212 is connected to a shift clevis 214 by a set of bearings 215. The bearing 215 may be rotationally constrained to the carrier driver ring 212 by, for example, dowel pins 217. In one embodiment, the shift U-shaped member 214 is provided with a threaded hole 213. The threaded bore 213 is generally parallel to the longitudinal axis 204. The threaded bore 213 may be connected to a threaded shift rail (not shown) to facilitate axial translation of the shift clevis 214.

Referring specifically to fig. 9 and 10, the carrier driver ring 212 has a set of longitudinal grooves 220 formed on the inner circumference on the carrier driver ring 212. The longitudinal grooves 220 are substantially parallel to the longitudinal axis 204. The carrier driver ring 212 has a set of offset longitudinal grooves 222 formed on the inner circumference. These offset longitudinal grooves 222 are angled with respect to the longitudinal axis 204. The offset longitudinal grooves 222 form an angle 224 with respect to the longitudinal axis 204 when viewed in the plane of fig. 9. In some embodiments, the angle 224 may be any angle in the range of 0 to 30 degrees including any angle therebetween or a fraction thereof. For example, this angle 224 may be 0, 1, 2, 3,4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, 26, 27, 28, 29, 30, or any portion thereof. In one embodiment, the first carrier member 208 is provided with a plurality of locating pins 228. The detent pins 228 are connected to and guided by the grooves 220. The second carrier member 210 is provided with a plurality of alignment pins 230. The alignment pins 230 are connected to and guided by the offset longitudinal slots 222.

During operation of the IVT 200, a change in gear ratio can be achieved by axially translating the shift clevis 214. Axial translation of the shift clevis 214 tends to axially translate the carrier driver ring 212. Axial translation of the carrier driver ring 212 tends to guide the detent pins 228, 230 in the grooves 220, 222, respectively. Since the first and second carrier members 208, 210 are substantially fixed in the axial direction, the first and second carrier members 208, 210 rotate relative to each other as the alignment pins 228, 230 axially advance in the recesses 220, 222, respectively.

Referring now specifically to fig. 11-13, the longitudinal grooves formed on the carrier driver ring 212 may take a variety of forms to provide the desired relative rotation of the first carrier member 208 with respect to the second carrier member 210. For example, fig. 11 shows the longitudinal grooves 220 and the offset longitudinal grooves 222. On the side carrying the driver ring 212, the grooves 220, 222 are separated by a distance 232. On the opposite side of the carrier driver ring 212, the grooves 220, 222 are separated by a distance 234. In the embodiment illustrated in fig. 12, the carrier driver ring 212 is provided with the longitudinal grooves 220 and a set of curved grooves 236. In the embodiment illustrated in fig. 13, the carrier driver ring 212 is provided with a set of positively biased longitudinal grooves 238 and a set of negatively biased longitudinal grooves 240. It should be noted that the embodiments described herein are for illustrative purposes and that the shape and size of the grooves formed on the carrier ring 212 may be configured by the designer to achieve the desired shifting performance. For example, a distance 232 between the longitudinal groove 220 and the offset longitudinal groove 222 may be less than a distance 234 on an opposite side of the carrier driver ring 212. The difference between the distances 232, 234 may be configured to produce a desired rotation of the first carrier member 208 relative to the second carrier member 210 upon axial displacement of the carrier driver ring 212 along the longitudinal axis 204.

Turning now to fig. 14, in one embodiment, an IVT 300 may be substantially similar to the IVT 200. The IVT 300 can include a housing 302 configured to substantially enclose the internal components of the IVT 300. IVT 300 can be provided with a carrier driver ring 304. The carrier driver ring 304 may be coupled to the first and second carrier members 208, 210 in a similar manner as the carrier driver ring 212. The carrier driver ring 304 may be configured to be axially translated by an actuator, such as a motor (not shown). In one embodiment, the carrier driver ring 304 is radially supported on an output ring 306. The output ring 306 is operatively connected to each of the traction planet assemblies 202.

Turning now to fig. 15, an IVT 400 can have a plurality of traction planet assemblies 402 arranged angularly about a main axis 404 in one embodiment. Each traction planet assembly 402 is coupled to first and second traction rings 406, 408, respectively. Each traction planet assembly 402 is coupled to an idler assembly 410. The idler assemblies 410 are positioned radially inward from each of the traction planet assemblies 402. In one embodiment, each traction planet assembly 402 is coupled to first and second carrier members 412, 414. The first and second carrier members 412, 414 may be substantially similar to the first and second carrier members 116, 118, respectively. In one embodiment, the first carrier member 412 is rigidly connected to the main shaft 404. The first and second carrier members 412, 414 and the spindle 404 may be adapted to be operatively connected to a source of rotational power (not shown). The second carrier member 414 is adapted to rotate relative to the first carrier member 412. In one embodiment, the second carrier 414 is connected to a torque plate 416. The torque plate 416 is coaxial with the second carrier plate 414 and may be rigidly attached to the second carrier plate 414 by splines, welding or gas suitable fastening means. In one embodiment, the torque plate 416 is rotationally rigid or stiff, but has some degree of flexibility in the axial direction, as is common in torque plates. This degree of flexibility in the axial direction provides a spring-like compliance for the torque plate 416. The torque plate 416 is connected at a radially inward location to a carrier driver nut 418. The carrier driver nut 418 has an internal bore formed with a plurality of helical splines 420 configured to engage mating helical splines formed on the main shaft 404. The carrier driver nut 418 is operatively connected to an actuator coupling 422. In one embodiment, the actuator linkage 422 is coupled to a linear actuator, such as a servo motor or manual lever (not shown), that generates a force as depicted by vector 424 in fig. 15. In one embodiment, the actuator linkage 422 is substantially non-rotatable about the spindle 404.

During operation of the IVT 400, a change in gear ratio is achieved by axially translating the actuator linkage 422. Axial translation of actuator linkage 422 tends to axially translate carrier driver nut 418. Because the carrier driver nut 418 engages the spindle 404 on the helical spline 420, axial translation of the carrier driver nut 418 relative to the spindle 404 tends to assist in relative rotation between the carrier driver nut 418 and the spindle 404. The torque plate 416 rotates as the carrier driver nut 418 rotates, which tends to rotate the second carrier member 414 relative to the first carrier member 412.

Referring now to fig. 16-19, an IVT 500 can be provided with traction planet assemblies 502 in one embodiment in contact with and radially outward of an idler assembly 504. Each traction planet assembly 502 is in contact with first and second traction rings 506, 508, respectively. In one embodiment, the first traction ring 506 is substantially non-rotatable. The IVT 500 can be provided with an output shaft 510. The output shafts 510 are connected to a common axial force generator coupling 512 that is configured to engage the second traction ring 508. Each traction planet assembly 502 is guided and supported by first and second carrier members 514, 516, respectively. The first and second carrier members 514, 516 are provided with guide slots 513, 515, respectively. In one embodiment, the guide slots 513, 515 are substantially similar to the guide slots 170, 174, respectively. The first and second carrier members 514, 516 are adapted to receive power input from a source of rotational power (not shown). In one embodiment, an input shaft 518 may be connected to a drive gear 520 that engages a carrier gear 522. The carrier gear 522 assists in transferring power to the first and second carrier members 514, 516. The output shaft 510 may be supported on the housing 524 by, for example, a bearing. In one embodiment, the housing 524 is formed of two parts that are fastened together to substantially enclose the internal components of the IVT 500.

In one embodiment, the IVT 500 is provided with a central shaft 526 that substantially defines a longitudinal axis of the IVT 500. The central shaft 526 may be configured to support the first and second carrier members 514 and 516. In some embodiments, the second carrier member 516 is rigidly attached to the central shaft 526. The first carrier member 514 may be guided onto the central shaft 526 such that the first carrier member 514 may rotate relative to the second carrier member 516. One end of the central shaft 526 may be configured to support an actuator connector 528. In one embodiment, a bearing 529 supports the actuator connector 528 on the central shaft 514. The bearings 529 are configured to allow the actuator connector 528 to translate axially relative to the central shaft 526. The actuator connector 528 is splined to the housing 524 and is substantially non-rotatable relative to the central shaft 526. In one embodiment, the actuator linkage 528 is coupled to a linear actuator (not shown) to facilitate axial translation of the actuator linkage 528. The actuator linkage 528 is coupled to a carrier drive hub 532 by a bearing 530. The carrier driver hub 532 is coupled to the first and second carrier members 514, 516.

Referring now specifically to fig. 17-19, the carrier driver hub 532 may be provided with rods 534 extending from a substantially cylindrical body. Each rod 534 is provided with a roller 536. The rods 534 engage longitudinal slots 538 formed on the second carrier member 516. The rollers 536 engage longitudinal slots 540 formed on the first carrier member 514. The longitudinal grooves 538 are substantially parallel to the longitudinal axis of the IVT 500. The longitudinal slots 540 are angled relative to the longitudinal axis of the IVT 500 when viewed in the plane of the page of fig. 19.

During operation of the IVT 500, a change in gear ratio is achieved by axially translating the actuator linkage 528. Axial translation of the actuator linkage 528 tends to axially translate the carrier driver hub 532. As the carrier driver hub 532 translates axially, the rods 534 and rollers 536 translate axially along the longitudinal slots 538, 540, respectively. Because the longitudinal slot 540 is angled relative to the longitudinal slot 540, axial translation of the rod 534 and roller 536 causes relative rotation between the first and second carrier members 514, 516 and thereby tends to change the ratio of the IVT 500. In some embodiments, the IVT 500 can be provided with a spring 542 configured to urge the carrier driver hub 532 toward an axial end of the IVT 500.

Referring now to fig. 20 and 21, in one embodiment, the IVT600 includes a housing 602 coupled to a housing cap 604. The housing 602 and housing cap 604 support a power input interface, such as a pulley 606, and a shift actuator 608. The pulley 606 may be connected to a belt driven by a source of rotational power, such as an internal combustion engine (not shown). In one embodiment, the IVT600 is provided with a main shaft 610 that substantially defines a longitudinal axis of the IVT 600. The main shaft 610 is connected to the pulley 606. The IVT600 includes a plurality of traction planet gears 614 that are coupled to first and second carrier members 616, 618, respectively. The first and second carrier members 616, 618 are provided with guide slots that are substantially similar to the guide slots 170 and the radially offset guide slots 174. In one embodiment, the first and second carrier members 616, 618 have a thin, substantially uniform cross-section when viewed in the plane of the paper of fig. 21, which allows for various manufacturing techniques, such as sheet metal stamping, to be employed in the manufacture of the first and second carrier members 616, 618.

Still referring to fig. 20 and 21, in one embodiment, the main shaft 610 is coupled to a first carrier member 616. Each traction planet assembly 614 is in contact with first and second traction rings 620, 622, respectively. Each traction planet assembly 614 contacts an idler assembly 621 at a radially inward location. The second traction ring 622 is coupled to an axial force generator 624. The axial force generator 624 is connected to an output driver 626. In one embodiment, the first traction ring 620 is coupled to a ground ring 625 and is substantially non-rotatable with respect to the housing 602. The IVT600 has an output shaft 627 connected to the output driver 626. The output shaft 627 transmits rotational power from the IVT 600. In one embodiment, the output shaft 627 is supported in the housing 602 by an angular contact bearing 628 and a radial ball bearing 629 (see, e.g., fig. 23). In some embodiments, a shaft seal 631 may be coupled to the output shaft 627 and the housing 602.

In some embodiments, the IVT600 can be provided with a torque limiter 630 connected to the second carrier member 618 and the main shaft 610. The IVT600 can also be provided with a pump assembly 635 connected to the main shaft 610 (see, e.g., fig. 22). In one embodiment, the pump assembly 635 can use a rotodynamic pump to pressurize and distribute the transport fluid over the internal components of the IVT 600. The pump assembly 635 may be suitably equipped with a plurality of hoses and/or lines to direct the transport fluid. During operation of the IVT600, the pump assembly 635 is driven by the main shaft 610.

Referring now to fig. 22 and 23, in one embodiment, the IVT600 is provided with a shift control mechanism 640. The shift control mechanism 640 may be used with other types of transmissions and is shown here for example in the IVT 600. The shift control mechanism 640 can include an actuator link 642 coupled to the shift actuator 608. The shift actuator 608 can be connected to a shift fork 644. In one embodiment, shift actuator 608 is configured to pivot shift fork 644 about an axis 646. In one embodiment, the axis 646 is offset from the longitudinal axis of the IVT 600. The shift fork 644 can be supported in the housing cap 604. The shift fork 644 may be connected to a shift collar 648. The shift collar 648 supports a bearing 650. The shift fork 644 and the shift collar 648 can be connected, such as by a plurality of pins 651. The shift fork 644 and the shift collar 648 are substantially non-rotatable about the longitudinal axis of the IVT 600. In one embodiment, the shift control mechanism 640 includes a carrier driver nut 652. The carrier driver nut 652 is connected to the main shaft 610 by a set of helical splines 654. The carrier driver nut 652 is connected to the first carrier member 616 by a carrier extension 656. In one embodiment, the carrier extension 656 has an axial guide slot configured to engage the carrier driver nut 652.

During operation of the IVT600, a change in gear ratio can be achieved by moving the actuator link 642, thereby rotating the shift actuator 608. Rotation of shift actuator 608 corresponds to pivoting of shift fork 644 about axis 646. The pivoting of the shift fork 644 pushes the shift collar 648 axially relative to the main shaft 610. The shift collar 648 thereby axially translates the bearing 650 and carrier driver nut 652. These helical splines 654 tend to rotate the carrier driver nut 652 as the carrier driver nut 652 moves axially. The rotation of the carrier driver nut 652 is typically a small angle. The carrier extension 656, and thus the first carrier member 616, is guided by the carrier driver nut 652 through rotation. As previously explained with respect to fig. 6, rotation of the first carrier member 616 relative to the second carrier member 618 causes a change in the gear ratio of the IVT 600.

In one embodiment, the helical splines 654 have a lead in the range of 200 and 1000 mm. For some applications, the lead is in the range of 400-800 mm. The lead is related to how much friction in the system can counteract what is known as a counter torque change. The lead may be sized to reduce the input force on the carrier driver nut 652, the rotation of the first carrier member 616 required to shift through the ratio, and the available packaging space. The size of the lead is subject to design requirements and may also be affected by the test results.

Turning now to fig. 24 and 25, the IVT600 can be provided with a torque limiter 630 connected to the second carrier member 618 in one embodiment. The torque limiter 630 may be used with other types of transmissions and is shown here for example for the IVT 600. The second carrier member 618 is provided with a pivot shoulder 660 configured to guide to the spindle 610. The second carrier member 618 has a plurality of openings 662 radially arranged about the pivot shoulder 660. These openings 662 are appropriately sized to couple to a plurality of springs 664. In one embodiment, the springs 664 are coil springs with end caps 666. The torque limiter 630 includes a spring carrier 668. The springs 664 are connected to the spring carrier 668. In some embodiments, a plurality of retaining detents 670 are provided on the spring carrier 668 to mate with the end cap 666 to assist in retaining the spring 664 on the spring carrier 668. The spring carrier 668 is connected to the main shaft 610 through a splined inner bore 672.

In one embodiment, the torque limiter 630 includes a carrier cap 676 that is coupled to the second carrier member 618. In some embodiments, the spring carrier 668 is axially positioned between the second carrier member 618 and the carrier cap 676. The carrier cap 676 may be provided with tabs 678 to facilitate attachment to the second carrier member 618 by, for example, rivets 679. The carrier cap 676 can be provided with openings 680 radially arranged about a pivot shoulder 682. In one embodiment, the pivot shoulder 682 cooperates with a mating shoulder 684 formed on the spring carrier 668.

During operation of the IVT600, torque may be limited to a predetermined value by using a torque limiter 630. The main shaft 610 is adapted to receive rotational power from the pulley 606. This rotational power is transmitted to first carrier member 616 and spring carrier 668. The spring carrier 668 transmits the rotational power to the second carrier member 618 through the springs 664. The springs 664 are appropriately sized to deflect when an output torque is above a predetermined value or when the torque on the second carrier member 618 is above a predetermined value. The deflection of the spring 664 corresponds to the rotation of the second carrier member 618 relative to the first carrier member 616, thereby changing the gear ratio. The change in gear ratio reduces torque on the second carrier member 618.

Turning now to fig. 26-29, in one embodiment, the IVT600 can be provided with a disengagement mechanism 700. The disengagement mechanism 700 may be used with other types of transmissions and is shown here for example for the IVT 600. In one embodiment, the disengagement mechanism 700 includes an outer ring 702 coupled to an attachment ring 704. The connection ring 704 is attached to a traction ring 620. In some embodiments, the ground ring 625 is replaced by an outer ring 702 and a connection ring 704. The outer ring 702 is coupled to the housing 602 and the housing cap 604. In some embodiments, an actuator (not shown) is coupled to the outer ring 702. For example, the actuator may be a lever (not shown) that extends through the housing 602 to thereby enable the outer ring 702 to be rotated. The outer ring 702 is provided with a plurality of ramps 706 around its inner circumference. These ramps 706 are connected to a set of splines 708 formed on the outer circumference of the inner ring 704. During operation of the IVT600, input and output ports can be implemented by rotating the outer ring 706. Rotation of the outer ring 706 corresponds to axial displacement of the traction ring 620 from the traction planet assemblies 614.

Turning now to fig. 29-30, in one embodiment, the IVT600 can be provided with a disengagement mechanism 800. The disengagement mechanism 800 may be used with other types of transmissions and is shown here for example for the IVT 600. In some embodiments, the disengagement mechanism 800 has a drive shaft 802 that can be selectively coupled to an output shaft 804 using a coupling 806. Once assembled, the drive shaft 802 and output shaft 804 may be used in place of the output shaft 627. The connector 806 is configured to engage a set of splines 808 formed on an inner diameter of the output shaft 804. In some embodiments, a spring (not shown) may be inserted between the connector and the output shaft 804. The spring tends to bias the connector 806 to the position depicted in fig. 29, which is an engaged position. The connector 806 is attached to a cable handle 810. The cable handle 810 may be supported on the inner bore of the connector 806 by a bearing 812. The cable handle 810 may be attached to a push-pull cable (not shown). The cable may be connected to an external link that may be actuated to tension the zipper and move the link 806 axially. A cable guide 814 provides a path through which the zipper can pass into the internal bore of the output shaft 814 without interference. The cable guide 814 is supported by a bearing 816. During operation of the IVT600, the output shaft 804 can be selectively connected to an engaged position by tensioning the cable (not shown) and axially moving the link 806, as illustrated in fig. 30.

Referring now to fig. 31-34, in one embodiment, the IVT600 can be provided with a disengagement mechanism 900. The disengagement mechanism 900 may be used with other types of transmissions and is shown here for example for the IVT 600. In one embodiment, the disengagement mechanism 900 may replace the output shaft 627. The disengagement mechanism 900 can include an elongated shaft 902 suitably configured to be supported in the housing 602 by bearings 628, 629 and seal 630. The elongate shaft 902 can have a first end 901 and a second end 903. The first end 901 may be adapted to connect to an output load, such as by a keyway or other fastening means. The second end 903 of the shaft 902 is equipped with retractable teeth 904. The retractable teeth 904 are positioned radially around the periphery of the tip 903. The retractable teeth 904 may be inserted between and retained by axially extending segments 906 formed on the tip 903. The retractable teeth 904 are operatively connected to a sliding member 908. The slide member 908 is coupled to an actuator linkage 910. The sliding member 908 guides the retractable teeth 904 to an engaged position or a disengaged position. In one embodiment, the retractable teeth 904 may be connected to a spring member (not shown) configured to bias the retractable teeth 904 to the position depicted in fig. 31 and 32. In the position, the retractable teeth 904 may, for example, engage the output drive 626. An actuator (not shown) may be configured to connect to the actuator link 910 through the inner bore of the shaft 902 to facilitate movement of the sliding member 908 and correspondingly move the teeth 904 to the second position depicted in fig. 33 and 34. In the position, the teeth 904 are radially displaced such that the output driver 626 is disconnected from the shaft 902.

Turning now to fig. 35, in one embodiment, a hydraulic system 950 may be used in the IVT100, IVT600, or other embodiments of the transmission. The hydraulic system 950 includes a reservoir 952 having a fill depth 954. In some embodiments, for example, the reservoir 952 is formed, for example, in a lower portion of the housing 602. For illustrative purposes, the rotational member of the IVT600 may be depicted as rotational member 955 in fig. 35. The hydraulic system 950 includes a pump 956, which may be substantially similar to the pump assembly 635, for example. The pump 956 delivers fluid from the reservoir 952 to a storage container 958. In one embodiment, the storage container 958 is provided with a first orifice 960 and a second orifice 962. The first orifice 960 is positioned above the second orifice 962. The storage container 958 is positioned over the rotational members 955 and the reservoir 952. In one embodiment, for example, the storage container 958 may be formed on the housing 602, for example. In other embodiments, the storage container 958 is attached to the exterior of the housing 602 and is configured to be in fluid communication with the rotational members 955 and the reservoir 952.

During assembly of the IVT600, a fluid is added to the reservoir 952, for example. In some embodiments, the volume of the reservoir 952 may be small, so that a change in the volume of fluid added to the reservoir 952 has a significant effect on the fill depth 954. In some cases, the fill depth 954 may be high enough to allow fluid in the reservoir 952 to contact the rotational members 955. Contact between the fluid in the reservoir 952 and the rotating members 955 can create drag and air friction, which is considered problematic. In some cases, however, it may be desirable to increase the volume of fluid added to the reservoir 952. For example, increasing the volume of fluid may improve thermal characteristics, durability, and maintenance. Accordingly, the hydraulic system 952 may be implemented to facilitate an increase in the volume of fluid added to the reservoir 952 and maintain a fill depth 954 below the rotational members 955.

During operation of the IVT600, fluid is drawn from the reservoir 952 by the pump 956, for example, which reduces the fill depth 954. The fluid is pressurized and delivered to the storage vessel 958 by a pump 956. The storage container 958 receives the pressurized fluid and fills the volume of the storage container 958. The first and second orifices 960, 962 are suitably sized such that once the storage container 958 is under pressure, fluid may flow from the first orifice 960 while substantially no fluid flows from the second orifice 962. In some embodiments, the second orifice 962 may be a one-way valve configured to be open when the storage container 958 is depressurized and closed when the storage container 958 is pressurized. Fluid flow from the first aperture 960 is directed to the rotational members 955 to provide lubrication and cooling. During operation of the IVT600, for example, the storage container 958 accumulates a volume of fluid. Once the operation of the IVT600 is stopped, the accumulated fluid drains from the storage container 958 and returns to the reservoir 952.

Referring now to fig. 36-38, in one embodiment, an IVT1000 can be substantially similar to IVT 100. For clarity, only certain internal components of the IVT1000 are shown. In one embodiment, the IVT1000 has a plurality of balls 1001 arranged angularly about a longitudinal axis 1002. Each ball 1001 is configured to rotate about an axis 1003 forming a tiltable axis. One end of the axis 1003 is provided with a spherical roller 1004. The opposite end of the axis 1003 is connected to a guide block 1005 by, for example, a pin 1010. In one embodiment, the guide block 1005 has an extension 1006. The IVT1000 can include a first carrier member 1007 that is substantially similar to the carrier member 118. The first bearing member 1007 is configured to couple to the ball rollers 1004 to provide the appropriate degree of freedom for the axis 1003. The IVT1000 can include a second carrier member 1008 configured to be operatively connected to the guide blocks 1005. The IVT100 is provided with a shift plate 1012 that is arranged coaxially with the first and second carrier members 1007, 1008. The shift plate 1012 is connected to the extensions 1006. In one embodiment, shift plate 1012 may be actuated, for example, by the shift control mechanism 140. The shift plate 1012 is configured to rotate relative to the first and second carrier members 1007, 1008.

Referring now specifically to fig. 38, in one embodiment the shift plate 1012 is provided with a plurality of slots 1014. The extensions 1006 are connected to the slots 1014. For illustration purposes, only one slot 1014 is shown. The slot 1014 can be illustrated as having three portions: a first portion 1015, an intermediate portion 1016, and a third portion 1017. The intermediate portion 1016 may be defined as an arc segment between a corresponding set of radial construction lines 1018, 1019. The first and third portions 1015, 1017 are angularly offset from the radial construction lines 1018, 1019, respectively, in a manner substantially similar to the manner in which the radially offset slots 174 are offset from the radial construction line 76. During operation of the IVT1000, a change in gear ratio can be achieved by rotationally biasing the shift plate 1012 with respect to the first and second carrier members 1007, 1008. The extensions 1006 are guided by the slots 1014. When the extension 1006 is positioned on the first portion 1015 of the slot 1014, the transmission ratio may be a positive or positive ratio. When the extension 1006 is positioned over the third portion 1017 of the slot 1014, the transmission ratio may be a reverse or negative ratio. When the extension 1006 is positioned on the middle portion 1016, the transmission ratio is neutral or a condition referred to as "zero power". The slot 1014 may be appropriately sized to accommodate a desired relationship between a change in gear ratio and, for example, a change in actuator position.

It should be noted that the above description has provided dimensions for particular components or subassemblies. These mentioned dimensions, or ranges of dimensions, are provided herein to best comply with certain legal requirements (e.g., best mode) as possible. However, the scope of the inventions described herein should be determined only by the language of the claims, and thus, neither of these dimensions should be considered limiting of the inventive embodiments, except to the extent that any claim makes a particular dimension, or range thereof, a feature of that claim.

The foregoing description details certain specific embodiments of the invention. It will be appreciated, however, that no matter how detailed the foregoing appears in text, the invention can be practiced in many ways. As also stated above, it should be noted that the use of particular terminology when describing certain features or aspects of the invention should not be taken to imply that the terminology is being redefined herein to be restricted to including any specific characteristics of the features or aspects of the invention with which that terminology is associated.

Claims (10)

1. A variator mechanism for an Infinitely Variable Transmission (IVT) having a longitudinal axis and traction planet assemblies arranged angularly about the longitudinal axis, the variator mechanism comprising:

a first carrier member connected to each of the traction planet assemblies, the first carrier member configured to guide the traction planet assemblies;

a second carrier member connected to each of the traction planet assemblies, the second carrier member configured to guide the traction planet assemblies, wherein the first and second carrier members are rotatable about the longitudinal axis; and

a carrier driver nut coupled to the first carrier member, the carrier driver nut adapted to translate axially, wherein axial translation of the carrier driver nut corresponds to rotation of the first carrier member relative to the second carrier member.

2. The variator of claim 1, wherein the first carrier member is provided with radially offset slots.

3. The variator of claim 2, further comprising a main shaft positioned along the longitudinal axis.

4. The gearshift mechanism of claim 3, wherein the main shaft is operatively connected to the first and second carrier members.

5. The variator of claim 4, wherein the main shaft is provided with helical splines.

6. The variator of claim 5, wherein the carrier driver nut is adapted to translate axially along the spindle.

7. The variator of claim 6, wherein the carrier driver nut is coupled to the helical splines.

8. The shifting mechanism of claim 1, further comprising a shift fork operatively connected to the carrier driver nut.

9. The gearshift mechanism of claim 8, wherein the shift fork has a pivot axis that is offset from the longitudinal axis.

10. The gearshift mechanism of claim 9, wherein pivoting of the shift fork corresponds to axial translation of the carrier driver nut.