Patent Grant
9850993
Field of the Invention
The disclosed invention relates generally to mechanical power modulation and transmission. More specifically, the invention concerns continuously and infinitely variable units and transmissions, subassemblies, components, and methods for use therewith.
Description of the Related Art
In the relevant technology various types of continuously and infinitely variable transmissions (C/IVT) are known. For example, one well known class of continuous variators is the belt-and-variable-radius-pulley variator. Other known variators include hydrostatic, toroidal, and cone-and-ring variators. In some cases, these variators couple to other gearing to provide infinitely variable transmission functionality. The present disclosure is addressed in part to a type of C/IVT typically known as a ball-type rolling traction CVT. To provide a continuously or infinitely variable transmission, various ball-type rolling traction transmissions have been developed in which power is transmitted through traction rollers supported in a housing between torque input and output discs. In some such transmissions, traction rollers are mounted on support structures configured to cause the engagement of the traction rollers with the input and output discs in circles of varying diameters depending on the desired transmission ratio.
Although ball-type rolling traction CVTs have gained some acceptance in certain industrial applications, the technology has generally been unable to overcome technical and economic hurdles to gain a wider adoption across multiple fields of use. The success of many known solutions has been limited. There is a continuing need in the CVT/IVT industry for transmission and variator improvements in increasing efficiency and packaging flexibility, simplifying operation, and reducing cost, size, and complexity, among other things. The inventive embodiments disclosed here address many of these challenges. In particular, though certainly not limited in scope of applicability, certain inventive embodiments disclosed here provide mechanisms and methods for employing continuously variable units and/or continuously variable transmissions in vehicle applications.
The systems and methods herein described have several features, no single one of which is solely responsible for its desirable attributes. Without limiting 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 the Preferred Embodiments” one will understand how the features of the system and methods provide several advantages over traditional systems and methods.
One aspect of the invention relates to a continuously variable transmission (CVT) having a number of planets arranged angularly about the longitudinal axis of the CVT, each planet having a through bore that forms a tiltable axis of rotation of the planet. The CVT further includes a main axle arranged along the longitudinal axis of the CVT and a lubricant manifold coupled to the main axle. The lubricant manifold is adapted to supply lubricant to the main axle. Optionally, the CVT has a stator assembly operably coupled to the planets. The stator assembly is concentric with the longitudinal axis of the transmission. Alternatively, the CVT has a shift rod arranged in a central bore of the main axle. In some cases, the shift rod is adapted to supply the lubricant to the interior of the CVT.
Another aspect of the invention addresses a method for lubricating internal components of a transmission. The method includes, in one embodiment, providing a lubricant manifold configured to cooperate with a lubricant source, providing a main axle adapted to receive the lubricant manifold, providing a shift rod having a central bore and adapted to cooperate with the main axle. The method further includes supplying a lubricant via the lubricant manifold to the main axle and delivering the lubricant through the main axle to the rod. In some embodiments, the method includes delivering the lubricant through the central bore of the shift rod to a shift rod lubricant passage. Optionally, the method includes the step of supplying a pressurized lubricant via the lubricant source. Alternatively, the method includes the step of delivering the lubricant through a lubricant delivery passage of the main axle to the interior of the transmission.
One more aspect of the invention concerns an infinitely variable transmission that includes an input shaft arranged along the longitudinal axis of the transmission and operably coupled to a power source. The transmission further includes a stator assembly coupled to the input shaft and a number of planets operably coupled to the stator assembly. In some embodiments, the transmission has a means for supplying lubricant to the input shaft. Optionally, the input shaft and the stator assembly are rigidly coupled. Alternatively, the means for supplying a lubricant includes a lubricant manifold adapted to supply lubricant to the input shaft. Optionally, the transmission has a shift rod operably coupled to the input shaft.
Yet another aspect of the invention involves a mechanism for facilitating an adjustment in a speed ratio of a transmission. In one embodiment, the mechanism includes a shift rod having a number of lubricant ports and a closed end. The mechanism can also include a shift cam body operably coupled to the shift rod, the shift cam body having a number of lubricant channels. Optionally, the mechanism has a shift actuation subassembly coupled to the shift rod. Optionally, the shift actuation subassembly includes a shift pin collar coupled to the shift rod. The shift pin collar is configured to rotate with an input shaft of the transmission. Alternatively, the shift actuation subassembly includes a shift screw operably coupled to the shift pin collar. The shift screw is substantially non-rotatable with an input shaft of the transmission.
One aspect of the invention is directed to an infinitely variable transmission that includes an input shaft arranged along the longitudinal axis of the transmission and a stator assembly coupled to, and coaxial with, the input shaft. The transmission further includes a number of planets operably coupled to the stator assembly. In one embodiment, the planets are arranged angularly about the longitudinal axis of the transmission. The transmission further includes a traction ring operably coupled to the planets and a housing operably coupled to the traction ring. In one embodiment, the housing is substantially fixed from rotating with the input shaft. Optionally, the traction ring is substantially fixed from rotating with the input shaft. Alternatively, the input shaft and the stator assembly are rigidly coupled. Optionally, the traction ring has a substantially annular ring having a front face and a rear face and a number of bi-directional ramps located on the front face. The cross-section of each ramp is curved. Alternatively, the traction ring has a contact surface located on the rear face.
Another aspect of the invention relates to a mechanism for facilitating an adjustment of a speed ratio in an infinitely variable transmission. The mechanism includes, in one embodiment, a shift rod arranged along a longitudinal axis of the transmission, a shift nut operably coupled to the shift rod, and a shift screw operably coupled to the shift nut. In some embodiments, the shift rod is adapted to supply a lubricant to the interior of the transmission. Optionally, a rotation of the shift screw axially translates the shift rod. Alternatively, the shift rod is adapted to supply a lubricant to the interior of the infinitely variable transmission. Optionally, the mechanism has a shift cam body operably coupled to the shift rod. The shift cam body has a number of lubricant channels.
Yet one more aspect of the invention addresses a method of operating an infinitely variable transmission (IVT). The method includes receiving power on an input shaft and providing a shift rod arranged along the longitudinal axis of the IVT. In one embodiment, the shift rod is adapted to supply a lubricant to internal components of the IVT and is also adapted to facilitate an adjustment speed ratio of the IVT. The method further includes transferring power from the input shaft to a number of planets arranged angularly around the longitudinal axis of the IVT. In one embodiment, the method includes providing an output shaft coupled to the planets. The output shaft delivers power from the planets to an external load coupled to the IVT. Optionally, the method includes the step of coupling a stator assembly to the input shaft. The stator assembly and the input shaft are substantially rotatable. Alternatively, the method includes the step of providing a source of pressurized lubricant coupled to the IVT. Optionally, the method includes the step of supplying the pressurized lubricant to the shift rod.
In another aspect, the invention concerns a shift actuation mechanism for an infinitely variable transmission (IVT). The shift actuation mechanism includes a shift pin collar having a central bore adapted to receive an input shaft, a shift screw coupled to the shift pin collar, and a control plate coupled to the shift pin collar. The shift actuation mechanism further includes a shift nut coupled to the shift screw. The shift nut is adapted to be substantially fixed from rotating relative to the shift screw. In one embodiment, the shift actuation mechanism includes a shift rod arranged along the longitudinal axis of the IVT and operably coupled to the shift screw. Optionally, the shift actuator has a coupling device adapted to cooperate with the shift rod. Alternatively, the shift rod is configured to rotate about the longitudinal axis of the IVT. Optionally, the shift screw is substantially fixed from rotation relative to the shift rod.
Another aspect of the invention relates to a shift pin collar for an infinitely variable transmission (NT). The shift pin collar is a substantially cylindrical body with a central bore. A neck is located on the periphery of the cylindrical body and is adapted to receive a bearing. The substantially cylindrical body has a number of holes which are adapted to receive a coupling device of the IVT.
Yet one more aspect of the invention addresses a shift screw for an infinitely variable transmission (IVT). The shift screw is a substantially cylindrical body having a central bore, a threaded portion arranged on the central bore, and a first shoulder arranged on the central bore. The first shoulder is adapted to receive a first bearing of the IVT. In one embodiment, the shift screw has a second shoulder located on the periphery of the cylindrical body. The second shoulder is adapted to receive a second bearing of the NT. The shift screw also has a reaction flange located on the periphery of the cylindrical body.
In another aspect, the invention concerns a lubricant manifold for use with a transmission. The lubricant manifold is a substantially disc-shaped body with a central bore. In one embodiment, the lubricant manifold has a shoulder located on the central bore that is adapted to receive a bearing of the transmission. The lubricant manifold has a lubricant passage configured to intersect the central bore. The lubricant passage extends radially from the central bore to an outer circumference of the disc-shaped body. The lubricant manifold also has a number of grooves arranged on the central that are adapted to receive a number of seals of the transmission. The lubricant manifold has an engagement shoulder extending from a face of the disc-shaped body and is coaxial with the central bore. The lubricant manifold also has an engagement face located on a face of the disc-shaped body that is oppositely located to the engagement shoulder. The lubricant manifold has a seal groove located on the engagement face. Optionally, the lubricant passage has a threaded portion. Alternatively, the lubricant manifold has a first and second seal groove. Each seal groove is formed on the central bore. The first seal groove is located on one side of the lubricant passage. The second seal groove is located on a second side of the lubricant passage. Alternatively, the threaded portion of the lubricant passage is arranged on the periphery of the disc-shaped body.
One more aspect of the invention concerns a lubricant manifold for use with a transmission. The lubricant manifold is a circular body with a central bore. The lubricant manifold has a flange extending from the circular body. The flange is concentric with the central bore. One side of the flange is an engagement face. The lubricant manifold also has an engagement hub extending from the engagement face. The engagement hub has a central pilot recess. The outer face of the engagement hub has a reaction surface. The engagement hub also has a lubricant passage boss extending from the flange. Optionally, the central piloting recess has a substantially square cross-section. Alternatively, the flange has a number of fastening holes arranged around the periphery of the flange. Optionally, the reaction surface has a substantially circular cross-section.
Yet another aspect of the invention involves a housing cover plate for use with an infinitely variable transmission (IVT). The housing cover plate is a generally circular body with a central bore. The housing cover plate has a flange coupled to the circular body. The flange is concentric with the central bore. The housing cover plate has a shoulder located on the inner diameter of the circular body and a number of lubricant channels arranged angularly around the circumference of the circular body. Optionally, the housing cover plate has grooves arranged on the central bore and adapted to receive a retention device of the IVT. Alternatively, the central bore is adapted to receive a bearing of the IVT. Optionally, the flange has a number of fastening holes.
One aspect of the invention concerns a housing cover plate for use with a continuously or infinitely variable transmission (C/IVT). The housing cover plate is a substantially circular disc with a central passage. The housing cover plate has a bearing recess formed on the central passage and a thrust washer recess coupled to the central passage in proximity to the bearing recess. The housing cover plate also has a number of engagement features. The engagement features are arranged on a face of the circular body in proximity to the outer circumference. The housing cover plate also has a flange coupled to the periphery of the circular body. Optionally, the engagement features have a substantially square cross-section. Alternatively, the flange has a number of fastening holes. Optionally, the housing cover plate has a groove formed on the central passage. The groove is configured to couple to a seal of the C/IVT.
Another aspect of the invention relates to a lubricant sump for use with an infinitely variable transmission (IVT). The lubricant sump is a body with a central bore and a number of holes located on an exterior perimeter edge portion of the body. The holes are adapted for mounting the body to a support structure of the IVT. The lubricant sump also has a number of lubricant passages located on the periphery of the body. The lubricant passages are configured to intersect the central bore. The lubricant sump has a seal pocket located substantially at the central bore of the body and a cavity concentric with the central bore. The cavity is adapted to receive a lubricant of the IVT. Optionally, the body has a substantially square cross-section.
Yet one more aspect of the invention addresses a mechanism for adjusting a speed ratio range for an infinitely variable transmission (IVT). The mechanism includes a shift rod arranged along the longitudinal axis of the IVT. The mechanism, in one embodiment, includes a shift-stop-cylinder assembly. The shift-stop-cylinder assembly is arranged coaxially with the shift rod and is coupled to a first end of the shift rod. The mechanism also includes a shift-stop-dowel assembly. The shift-stop-dowel assembly is arranged coaxially with the shift rod and is coupled to a second end of the shift rod. Optionally, the shift-stop-cylinder has a shift stop cylinder coupled to a spring and an adjustment nut. Alternatively, the shift-stop-spring assembly has a substantially cylindrical dowel coupled to the spring and an adjustment nut coupled to the spring. Optionally, the adjustment nut is configured to couple with a main axle of the IVT.
In another aspect, the invention concerns an axial force generating (AFG) mechanism for use in a continuously variable transmission (CVT). The AFG includes a load cam ring. The load cam ring is a substantially annular ring having a front face and a rear face. A number of bi-directional ramps are located on the front face of the load cam ring. The cross-section of the ramps of the load cam ring is curved. The AFG further includes a number of load cam rollers coupled to the load cam ring and a traction ring coupled to the load cam rollers. The traction ring is a substantially annular ring having a front face and a rear face. A number of bi-directional ramps are located on the front face of the traction ring. The ramps of the traction ring are adapted to receive the load cam rollers. The cross-section of the ramps of the traction ring is curved. Optionally, the load cam rollers are substantially spherical. Alternatively, the AFG has a preload spring coupled to the load cam ring. Optionally, the preload spring is a wave spring adapted to couple to the load cam ring.
Another aspect of the invention relates to a load cam ring for use in a continuously variable transmission (CVT). The load cam ring is a substantially annular ring having a front face and a rear face. A number of bi-directional ramps are located on the front face of the load cam ring. The cross-section of the ramps of the load cam ring is curved. Optionally, the engagement features have a substantially square cross-section.
In another aspect, the invention concerns a traction ring for use in a continuously variable transmission. The traction ring is a substantially annular ring having a front face and a rear face. A number of bi-directional ramps are located on the front face of the traction ring. The cross-section of the ramps of the traction ring is curved. Optionally, the engagement features have a substantially square cross-section. Alternatively, the contact surface has an angle of inclination in the range of 5 degrees to 75 degrees. Optionally, the contact surface has an angle of inclination of about 45 degrees.
One more aspect of the invention addresses an output shaft for use with a continuously variable transmission. The output shaft has a substantially cylindrical neck having a central bore. A reaction flange extends from one end of the neck and is concentric to the central bore. A number of splines are located on the central bore. A number of engagement features are located on the peripheral circumference of the reaction flange. Optionally, the output shaft has a number of piloting guides located on the peripheral circumference of the reaction flange. The piloting guides are substantially aligned with the engagement features about the central bore. Alternatively, the output shaft has a bearing support surface arranged on the central bore. Optionally, the output shaft has a lubricant passage formed on the cylindrical neck. The lubricant passage extends radially from the periphery of the cylindrical neck and is configured to intersect the central bore.
Yet another aspect of the invention involves a main axle for use in a continuously variable transmission (CVT). The main axle is an elongated body having a first end portion, a second end portion, and a central portion. A central bore is formed through the main axis of the elongated body, and extends from the first end portion and beyond the middle portion. The central bore has a fluted portion. The main axle has an axial reaction flange located at the first end portion. A threaded portion is located at the second end portion. The central portion of the main axle includes a first segment extending from the reaction flange, a second segment extending from the first segment, and a third segment extending from the second segment. The second segment has a slot. The third segment has a lubricant delivery passage and a lubricant inlet passage. The first, second, and third segments define respective shoulders that couple to components of the CVT. Optionally, the main axle has a first lubricant delivery passage located at the first end portion of the elongated body. Alternatively, the diameter of the first segment is larger than the diameter of the second segment. Optionally, the diameter of the second segment is larger than the diameter of the third segment.
One aspect of the invention concerns an auxiliary axle for use with a continuously or infinitely variable transmission. The auxiliary axle has a main body with a central bore. A locking member slot is provided along the axial length of the central bore. A reaction flange extends radially from a central portion of the main body. A lubricant passage is located on the reaction flange and intersects the central bore. The auxiliary axle has a first shoulder that extends from a first face of the reaction flange. The first shoulder is configured to couple to a stator of the transmission. Optionally, the auxiliary axle has a second shoulder extending from a second face of the reaction flange. The second shoulder has a substantially square-cross section. Alternatively, the first shoulder has a substantially circular cross-section.
Another aspect of the invention relates to a shift rod for use with a continuously or infinitely variable transmission. The shift rod is an elongated body having a central bore. The central bore is adapted to supply a lubricant to internal components of the transmission. The shift rod has a slot located substantially at the central portion of the elongated body. The slot is adapted to supply lubricant to the central bore. The shift rod has a number of lubricant passages on a first end of the elongated body. An actuator engagement passage is located on a second end of the elongated body. Optionally, one end of the elongated body is substantially closed. Alternatively, the shift rod has a piloting stub arranged on one end of the elongated body. Optionally, the shift rod has a seal groove arranged on the periphery of the elongated body between the slot and the actuator engagement passage.
Yet one more aspect of the invention addresses an input shaft for use in an infinitely variable transmission (IVT). The input shaft is an elongated body having a first end portion, a second end portion, and a central portion. A central bore is formed through the main axis of the elongated body, and extends from the first end portion and beyond the middle portion. The central bore has a fluted portion. The input shaft has an axial reaction flange located at the first end portion. A threaded portion is located at the second end portion. The central portion of the input shaft includes a first segment extending from the reaction flange, a second segment extending from the first segment, a third segment extending from the second segment, a fourth segment extending from the third segment, and a fifth segment extending from the fourth segment. The second segment has a first slot. The third segment has a first locking member seat, a lubricant delivery passage, and a lubricant inlet passage. The fourth segment has a second slot. The fifth segment has a second locking member seat. The first, second, third, fourth, and fifth segments define respective shoulders that couple to components of the CVT. Optionally, the second segment has a smaller diameter than the first segment. Alternatively, the third segment has a smaller diameter than the second segment. Optionally, the fifth segment has a smaller diameter than the fourth segment.
In another aspect, the invention concerns a drivetrain casing for use with a continuously or infinitely variable transmission (C/IVT). The drivetrain casing, in one embodiment, has a main body with an exterior surface and an interior surface, and also has an upper portion and lower portion. A mounting portion is arranged on the upper portion of the exterior surface. The mounting portion is configured to couple to a housing cover of the C/IVT, and has a central passage. A lubricant sump cavity is located on the lower portion of the main body. Optionally, the drivetrain casing has a number of fastening bosses arranged on the periphery of the upper portion. Alternatively, the drivetrain casing has a mounting surface configured to receive a seal of the C/IVT. Optionally, the drivetrain casing has an interior space partially separated from the lubricant sump cavity.
Another aspect of the invention relates to a continuously variable transmission (CVT). The CVT includes a number of planets arranged angularly about the longitudinal axis of the CVT. Each planet has a through bore that forms a tiltable axis of rotation of the planet. The CVT includes a load cam ring that is coaxial with the number of planets. The load cam ring is a substantially annular ring having a front face and a rear face. A number of bi-directional ramps are located on the front face of the load cam ring. The cross-section of the ramps of the load cam ring is curved. The CVT further includes a number of load cam rollers coupled to the load cam ring, and a traction ring coupled to the load cam rollers. The traction ring is a substantially annular ring having a front face and a rear face. A number of bi-directional ramps are located on the front face of the traction ring. The ramps of the traction ring are adapted to receive the load cam rollers. The cross-section of the ramps of the traction ring is curved. Optionally, the transmission has a main axle arranged along the longitudinal axis of the CVT. Alternatively, the transmission has a stator assembly operably coupled to the planets. The stator assembly is concentric with the longitudinal axis of the CVT. Optionally, the transmission has a lubricant manifold configured to supply a lubricant to the main axle.
Yet another aspect of the invention involves a transmission having a number of planets arranged about the longitudinal axis of the transmission. Each planet has a through bore that forms a tiltable axis of rotation of the planet. The transmission has a housing cover. The housing cover is a generally circular body with a central bore. The housing cover plate has a flange coupled to the circular body. The flange is concentric with the central bore. The housing cover plate has a shoulder located on the inner diameter of the circular body and a number of lubricant channels arranged angularly around the circumference of the circular body. Optionally, the transmission has a housing subassembly coupled to the housing cover. The housing subassembly includes a substantially cylindrical body configured to enclose components of the transmission. Alternatively, the housing subassembly is configured to rotate about the longitudinal axis of the transmission. Optionally, the housing subassembly is substantially fixed from rotating about the longitudinal axis of the transmission.
In another aspect of the invention involves a continuously or infinitely variable transmission. The transmission includes a number of planets arranged about the longitudinal axis of the transmission. Each planet has a through bore that forms a tiltable axis of rotation of the planet. The transmission also includes a main axle arranged coaxial with the planets. The main axle is an elongated body having a first end portion, a second end portion, and a central portion. A central bore is formed through the main axis of the elongated body, and extends from the first end portion and beyond the middle portion. The central bore has a fluted portion. The main axle has an axial reaction flange located at the first end portion. A threaded portion is located at the second end portion. The central portion of the main axle includes a first segment extending from the reaction flange, a second segment extending from the first segment, and a third segment extending from the second segment. The second segment has a slot. The third segment has a lubricant delivery passage and a lubricant inlet passage. The first, second, and third segments define respective shoulders that couple to components of the transmission. The transmission also includes an auxiliary axle coupled to the main axle. The auxiliary axle has a main body with a central bore. A locking member slot is provided along the axial length of the central bore. A reaction flange extends radially from a central portion of the main body. A lubricant passage is located on the reaction flange and intersects the central bore. The auxiliary axle has a first shoulder that extends from a first face of the reaction flange. The first shoulder is configured to couple to a stator of the transmission. The transmission also includes a stator assembly coupled to, and coaxial with, the main axle. Optionally, the transmission has a lubricant manifold coupled to the main axle. The lubricant manifold supplies a lubricant to the main axle. Alternatively, the transmission has a shift rod coupled to the main axle. Optionally, the shift rod is adapted to supply lubricant to the interior of the transmission.
These and other improvements will become apparent to those skilled in the relevant technology as they read the following detailed description and view the enclosed figures.
The inventive embodiments disclosed here relate to technology described in U.S. patent application Ser. Nos. 11/243,484, 11/585,677, and 60/948,152, which are hereby incorporated herein by reference in entireties. As used here, the terms “operationally connected,” “operationally coupled”, “operationally linked”, “operably connected”, “operably coupled”, “operably linked,” and like terms, refer to a relationship (mechanical, linkage, coupling, etc.) between elements whereby operation of one element results in a corresponding, following, or simultaneous operation or actuation of a second element. It is noted that in using said terms to describe inventive embodiments, specific structures or mechanisms that link or couple the elements are typically described. However, unless otherwise specifically stated, when one of said terms is used, the term indicates that the actual linkage or coupling may take a variety of forms, which in certain instances will be obvious to a person of ordinary skill in the relevant technology.
Components which are used on both the right and left side of a transmission or equipment are designated with the letters a and b. For example, where there are two axial force generator subassemblies 2800, the first axial force generator subassembly 2800A, while the second axial force generator subassembly 2800B. Generally, all of the components on a side are designated with the letter a, and all substantially similar components on another side are designated with the letter b; when a component is referred to generically without a side designation, the a or b suffix is removed.
Referring to
Still referring to
The main axle 1000 supports an output shaft 2300 in a manner such that a longitudinal axis L3 of the output shaft 2300 extends coincidentally with the main axle longitudinal axis L1. The output shaft 2300 and the main axle 1000 are engaged in a manner allowing the output shaft 2300 to rotate with respect to the main axle 1000 about the output shaft longitudinal axis L3. The output shaft 2300 and the auxiliary axle 1600 jointly support a housing subassembly 2600 in a manner that coincidentally aligns a centerline axis C2 of the housing subassembly 2600 with the main axle longitudinal axis L1 and that allows relative rotation of the housing subassembly 2600 with respect to the output shaft 2300 and the auxiliary axle 1600. The main axle 1000 and the auxiliary axle 1600 jointly support a lubricant manifold 2700 in a manner inhibiting unrestricted relative rotation of the lubricant manifold 2700 with respect to the main axle 1000. A shift rod 3000 extends though the main axle 1000 and couples to the shift-cam-and-sun subassembly 1300 for facilitating selective translation of the shift-cam-and-sun subassembly 1300 along the main axle longitudinal axis L1.
Each one of the planet-and-shift-lever subassemblies 2100 is supported in a manner that allows synchronous rotation of all the planet-and-shift-lever subassemblies 2100 about a respective reference axis T1 extending through a planet 2102 of each one of the planet-and-shift-lever subassemblies 2100. Through such synchronous rotation, all of the planet-and-shift-lever subassemblies 2100 are substantially in the same relative rotational position at a given point in time. An axis T1 (see
Referring now to
During operation of the CVT 100, the main axle 1000 and the lubricant manifold 2700 are held stationary through rigid connection of the lubricant manifold 2700 to a mating structure (for example, a drivetrain casing 3700 shown in
Through traction at a respective second traction interface TI2 between the second axial force generator subassembly 2800B and each planet 2102, torque is exerted by the planets 2102 on the second axial force generator subassembly 2800B, thereby causing the second axial force generator subassembly 2800B and output shaft 2300 to jointly rotate about the main axle 1000. The second traction interface TI2 is defined, as used here, as a region of contact between the second axial force generator subassembly 2800B and the respective planet 2102.
Turning now to a brief discussion of power flow through the CVT 100 and still referring to
Synchronous rotation of all the planet-and-shift-lever subassemblies 2100 about the respective reference axis T1 allow a torque ratio of the CVT 100 to be varied. The torque ratio refers to a relative position of the first traction interface TI1 and the second traction interface TI2 for a given angular orientation (that is, tilt) of the planet-and-shift-lever subassemblies 2100. When the surface speed of the planets 2102 at the respective first traction interface TI1 is the same as the surface speed of the planets 2102 at the respective second traction interface TI2, the torque ratio is substantially 1:1 and, ignoring system inefficiencies, there is no corresponding torque multiplication. Through controlled tilting of the planet-and-shift-lever subassemblies 2100, the ratio of the surface speed at the first traction interfaces TI1 to that of the surface speed at the second traction interfaces TI2 is selectively adjustable, thereby adjusting torque ratio. As discussed further below, the shift-cam-and-sun subassembly can be configured such that translation of the shift-cam-and-sun subassembly 1300 causes such tilt of the planet-and-shift-lever subassemblies 2100. The direction of tilt of the planet-and-shift-lever subassemblies 2100 from the position corresponding to the torque ratio of 1:1 dictates whether the corresponding torque multiplication is greater than 1 (that is, torque output is greater than torque input) or less than 1 (that is, torque input is greater than torque output).
As depicted in
Presented now is a brief description of torque ratio variation functionality provided by a Continuously Variable Transmission (CVT) in the context of the disclosures made herein (for example, the CVT 100). Such CVT functionality allows essentially every fractional torque ratio within a given range to be selected in a continuous manner as opposed to a discrete or stepped manner. For example, in the case of the CVT 100 disclosed herein, the ability to adjust torque ratio in a continuous manner over a defined torque ratio range is through angular control of the planet-and-shift-lever subassemblies 2100.
It should be noted that such CVT functionality does not inherently offer rotational direction change through torque ratio adjustment. For a given CVT construction, power input rotational direction with respect to power output rotational direction is fixed (that is, the same direction or the opposite direction). For example, referring to the CVT 100 and
Returning now to discussing construction and elements of the CVT 100, as best shown in
Referring to
Referring now to
In one embodiment, the main axle 1000 includes various structural features configured for engaging mating components of subassemblies and/or related fastening devices. The central portion 1010 can include a first segment 1014 of a first diameter, a second segment 1016 of a second diameter, a third segment 1018 of a third diameter, a slot 1020, a locking member seat 1022 (for example, a recess configured for receiving a key), a first lubricant delivery passage 1024, a second lubricant delivery passage 1025, and a lubricant inlet passage 1026. The first segment 1014 can extend from an inboard face 1027 of the axial reaction flange 1003, with the second segment 1016 extending from the first segment 1014, and the third segment 1018 extending from the second segment 1016. In this manner, the segments 1014, 1016, and 1018 can define respective shoulders on which various components and/or subassemblies can be mounted. The second end portion 1006 of the main axle 1000 can include a shoulder 1028 extending from an outboard face 1030 of the axial reaction flange 1003, which shoulder 1028 can have a recess 1032 therein to provide axial clearance for a shaft (not shown) engaged within a splined bore 2310 of the output shaft 2300.
In one embodiment, the main axle longitudinal passage 1001 extends along the longitudinal axis L1 between the first end portion 1006 and the second end portion 1008 of the main axle 1000. The slot 1020, the lubricant delivery passages (1024, 1025), and the lubricant inlet passage 1026 each extend communicatively between a respective exterior face of the main axle 1000 and the longitudinal passage 1001. Adjacent to the first end portion 1006 of the main axle 1000, the longitudinal passage 1001 can be configured to receive a bushing 1036A and a bushing 1036B (See
As best shown in
Referring to
As shown in
The stator 1705 can include a number of shift lever guide flanges 1715. In one embodiment, the shift lever guide flanges 1715 extend from a main body 1720 and are oriented in a radially extending manner. A planet axle passage 1725 extends between each adjacent pair of shift lever guide flanges 1715. Preferably, but not necessarily, the shift lever guide flanges 1715 are uniformly spaced around a central bore 1730 of the stator 1705 whereby the stator 1705 is generally circularly shaped and symmetrical with respect to the central bore 1730. Each shift lever guide flange 1715 includes a skew roller reaction surface 1735 and a shift guide roller reaction surface 1740. The skew roller reaction surface 1735 is substantially flat and the shift guide roller reaction surface 1740 is contoured. Examples of such contour include, but are not limited to, semi-circular, parabolic, elliptical and angularly tapered. Adjacent skew roller reaction surfaces 1735 of adjacent shift lever guide flanges 1715 extend substantially parallel to each other and adjacent shift guide roller reaction surfaces 1740 of adjacent shift lever guide flanges 1715 are substantially aligned.
Referring to
As best shown in
As best shown in
Referring to
In some embodiments, the shift cam surfaces 1330, 1335 of the shift cam bodies 1302, 1304 have substantially identical shift cam surface profiles. One embodiment of data points defining a shape of the shift cam profiles 1330, 1335 is shown in the table of
As shown in
Still referring to
Referring now to
Planet axle shift levers 2106 (“shift levers 2106”) can be fixedly attached to opposing end portions 2107 of the planet axle 2104 such that the planet 2102 is positioned between the shift levers 2106. The planet axle 2104 extends through a planet axle bore 2111 (see
As shown in
At a second end portion 2125 of the shift lever 2106, a roller receiving channel 2129 can be provided. A shift cam roller 2128 is positioned in the roller receiving channel 2129. A shift cam roller axle 2130 extends through the shift cam roller 2128 and into engagement with axle receiving passages 2131 (
Referring to
Hence, each planet-and-shift-lever subassembly 2100 is substantially axially and radially constrained relative to the main axle longitudinal axis L1, and constrained with respect to rotation about any radial axis extending perpendicular to the main axle longitudinal axis L1. However, preferably, each planet-and-shift-lever subassembly 2100 is rotatable about the respective tangential reference axis T1, which extends through a center point of the respective planet 2102 substantially perpendicular to a radial reference axis extending from the main axle longitudinal axis L1 through the center point of the respective planet 2102.
Referring now to
As best shown in
As best shown in
The ramps 2840, 2870 can each be configured for receiving one of the load cam rollers 2806 (
The first traction interface TI1 is the region of contact between the contact surface 2865 and each one of the planets 2102 (one shown in
As disclosed above, in one embodiment, the first axial force generator subassembly 2800A and the second axial force generator subassembly 2800B are substantially identical in construction and function. Accordingly, through traction at each second traction interface TI2 (See
As shown in
The first side of the thrust reaction flange 2304 can be defined by a bearing thrust reaction surface 2322 (See
Referring now to
As best shown in
Referring to
Referring to
Referring now to
A bearing 2686 couples between the output shaft neck 2302 and the first housing cover plate 2605 for rotatably and radially supporting the first housing cover plate 2605 on the output shaft 2300. The bearing 2686 resides within the central bore 2308 secured between retention devices such as c-clips engaged with the retention device grooves 2631. A ball thrust bearing 2688 couples between the bearing recess 2625 of the first housing cover plate 2605 and the bearing support shoulder 2324 for reacting axial loads between the first housing cover plate 2605 and the output shaft 2300. Alternatively, in some embodiments, a thrust washer 2690 and a thrust needle bearing 2692 couple between the thrust washer recess 2660 of the first housing cover plate 2605 and the bearing thrust reaction surface 2322 of the output shaft 2300 for reacting axial loads between the first housing cover plate 2605 and the output shaft 2300.
An axle ball bearing 2694 couples between the second housing cover plate 2610, the end cap 2617, and the reaction flange 1605 of the auxiliary axle 1600 for reacting radial loads between the second housing cover plate 2610 and the auxiliary axle 1600. The axle ball bearing 2694 engages a bearing recess 2655, a bearing support surface 1640 of the auxiliary axle 1600, and a bearing support surface of the end cap 2617. The end cap 2617 is secured to the second housing cover plate 2610 through, for example, threaded fasteners (not shown) that extend through holes in the end cap 2617 and engage mating holes of the second housing cover plate 2610, thereby securing the axle ball bearing 2694 in place. A thrust needle roller bearing 1755 is coupled between the thrust washers 1757, 1759, which are respectively in contact with the thrust washer recess 2660 of the second housing cover plate 2610 and a thrust washers reaction surface 1760 of the stator subassembly 1700. The auxiliary axle lubricant passages 1630 are aligned with the first lubricant delivery passage 1024 of the main axle 1000 to allow the flow of lubricant from the shift rod central bore 3026 to the axle ball bearing 2694, thrust bearing 1755, and optionally subsystem components adjacent to the reaction flange 1605 and/or the axle ball bearing 2694.
The second housing cover plate 2610 circumferentially engages the first axial force generator subassembly 2800A in a manner that inhibits unrestricted rotation of the first axial force generator subassembly 2800A with respect to the housing subassembly 2600. More specifically, all or a portion of the engagement features 2326 engage adjacent pairs of the engagement features 2835 of the load cam ring 2802 with the pilot guides 2328 extending over a peripheral edge of the load cam ring 2802 for helping to maintain alignment of the load cam ring 2802 with the second housing cover plate 2610. Through such inhibiting of unrestricted rotation of the second axial force generator subassembly 2800B with respect to the second housing cover plate 2610, torque can be transferred to the second axial force generator subassembly 2800B from the second housing cover plate 2610.
As best shown in
Referring now to
In operation (referring to
Referring to
A main body 3702 of the drivetrain casing 3700 includes a transmission mounting portion 3704 to which the flange 2710 of the CVT 100 (See
The drivetrain casing main body 3702 is configured for fixedly securing to a mating portion of a vehicle chassis structure or a prime mover structure. In one embodiment, the main body 3702 includes fastener bosses 3714 that are each configured for receiving a fastener (for example, a threaded bolt or threaded screw). Through engagement of each fastener with a respective engagement portion of the vehicle chassis structure or a prime mover structure (for example, treaded holes), fasteners extending through the fastener bosses 3714 secure the drivetrain casing 3700 to the vehicle chassis structure or a prime mover structure.
In one embodiment, the drivetrain casing 3700 includes a lubricant sump cavity 3716. The lubricant sump cavity 3716 is a partially separated space from the main body interior space 3712 and includes an edge portion 3718 that is configured for being engaged by a sump cavity cover plate (not shown). Through sealed engagement of the sump cavity cover plate with the edge portion 3718, the lubricant sump cavity 3716 and the sump cavity cover plate jointly define a sump chamber in which lubricant can be contained and extracted by a sump pump (not shown) that supplies lubricant to the lubricant manifold 2700. It is disclosed herein that the sump cavity cover plate can be replaced by a wall that is unitarily formed with the drivetrain casing 3700, with a lubricant fill plug opening and/or lubricant drain plug opening being provided for facilitating filling the sump chamber with lubricant and/or draining removing lubricant from the sump chamber. It is further disclosed herein that the drivetrain casing 3700 and/or the sump cavity cover plate can include cooling fins for dissipating heat.
Referring to
Still referring to
The number of planet-and-shift-lever subassemblies 2100 discussed above in reference to the CVT 100 is arrayed angularly around the input shaft longitudinal axis L21 and is supported jointly by the shift-cam-and-sun subassembly 1300 and the stator subassembly 1700. The input shaft 4202 supports the output shaft 2300 discussed above in reference to the CVT 100. Bearings 2686, 2688, and 2332 rotatably support the output shaft 2300 between the input shaft 4202 and the housing subassembly 5600 in a manner such that a longitudinal axis L23 of the output shaft 2300 extends coincidentally with the input shaft longitudinal axis L21.
The output shaft 2300 and the auxiliary axle 4600 jointly support a housing subassembly 5600. The housing subassembly 5600 is supported in a manner that coincidentally aligns a centerline axis C22 of the housing subassembly 5600 with the input shaft longitudinal axis L21 and allows relative rotation of the housing subassembly 5600 with respect to output shaft 2300 and the auxiliary axle 4600. A shift actuation subassembly 5900 mounts on the input shaft 4202 in a manner allowing select components of the shift actuation subassembly 5900 to rotate with the input shaft 4202 while other components of the shift actuation subassembly 5900 are held stationary and/or allowed to rotate independent from rotation of the input shaft 4202. The shift actuation subassembly 5900 is coupled to the shift-cam-and-sun subassembly 1300 through a shift rod 6000 for facilitating selective translation of the shift-cam-and-sun subassembly 1300 along the input shaft longitudinal axis L21. A lubricant manifold 5700 is jointly supported by the housing subassembly 5600, the shift actuation subassembly 5900 and a bearing 4208 in a manner whereby the lubricant manifold 5700 is held stationary with respect to rotation of the input shaft 4202. A lubricant sump body 6300 mounts on the housing subassembly 5600 thereby providing a sump chamber 6205 in which a supply of lubricant can be maintained.
With respect to the IVT 4200, the stator subassembly 1700 and the planet-and-shift-lever subassemblies 2100 can be configured and interact in the same manner discussed above in reference to the CVT 100. Accordingly, the planet-and-shift-lever subassemblies 2100 can be synchronously rotated for facilitating torque ratio adjustment. Through such synchronous rotation, all of the planet-and-shift-lever subassemblies 2100 are in the same relative rotational position at a given point in time. Furthermore, it is disclosed herein that the stator subassembly 1700 can be secured to the input shaft 4202 and/or the auxiliary axle 4600 by any suitable fastening method. Examples of such suitable fastening methods include, but are not limited to, interference press fit, threaded fastener and mating threaded holes, keyed engagement, splined engagement, etc. For example, one or both of the stators 1705A, 1705B can be secured using screws that engage mating threaded holes (not shown) of the input shaft 4202 and/or the auxiliary axle 4600.
Referring now to
During operation of the IVT 4200, torque exerted on the input shaft 4202 causes the input shaft 4202 and the stator subassembly 1700 to jointly rotate about the input shaft longitudinal axis L21. The stator subassembly 1700 supports the planet-and-shift-lever subassemblies 2100 in a manner that inhibits unrestricted relative rotation of the planet-and-shift-lever subassemblies 2100 with respect to the stator subassembly 1700. Accordingly, the planet-and-shift-lever subassemblies 2100 rotate together with the input shaft 4202 and the stator subassembly 1700. The lubricant manifold 5700, the housing subassembly 5600, the lubricant sump body 6200, and portions of the shift actuation subassembly 5900 are held stationary with respect to rotation of the input shaft 4202. Through traction at a respective first traction interface TI21 between the input axial force generator subassembly 2800A and each planet 2102, torque is exerted by the first axial force generator subassembly 2800A on the planets 2102, thereby causing each planet 2102 to rotate about a respective planet longitudinal axis L4. The first traction interface TI21 is defined, as used here, as a region of contact between the first axial force generator subassembly 2800A and the respective planet 2102. The interaction between the first-axial force generator subassembly 2800A and the planets 2102 causes the planet-and-shift-lever subassemblies 2100 to orbit about the longitudinal axis L23. Through traction at a respective second traction interface TI22 between the second axial force generator subassembly 2800B and each planet 2102, torque is exerted by the planets 2102 on the second axial force generator subassembly 2800B, thereby causing the second axial force generator subassembly 2800B and output shaft 2300 to jointly rotate about the output shaft longitudinal axis L23. The second traction interface TI22 is defined, as used here, as a region of contact between the second axial force generator subassembly 2800B and the respective planet 2102.
Turning now to a brief discussion of power flow through the IVT 4200 and still referring to
Presented now is a brief description of torque ratio variation functionality provided by an Infinitely Variable Transmission (IVT) in the context of the disclosures made herein (for example, the IVT 4200). Such IVT functionality, like the CVT functionality described above in reference to the CVT 100, allows essentially every fractional ratio within a given range to be selected in a continuous manner as opposed to a discrete or stepped manner. However, in addition to allowing essentially every fractional torque ratio within a given range to be selected in a continuous manner, IVT functionality also allows delivery of a zero output speed (a “powered zero” state) with a non-zero input speed of a power delivery device (for example, constant speed of a sprocket attached to the input shaft 4202 of the IVT 4200). Hence, given the definition of torque ratio as the ratio of input torque to output torque, an IVT in the context of the disclosures made herein is (at least theoretically) capable of delivering an infinite set of torque ratios.
For a given IVT construction, power input rotational direction with respect to power output rotational direction is variable. That is, for a given power input rotational direction, torque ratio adjustment can result in power output rotational direction being the same or opposite the given power input rotational direction. The zero output speed discussed above is present at the adjustment position where the input and output rotational directions transition between being the same and being opposite. For example, referring to the IVT 4200 and
With the planet-and-shift-lever subassemblies 2100 adjusted with their respective longitudinal axis L4 extending parallel to the longitudinal axis L21 of the input shaft 4202 (as shown in
Still referring to the IVT 4200 and
It should be noted that some transmissions use a continuously variable variator unit (for example a CVT) coupled to other gearing and/or clutches to produce IVT functionality. Usually, in such transmissions, power is diverted from a mixing device, routed through the CVT section, and summed back to the original power path at some node in the transmission. In such an arrangement, recirculating power can be greater than the throughput power and can significantly decrease the efficiency of the transmission. Many of the inventive embodiments described here require no split powered arrangement to achieve IVT functionality. In the context of the disclosures presented herein, IVT functionality such as that provided by the IVT 4200 is preferably understood as providing IVT functionality without being necessarily coupled to additional gearing, clutches, split powered arrangements, and/or other devices.
Returning now to discussing construction and elements of the IVT 4200, as best shown in
The input shaft 4202 includes various structural features configured for engaging mating components of subassemblies and/or related fastening devices. In one embodiment, the input shaft 4202 includes a first segment 4213 of a first diameter, a second segment 4214 of a second diameter, a third segment 4216 of a third diameter, a fourth segment 4218, a fifth segment 4219 of a fifth diameter, a first slot 4220, a first locking member seat 4222 (for example, a recess configured for receiving a key), a second slot 4224, a second locking member seat 4225, a lubricant inlet passage 4226, a lubricant delivery passage 4228, and a retention device groove 4229. The first segment 4213 can extend from an inboard face 4229 of the axial reaction flange 4206, with the second segment 4214 extending from the first segment 4213, the third segment 4216 extending from the second segment 4214, the fourth segment 4218 extending from the third segment 4216, and the fifth segment 4219 extending from the fourth segment 4218. In this manner, the input shaft segments 4213-4219 can define respective shoulders on which various components and/or subassemblies can be mounted.
The first end portion 4212 of the input shaft 4202 can include a shoulder 4230 extending from an outboard face 4231 of the axial reaction flange 4206 for supporting a bearing 4232 and can have a recess 4233 therein to provide for receiving a plug 4233 adapted to contain a spring (not shown) within a longitudinal passage 4236 of the input shaft 4202. The bearing 4232 serves to rotatably support the output shaft 2300 on the input shaft 4202. The spring and plug arrangement can be configured to bias the shift rod 6000 to a prescribed position. The first locking member seat 4222 is configured for receiving a retention device (for example, a key) that also engages a mating retention feature (for example, slot) of the auxiliary shaft 4600 for inhibiting unrestricted rotation of the auxiliary shaft 4600 with respect to the input shaft 4202. The second locking member seat 4225 is configured for engaging a retention device that also engages a mating structure (for example slot) of a power input means (not shown) such as, for example, a pulley, gear, sprocket, etc.
In one embodiment, a longitudinal passage 4236 of the input shaft 4202 extends along the longitudinal axis L1 between the end portions 4212, 4239. The longitudinal passage 4236 can be configured for having the shift rod 6000 slidably disposed therein. The slot 4220, 4224, the lubricant inlet passage 4226, and the lubricant delivery passage 4228 each extends communicatively between a respective exterior face of the input shaft 4202 and the longitudinal passage 4236 for allowing respective structural interconnection and/or providing a respective lubricant flow path.
As best shown in
Referring to
Referring to
The shift screw 5906 rotationally engages the shift pin collar 5902 and engages the shift nut 5904, which mounts on a mating structure of the lubricant manifold 5700 in a manner that limits, if not inhibits, relative rotation and translation therebetween. For example, in one embodiment, a press fit interface is provided between a central bore 5917 of the shift nut 5904 and the mating structure of the lubricant manifold 5700, which precludes the shift nut 5904 from relative rotation or translation with respect to the engaged mating structure. The shift screw bearing 5910 is coupled between the shift pin collar 5902 and the shift screw 5906 for allowing the shift pin collar 5902 to rotate independently from the shift screw 5906. With respect to the shift screw 5906 (See
Threads 5930 of the shift nut 5904 engage threads 5932 of the shift screw 5906. Rotation of the shift screw 5906 causes the shift screw 5906 to thread in or thread out of the shift nut 5904, resulting in corresponding translation of the shift screw 5906 along the input shaft longitudinal reference axis L21. Accordingly, due to constrainment of the shift screw 5906 with the shift pin collar 5902, the shift pin collar 5902 translates essentially in unison with the shift screw 5906 as does the shift rod 6000 and shift-cam-and-sun subassembly 1300. In this manner, the torque ratio can be adjusted through rotation of the shift screw 5906. The control plate 5908 can be attached to the shift screw 5906 such as through press fit interference between a central bore 5934 of the control plate 5908 and a shoulder 5936 of the shift screw 5906. In one embodiment, the shift screw 5906 includes a reaction flange 5014 adapted to react and/or locate the control plate 5908. In this manner, an external adjustment mechanism can be connected to the control plate 5908 such as via the one of more holes 5938 for allowing the external adjustment mechanism to control rotation of the shift screw 5906 and, thereby, control adjustment of the torque ratio.
As best shown in
Referring now to
As shown in
Referring to
As shown in
The chassis mounting holes 6305 can be positioned adjacent an exterior perimeter edge portion of the body 6302 and can be configured for receiving fasteners therein to secure the lubricant sump to a support structure (for example, a chassis, housing, block and/or case of a vehicle, an engine, a transmission, a motor, a differential, a power take-off unit and/or the like). The housing mounting holes 6310 can be positioned uniformly around the lubricant cavity 6320 and can be configured for receiving fasteners therein to secure the body 6302 to the housing subassembly 5600. For example, the mounting holes 6310 can be arranged to align with all or a portion of the mounting holes 5646 of the first housing cover plate 5605 such that the same fasteners fasten the body 6302 and the first housing cover plate 5605 to the central housing shell 5615 of the housing subassembly 5600.
In operation (referring to
Referring now to
Turning now to
During operation of the IVT 6700, the shift rod 6000 translates axially to actuate a change in transmission ratio. The range of transmission ratio corresponds at least in part to the axial distance travelled by the shift rod 6000. In some embodiments, the axial travel of the shift rod 6000 is limited on one end by the shift-stop-spring assembly 6701, and is limited on another end by the shift-stop-dowel assembly 6702. During operation of the IVT 6700, reaction of the gyroscopic overturning moment that can be generated in the IVT 6700 is achieved by limiting the axial travel of the shift rod 6000 with, for example, washers 6750, or with the shift stop dowel assembly 6702 and the shift-stop-spring assembly 6701. Collectively, these means of limiting axial travel of the shift rod 6000 are called shift stops. The gyroscopic forces imposed on various rotating components depend on the axial position of the shift stops. Shift stops can prevent excess axial travel of the shift-cam-and-sun assembly 1300 due to the gyroscopic forces that tend to tilt the planet-and-shift-lever assemblies 2100 during operation. Without shift stops such as washers 6750, the gyroscopic forces are reacted through the coupling device 1002. In other embodiments, the washers 6750 can be replaced by springs, such as disc springs or wave springs to provide some restoring force to the shift rod. The shift stop springs 6703 and 6706 can provide a restoring force to the shift rod 6000. The axial position of the adjustment screws 6705 and 6710 along the input shaft 4202 can be adjusted to set the desired maximum axial travel of the shift rod 6000, and therefore set the desired transmission ratio range.
Still referring to
Various embodiments of subassemblies are disclosed herein and each includes respective components thereof. It is disclosed herein that such subassemblies are not limited to the specific constituent components shown herein. For example, each one of such subassemblies can include few, greater and/or different constituent components disclosed herein. Furthermore, the functionality provided by a subassembly disclosed herein can be provided by a collection of components that are not characterized or deemed to be a subassembly. Furthermore, the bearings and bushings can be used interchangeably in some or all of their implementations. Still further, unless otherwise specified, the inventive embodiments are not limited to bearings being of a particular type.
The embodiments described herein are examples provided to meet the descriptive requirements of the law and to provide examples. These examples are only embodiments that can be employed by any party and they are not intended to be limiting in any manner. Therefore, the invention is defined by the claims that follow and not by any of the examples or terms used herein.
This application is a continuation of U.S. patent application Ser. No. 14/147,866, filed Jan. 6, 2014 and scheduled to issue on Nov. 10, 2015 as U.S. Pat. No. 9,182,018, which is a continuation of U.S. patent application Ser. No. 13/679,337, filed Nov. 16, 2012 and issued on Jan. 7, 2014 as U.S. Pat. No. 8,622,866, which is a continuation of U.S. patent application Ser. No. 12/394,821, filed Feb. 27, 2009 and issued on Nov. 20, 2012 as U.S. Pat. No. 8,313,405, which claims the benefit of U.S. Provisional Patent Application No. 61/032,834, filed on Feb. 29, 2008. Each of the above-identified applications is hereby incorporated by reference in its entirety.
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| Number | Date | Country | |
|---|---|---|---|
| 20160061301 A1 | Mar 2016 | US |
| Number | Date | Country | |
|---|---|---|---|
| 61032834 | Feb 2008 | US |
| Number | Date | Country | |
|---|---|---|---|
| Parent | 14147866 | Jan 2014 | US |
| Child | 14935213 | US | |
| Parent | 13679337 | Nov 2012 | US |
| Child | 14147866 | US | |
| Parent | 12394821 | Feb 2009 | US |
| Child | 13679337 | US |
