JP6453377B2 - Continuously variable transmission - Google Patents

Description

  The field of the invention relates generally to mechanical and / or electromechanical power adjustment devices and methods, and more particularly to power transmission mechanisms or power, such as the flow of power from a prime mover to one or more auxiliaries or driven devices. The present invention relates to a continuously and / or infinitely variable planetary power adjusting apparatus and method for adjusting power flow in a drive mechanism.

  In some systems, a single power source drives multiple devices. A power source typically has a narrow operating speed range where its performance is optimal. The power source is preferably operated within an operating speed range where its performance is optimal. Driven devices also typically have a narrow operating speed range where their performance is optimal. The driven device is also preferably operated within an operating speed range where its performance is optimal. Usually, a joint is employed to transmit power from a power source to a driven device. When a coupling that does not make direct adjustments connects the power source to the driven device, the driven device operates at a speed proportional to the speed of the power source. However, the optimal operating speed of the driven device is often not directly proportional to the optimal operating speed of the power source. Accordingly, it is preferable to incorporate into the system a coupling adapted to adjust between the speed of the power source and the speed of the driven device.

  The coupling between the power source and the driven device can be selected such that the input speed from the power source decreases or increases at the output of a given coupling. However, in a frequently implemented system, a typical known power transmission mechanism configuration and / or coupling configuration is, at best, between the input speed from the power source and the speed of power transmission to the driven device. It only allows a certain ratio. One such system is the so-called front end accessory drive (FEAD) system that is employed in many automotive applications. In a typical FEAD system, a prime mover (usually an internal combustion engine) provides power to operate one or more accessories such as cooling fans, water pumps, oil pumps, power steering pumps, alternators and the like. During the operation of the automobile, the accessory is forced to operate at a speed that is a fixed relationship to the speed of the prime mover. Thus, for example, when the engine speed is increased from 800 rpm during idling to cruising speed of 2500 rpm, the speed of each accessory driven by the engine is proportional to the increase in engine speed. As a result, some auxiliaries may be operating at varying speeds ranging from 1,600 rpm to 8,000 rpm. As a result of such a system configuration, it is often the case that no auxiliary equipment operates within its maximum efficiency speed range. Thus, inefficiency arises from wasted energy during operation and the accessory being too large to handle speed and / or torque ranges.

  Accordingly, there continues to be a need for an apparatus and method for adjusting power transmission between a prime mover and a driven device. In some systems, it may be beneficial to adjust the speed and / or torque transmission from the motor and / or internal combustion engine to one or more driven devices operating at various efficiency-optimized speeds. Depending on the current automotive application, it is necessary for the power adjuster to manage the front-end accessory drive within existing packaging limits. Embodiments of the present invention of power adjustment devices and / or power transmission mechanisms described below address one or more of these needs.

  The systems and methods described herein have several features, one of which does not yield its desired attributes alone. Here, the more prominent features will be briefly described without limiting the scope represented by the following claims. After considering this description, and in particular after reading the section entitled “Modes for Carrying Out the Invention”, how the features of the present system and method provide several advantages over conventional systems and methods. It will be understood.

  One aspect of the present invention relates to an auxiliary drive continuously variable drive (CVAD) having an auxiliary machine and a continuously variable transmission (CVT) coupled to the auxiliary machine. The auxiliary machine continuously variable transmission has a traction planet group. Each traction planet can be adapted to rotate about a tiltable axis. The CAVD also has a skew actuator operably coupled to the CVT. The skew actuator can be adapted to tilt the axis of the traction planet by applying a skew condition to the CVT.

  Another aspect of the present invention relates to an auxiliary drive continuously variable transmission (CVAD) having a traction planet group arranged at an angle around the longitudinal axis of the CVAD. The CVAD can have a planetary axis group. Each planet shaft is operably coupled to each traction planet. Each planet axis defines a rotation axis that can tilt with respect to each traction planet. Each planetary axis can be configured to be angularly displaced in a plane perpendicular to the longitudinal axis. Each planetary axis can be configured to be angularly displaced in a plane parallel to the longitudinal axis. In one embodiment, the CVAD has a first carrier member operably coupled to the first end of each planet shaft. The first carrier member can be mounted about the longitudinal axis. The CVAD has a second carrier member operably coupled to the second end of each planet shaft. The second carrier member can be mounted about the longitudinal axis. The first carrier member and the second carrier member are configured to rotate relative to each other about the longitudinal axis.

  Yet another aspect of the invention relates to an auxiliary drive continuously variable transmission (CVAD) having a rotatable input coaxial with the longitudinal axis of the CVAD. The CVAD has a variator that is coaxial with the longitudinal axis and is coupled to a rotatable input. The variator has a rotatable output. The CVAD has a planetary gear assembly coupled to the rotatable output. The planetary gear assembly is configured to supply power to the accessory. In one embodiment, the variator has traction planets arranged at an angle around the main shaft. The variator can have a first carrier member operably coupled to each of the traction planets. The variator can also have a second carrier member operably coupled to each of the traction planets. The second carrier member is configured to give a skew state to each of the planetary shafts by rotating with respect to the first carrier member.

  One aspect of the present invention relates to an auxiliary drive continuously variable transmission (CVAD) having a traction planet group arranged at an angle around a longitudinal axis of the CVAD. In one embodiment, the CVAD has a planetary axis group operably coupled to each traction planet. Each planet axis defines a rotation axis that can tilt with respect to each traction planet. Each planetary axis can be configured to be angularly displaced in a plane perpendicular to the longitudinal axis. Each planetary axis can be configured to be angularly displaced in a plane parallel to the longitudinal axis. In one embodiment, the CVAD has a first carrier member disposed coaxially about the longitudinal axis. A first carrier member can be operably coupled to each traction planet. The first carrier member can have a plurality of radial offset grooves arranged at an angle around the center of the first carrier member. Each of the radial offset grooves has a linear offset from the centerline of the carrier member. The CVAD can have a second carrier member disposed coaxially about the longitudinal axis. The second carrier member can have a plurality of radial grooves. The radial grooves can be arranged at an angle around the center of the second carrier member. Each of the radial grooves is substantially radially aligned with the center of the second carrier member. The CVAD can also have a skew actuator operably coupled to at least one of the first carrier member and the second carrier member. The actuator can be configured to apply a relative rotation between the first carrier member and the second carrier member.

  Another aspect of the invention relates to a method for facilitating control of an auxiliary drive continuously variable transmission (CVAD) speed ratio. In one embodiment, the method includes providing a traction planet group. The method includes providing a planet axis for each of the traction planets. Each traction planet can be configured to rotate about its respective planet axis. The method can include providing a first carrier member configured to engage a first end of each of the planet shafts. The first carrier member can be mounted along the longitudinal axis of the CVAD. The method can include providing a second carrier member configured to engage a second end of each of the planet shafts. The second carrier member can be attached coaxially with the first carrier member. The method also provides the first carrier member relative to the second carrier member such that during operation of the CVAD, the first carrier member can be rotated relative to the second carrier member about the longitudinal axis. A placing step may be included.

  Another aspect of the invention relates to a variator having traction planets arranged at an angle about a longitudinal axis. In one embodiment, the variator has a first carrier member disposed coaxially about the longitudinal axis. A first carrier member can be operably coupled to each traction planet. The first carrier member can have a plurality of radial offset grooves arranged at an angle around the center of the first carrier member. In one embodiment, each of the radial offset grooves has a linear offset from the centerline of the carrier member. The variator can also have a second carrier member disposed coaxially about the longitudinal axis. The second carrier member can have a plurality of radial grooves. In one embodiment, the radial grooves are arranged at an angle around the center of the second carrier member. Each of the radial grooves is substantially radially aligned with the center of the second carrier member. The variator can also have a traction sun assembly radially inward of and in contact with each traction planet. The traction sun assembly can be in contact with the first carrier member and the second carrier member. The traction sun assembly is fixed substantially along the longitudinal axis.

  Another aspect of the invention relates to a method for assembling an apparatus for regulating power to an accessory. The method includes providing a continuously variable transmission (CVT) having traction planets arranged at an angle about a longitudinal axis. In one embodiment, the CVT has a skew-based control system adapted to provide a skew condition for each of the traction planets. The method also includes operably coupling the CVT to the accessory.

  Yet another aspect of the invention relates to a variator having traction planets arranged at an angle about a longitudinal axis. In one embodiment, the variator has a first carrier member disposed coaxially about the longitudinal axis. A first carrier member can be operably coupled to each traction planet. The first carrier member has a plurality of radial offset grooves arranged at an angle around the center of the first carrier member. Each of the radial offset grooves has a linear offset from the centerline of the carrier member. The variator can have a second carrier member arranged coaxially about the longitudinal axis. In one embodiment, the second carrier member has a plurality of radial grooves. The radial grooves can be arranged at an angle around the center of the second carrier member. Each of the radial grooves can be substantially radially aligned with the center of the second carrier member. The variator can also have a traction sun located radially inward of and in contact with each traction planet. The traction sun has an outer periphery provided with a first contact surface and a second contact surface. The first contact surface and the second contact surface can be configured to contact each of the traction planets.

  In another aspect, the invention relates to a variator having traction planets arranged at an angle about a longitudinal axis. In one embodiment, the variator has a planet axis operably coupled to each traction planet. The planetary axis can be configured to provide a rotational axis that can be tilted with respect to each traction planet. The variator can have a first carrier member disposed coaxially about the longitudinal axis. The first carrier member can be operably coupled to the first end of the planet shaft. The variator can have a second carrier member arranged coaxially about the longitudinal axis. A second carrier member can be operably coupled to the second end of the planet shaft. The variator can also have a carrier retaining ring coupled to the first carrier member and the second carrier member. The carrier retaining ring may be substantially non-rotatable about the longitudinal axis. The carrier retaining ring can be configured to axially couple with the first carrier member and the second carrier member. The first carrier member is configured to give a skew state to each of the planetary shafts by rotating with respect to the second carrier member.

  One aspect of the invention relates to a variator having traction planets arranged at an angle about a longitudinal axis. The variator has a first carrier member that is coaxial with the longitudinal axis. In one embodiment, the variator has a second carrier member that is coaxial with the longitudinal axis. The variator can have a skew driver coupled to the first carrier member and the second carrier member. The skew driver can be adapted to rotate the first carrier member in a first rotational direction about the longitudinal axis. The skew driver can be adapted to rotate the second carrier member in a second rotational direction about the longitudinal axis. The first rotation direction is substantially opposite to the second rotation direction.

  Another aspect of the present invention relates to a method for adjusting the speed ratio of an auxiliary continuously variable transmission (CVAD) having traction planets. Each traction planet has a tiltable axis of rotation. In one embodiment, the CVAD has a carrier member operably coupled to each of the traction planets. The method can include establishing a setpoint for the angular displacement of the carrier member. The set value for the angular displacement of the carrier member is based at least in part on the set value for the speed ratio. The method includes rotating the carrier member to a set value for the angular displacement of the carrier member. By rotating the carrier member, a skew state is caused for each tiltable rotation axis. The carrier member is configured to adjust the skew state when each tiltable rotation axis is tilted. Rotating the carrier member includes actuating a skew actuator.

  Yet another aspect of the present invention relates to a method for adjusting the speed ratio of an auxiliary continuously variable transmission (CVAD) having traction planets. Each traction planet has a tiltable axis of rotation. The CVAD has a skew actuator operably coupled to each of the traction planets. In one embodiment, the method includes determining a skew actuator command signal. The skew actuator command signal is based at least in part on a set value for the tilt angle. The method also includes adjusting a skew state of the traction planet by applying a skew actuator command signal to the skew actuator.

  One aspect of the present invention relates to a method for adjusting the speed ratio of an auxiliary continuously variable transmission (CVAD) having a traction planet group. Each traction planet has a tiltable axis of rotation. The CVAD has a skew actuator operably coupled to each of the traction planets. In one embodiment, the method includes determining a skew actuator command signal. The command signal is based at least in part on a setpoint for the desired speed. The method also includes adjusting the skew state of the traction planet by applying a skew actuator command signal to the skew actuator.

  One aspect of the invention relates to a traction planet assembly having a traction planet having a central hole. The traction planet assembly can have a planet shaft disposed in the central hole. The planetary shaft has a first end and a second end. In one embodiment, the traction planet assembly has a first leg coupled to the first end of the planet shaft. The first leg may be substantially non-rotatable with respect to the planetary axis. The traction planet assembly can have a second leg coupled to the second end of the planet shaft. The second leg can be substantially rotatable with respect to the planetary axis.

  Another aspect of the invention relates to a traction planet assembly having a traction planet with a central hole. In one embodiment, the traction planet assembly has a planet shaft disposed within the central hole. The planetary shaft has a first end and a second end. Internal holes can be provided in the first end and the second end. The traction planet assembly can have a shift reaction ball received in each of the internal holes. In one embodiment, the traction planet assembly has a first leg coupled to the first end of the planet shaft. The traction planet assembly may also have a second leg coupled to the second end of the planet shaft. Tapered sides are provided on the first leg and the second leg.

  Yet another aspect of the present invention includes a traction sun assembly for a multi-speed transmission (CVT) having a traction planetary assembly. The traction sun assembly has a traction sun that is coaxial with the longitudinal axis of the CVT. The traction sun is radially inward of each of the traction planet assemblies and can be in contact therewith. In one embodiment, the traction sun assembly has a shift cam operably coupled to the traction sun. The traction sun assembly can also have a plurality of anti-rotation inserts attached to the shift cam.

  One aspect of the present invention relates to a carrier member for a continuously variable transmission (CVT) having a traction planet group. The carrier member can have a substantially bowl-like body with a central hole. In one embodiment, the carrier member can have a plurality of radial offset grooves arranged at an angle around the central hole. Each of the radial offset grooves can have a linear offset from the centerline of the bowl.

  In another aspect, the invention relates to a skew actuator for a continuously variable transmission (CVT) having a skew control system. The skew actuator can have a hydraulic piston coupled to the CVT. In one embodiment, the skew actuator has a hydraulic control valve in fluid communication with the hydraulic piston. The skew actuator can also have a spool actuator coupled to the hydraulic control valve. The spool actuator may be configured to adjust the hydraulic control valve based at least in part on the desired skew state of the CVT.

  Another aspect of the present invention relates to a skew control system for an auxiliary continuously variable transmission (CVAD) having a traction planet group. The skew control system has a sensor configured to receive data from the CVAD. The skew control system can have a skew actuator configured to communicate with the control module. The skew actuator can be further configured to impart a skew state to each of the CVAD traction planets. The skew control system can also have a skew controller in communication with the control module. The skew controller can be configured to determine a skew actuator command signal based at least in part on a signal from the sensor. The skew actuator command signal is configured to control the output speed of the CVAD.

1 is a perspective view of an embodiment of the present invention of an auxiliary drive continuously variable transmission (CVAD) having a skew control system. FIG. It is a cross-sectional perspective view of a continuously variable transmission (CVT) that can be used with the CVAD of FIG. FIG. 3 is an exploded perspective view of the CVT of FIG. 2. It is sectional drawing of CVT of FIG. FIG. 3 is a partial cross-sectional perspective view of a variator subassembly that may be used with the CVT of FIG. 2. FIG. 3 is a cross-sectional view of several components of the CVT of FIG. FIG. 6 is a cross-sectional detail view A of several components of the variator subassembly of FIG. FIG. 6 is a perspective view of a carrier retaining ring that can be used with the variator subassembly of FIG. FIG. 3 is a perspective view of an embodiment of the present invention of a U-shaped member that can be used with the CVT of FIG. 2. FIG. 6 is a perspective view of an embodiment of the present invention of a carrier member that can be used with the variator subassembly of FIG. 5. FIG. 6 is a cross-sectional view of a traction planet assembly that may be used with the variator subassembly of FIG. FIG. 12 is a perspective view of an embodiment of the present invention of a leg that can be used with the traction planet assembly of FIG. 11. It is sectional drawing AA of the leg part of FIG. 12A. FIG. 6 is a cross-sectional perspective view of a traction sun assembly that may be used with the variator subassembly of FIG. FIG. 14 is an exploded cross-sectional perspective view of the traction sun assembly of FIG. 13. 1 is a cross-sectional view of an embodiment of the present invention of a continuously variable transmission (CVT) having a skew-based control system. FIG. 16 is a perspective view of the variator subassembly of the CVT of FIG. 15. FIG. 17 is a cross-sectional view of the variator subassembly of FIG. 16. FIG. 17 is an exploded perspective view of the variator subassembly of FIG. 16. FIG. 17 is a plan view of the variator subassembly of FIG. 16. FIG. 17 is a plan view of an embodiment of the present invention of a carrier member that can be used with the variator subassembly of FIG. 16. FIG. 20B is a cross-sectional view of the carrier member of FIG. 20A. FIG. 20B is a perspective view of the carrier member of FIG. 20A. FIG. 20B is a detailed plan view B of the radial offset groove of the carrier member of FIG. 20A. FIG. 21B is a schematic view of the radial offset groove of FIG. 21A. FIG. 21B is another schematic view of the radial offset groove of FIG. 21A. FIG. 21B is still another schematic view of the radial offset groove of FIG. 21A. FIG. 20B is a plan view of another embodiment of the radial offset groove of the carrier member of FIG. 20A. FIG. 21B is a schematic view of the radial offset groove of FIG. 21E. FIG. 21E is another schematic view of the radial offset groove of FIG. 21E. FIG. 21E is still another schematic view of the radial offset groove of FIG. 21E. FIG. 17 is a cross-sectional view of an embodiment of a traction planet assembly that may be used with the variator subassembly of FIG. FIG. 16 is a perspective view of an embodiment of a housing member that can be used with the CVT of FIG. 2 or FIG. 15. FIG. 24 is another perspective view of the housing member of FIG. 23. FIG. 16 is a flowchart of a skew-based control process that can be used with the CVT of FIG. 2 or FIG. FIG. 26 is a graph representing a lookup table that can be used in a sub-process of the skew-based control process of FIG. 25. FIG. 26 is a flowchart of an actuator sub-process that can be used with the skew-based control process of FIG. 1 is a schematic diagram of an embodiment of the present invention of a skew-based control system. FIG. 28B is a schematic diagram of an embodiment of the present invention of a skew actuator that can be used with the skew-based control system of FIG. 28A. FIG. 29 is a schematic diagram of some electronic hardware that can be used with the skew-based control system of FIG. FIG. 16 is a flowchart of a skew-based control process that can be used with the CVT of FIG. 2 or FIG. FIG. 16 is another flowchart of a skew-based control process that can be used with the CVT of FIG. 2 or FIG. 15. FIG. 16 is yet another flowchart of a skew-based control process that can be used with the CVT of FIG. 2 or FIG. 15. 1 is a perspective view of an embodiment of the present invention of a continuously variable transmission (CVT) having a skew-based control system. FIG. It is a cross-sectional perspective view of CVT of FIG. It is sectional drawing of CVT of FIG. FIG. 31 is an exploded cross-sectional perspective view of the CVT of FIG. 30. FIG. 31 is a cross-sectional view of a variator subassembly that can be used with the CVT of FIG. 30. FIG. 35 is an exploded cross-sectional perspective view of the variator subassembly of FIG. 34. FIG. 35 is an exploded perspective view of an embodiment of a traction planet assembly that can be used with the variator subassembly of FIG. FIG. 37 is a cross-sectional view of the traction planet assembly of FIG. 36. FIG. 35 is a perspective view of an embodiment of the present invention of a carrier insert that can be used with the variator subassembly of FIG. FIG. 35 is a perspective view of a carrier member that can be used with the variator subassembly of FIG. FIG. 40 is a cross-sectional perspective view of the carrier member of FIG. 39. FIG. 31 is a perspective view of an embodiment of a skew driver that can be used with the CVT of FIG. 30. FIG. 42 is a cross-sectional view BB of the skew driver of FIG. 41. 1 is a schematic diagram of an embodiment of the present invention of a continuously variable transmission (CVT) having a skew-based control system. FIG. FIG. 6 is a schematic diagram of another inventive embodiment of a continuously variable transmission (CVT) having a skew-based control system. It is sectional drawing of embodiment of a variator. FIG. 46 is a partial cross-sectional perspective view of a traction solar assembly that can be used with the variator of FIG. 45. FIG. 47 is a cross-sectional view of the traction solar assembly of FIG. 46. FIG. 47 is a cross-sectional detail view C of the traction solar assembly of FIG. 46. FIG. 31 is a cross-sectional view of several components of a variator that can be used with the CVT of FIGS. 2, 15 and / or 30. FIG. 31 is a cross-sectional view of another embodiment of a carrier member that can be used with the CVT of FIGS. 2, 15 and / or 30. It is sectional drawing CC of the carrier member of FIG. FIG. 31 is a cross-sectional view of another embodiment of a carrier member that can be used with the CVT of FIGS. 2, 15 and / or 30.

  A preferred embodiment will now be described with reference to the accompanying drawings. Like numbers refer to like elements throughout the drawings. The terminology used in the following description is used in connection with a detailed description of some given embodiments of the invention and should not be construed as merely limiting or limiting. Furthermore, embodiments of the present invention may include several novel features, one of which is essential for practicing the described invention, even though it alone provides its desirable attributes. That's not true. Some CVT embodiments described herein are generally described in US Pat. Nos. 6,241,636, 6,419,608, 6,689,012, No. 7,011,600, No. 7,166,052, U.S. Patent Application No. 11 / 243,484, No. 11 / 543,311, No. 12 / 198,402 and PCT / US2007 / 023315, PCT / IB2006 / 054911, PCT / US2008 / 06929, PCT / US2007 / 023315 and PCT / US2008 / 074396. Related to the type. The entire disclosures of these patents and patent applications are hereby incorporated by reference.

  As used herein, “operably connected”, “operably coupled”, “operably coupled”, “operably connected”, “operably coupled” , “Operably linked” and the like are relationships between elements (mechanical) in which the operation of one element results in a corresponding, subsequent or simultaneous operation or actuation of a second element. , Link, bond, etc.). In describing the embodiments of the invention using the terminology, it should be noted that certain structures or mechanisms that connect or couple elements are generally described. However, unless specified otherwise, when one of the terms is used, it indicates that the actual connection or coupling may take a variety of forms, which may be related to the related art. It will be readily apparent to those skilled in the art.

  For purposes of explanation, the term “axial” as used herein refers to a direction or position along an axis parallel to the main shaft or longitudinal axis of the transmission or variator. As used herein, the term “radial” is used to indicate a direction or position perpendicular to the longitudinal axis of the transmission or variator. For clarity and brevity, similar components (eg, bearing 152A and bearing 152B) that are similarly labeled may be collectively referred to by a single label (eg, bearing 152).

  Reference herein to “traction” does not preclude applications where the main or exclusive mode of the power transmission system is due to “friction”. In general, these can be understood as different forms of the power transmission system without attempting to clarify the classification differences between traction drives and friction drives. A traction drive typically involves transmitting force between two elements by shear forces in a thin fluid layer trapped between the elements. The fluids used in these applications typically exhibit a traction coefficient that is greater than conventional mineral oil. The traction coefficient (μ) represents the maximum available traction force that can be used at the intermediate surface of the contacting component and is a measure of the maximum available drive torque. Generally, friction drive generally relates to transmitting power between two elements by the friction force between the elements. For the purposes of this disclosure, it should be understood that the CVT described herein can operate in both traction and friction applications. For example, in embodiments where the CVT is used in a bicycle application, the CVT may operate as a friction drive or a traction drive depending on the torque and speed conditions present during operation. .

  Embodiments of the present invention disclosed herein generally relate to variator and / or CVT control using a spherical planet so that each of the planets achieves a desired ratio of input speed to output speed during operation. It has a tiltable axis of rotation that can be adjusted. In some embodiments, the adjustment of the rotational axis includes an angular displacement of the planetary axis on the first surface to achieve angular adjustment of the planetary axis on the second surface, wherein the second surface is substantially Thus, it is perpendicular to the first surface. The angular displacement in the first surface is referred to herein as “skew”, “skew angle” and / or “skew state”. For illustrative purposes, the first surface is generally parallel to the longitudinal axis of the variator and / or CVT. The second surface can be generally perpendicular to the longitudinal axis. In one embodiment, the control system adjusts the use of the skew angle to generate a force that substantially tilts the axis of rotation of the planet in the second plane between several contacting components in the variator. . The speed ratio of the variator is adjusted by the inclination of the rotation axis of the planet. The skew angle or skew state described above can be applied, for example, in a plane that is substantially perpendicular to the page plane of FIG. Several transmission embodiments employing the skew control system of the present invention to obtain the desired speed ratio of the variator are described.

  One aspect of the torque / speed adjusting device disclosed herein relates to a drive system in which a prime mover drives various driven devices. The prime mover can be, for example, an electric motor and / or an internal combustion engine. For purposes of explanation herein, an accessory includes any machine or device that can be powered by a prime mover. For purposes of illustration and not limitation, the machine or device may be a power take off device (PTO), a pump, a compressor, a generator, an auxiliary motor, and the like. Auxiliaries configured to be driven by prime movers are also powered by alternators, water pumps, power steering pumps, fuel pumps, oil pumps, air conditioning compressors, cooling fans, superchargers, turbochargers, and usually automotive engines. Any other device that supplies can also be included. As mentioned above, the speed of the prime mover typically changes as the speed or power requirements change, but in many cases the accessories operate optimally at a given substantially constant speed. The embodiments of the torque / speed regulator disclosed herein can be used to control the speed of power supplied to accessories that the prime mover supplies power to.

  For example, in some embodiments, the speed regulator disclosed herein can be used to control the speed of automotive accessories driven by pulleys attached to the crankshaft of an automobile engine. In general, the accessories must function properly both when the engine is idling at low speed and when the engine is operating at high speed. Auxiliaries operate optimally at one speed, but often reduce efficiency at other speeds. In addition, accessory designs are compromised by the need to function over a wide speed range rather than an optimized narrow speed range. In many cases, when the engine operates at a non-low speed, the accessory consumes excessive power, thereby reducing the fuel economy of the vehicle. The power exhaust provided by the accessories also reduces the ability of the engine to power the vehicle, sometimes requiring a larger engine.

  In other situations, the speed and / or torque supplied to the accessories to achieve optimal system performance using the present embodiment of the torque / speed regulator disclosed herein. Can be reduced or increased. In some situations, the present embodiment of the torque / speed regulator disclosed herein may be used to increase the speed relative to the accessories when the prime mover operates at low speed and to compensate when the prime mover operates at high speed. You can reduce the speed of the machine. Therefore, by operating the accessories at one substantially preferred speed, the design and operation of the accessories can be optimized, and the accessories are required to provide sufficient performance at low speeds. There is no need to make it larger. When the prime mover operates at high speed, the torque / speed regulator can reduce the speed on the accessories and reduce the stress load that the accessories must endure at high rpm, thus making the accessories smaller It is also possible to do. Since the accessories are not exposed at high speed, their expected useful life can be substantially increased. In some cases, accessories do not need to operate at low or high speeds, resulting in smoother vehicle operation. Furthermore, since the accessory operates at a lower speed, the vehicle can operate more quietly at high speeds.

  The torque / speed regulator disclosed herein can facilitate the reduction of the size and weight of the prime mover along with the accessories, thereby reducing the weight of the vehicle and thus improving fuel economy. Further, in some cases, the choice of using smaller accessories and smaller prime movers reduces the cost of these components and the vehicle. By making the accessories small and the prime mover small, it is possible to provide flexibility in packaging, and the size of the system can be reduced. The torque / speed regulator embodiments described herein improve fuel economy by allowing accessories to operate at their most efficient speed over the prime mover operating range. Is also possible. Finally, the torque / speed regulator improves fuel economy by preventing the accessories from consuming excessive power at any non-low speed.

  Referring now to FIGS. 1 and 2, in one embodiment, an auxiliary drive continuously variable transmission (CVAD) 10 may include a continuously variable transmission (CVT) 12 coupled to an alternator / generator 14. it can. In one embodiment, the alternator / generator 14 includes C.I. E. It can be a Niehoff 1224-3 alternator. In one embodiment, the CVT 12 may be provided with a skew actuator 16 and a set of speed sensors 18 that are configured to communicate with a skew-based control system (eg, FIGS. 25-29). The CVT 12 may be provided with a lubricant manifold 20 and a lubricant sump 22 that are adapted to couple to a lubrication and cooling system (not shown). In one embodiment, a pulley cover 23 may be disposed between the CVT 12 and the alternator / generator 14. The pulley cover 23 can in particular allow a structural attachment of the CVT 12 to the alternator / generator 14. The pulley cover 23 is adapted to radially surround the drive pulley 24. The drive pulley 24 is configured to receive power input from, for example, a belt (not shown). In some embodiments, the pulley cover 23 is adapted to allow access to the pulley relative to the belt.

  Referring now to FIGS. 3 and 4, in one embodiment, the CVT 12 has a housing 26 that is adapted to couple to a housing cap 28. Housing 26 and housing cap 28 are configured to operably couple to and substantially surround variator subassembly 30. The variator subassembly 30 is coupled to the first traction ring 32 and the second traction ring 34. The first traction ring 32 is coupled to the first load cam roller assembly 36. The second traction ring 34 can be coupled to a second load cam roller assembly 38. In one embodiment, the first load cam roller assembly 36 is coupled to the input cam driver 40. A second load cam roller assembly 38 can be coupled to the output driver 42. In one embodiment, the input cam driver 40 is coupled to the drive pulley 24. Each of the load cam roller assemblies 36 and 38 can be provided with a toothed and / or notched perimeter, which can be located proximate to each of the speed sensors 18. The variator subassembly 30 can be operatively coupled to the skew actuator 16 via a U-shaped member 43.

  In one embodiment, the CVT 12 may be provided with a main shaft 44 that is substantially aligned with the longitudinal axis of the CVT 12. The main shaft 44 can be provided with a keyed hole 45 that can be adapted to receive, for example, the shaft of the alternator / generator 14. The drive pulley 24 can be supported radially by the first bearing 46 and the second bearing 48 at one end of the main shaft 44. In some embodiments, a shim 50 can be placed between the bearings 46 and 48. In one embodiment, the CVT 12 is provided with a thrust bearing 52 coupled to the main shaft 44. A thrust bearing 52 can be coupled to the pulley 24. Thrust bearing 52 can be adapted to provide axial support for some components of CVT 12 and to react to axial forces therefrom. The first bearing 46 and the second bearing 48 and the shim 50 can be configured to share a portion of the axial load provided to the thrust bearing 52. By sharing the axial load, in particular, the life of the thrust bearing 52 can be extended, and overload of the thrust bearing 52 can be prevented.

  In one embodiment, the variator subassembly 30 is provided with a plurality of traction planet assemblies 54 arranged at an angle around the main shaft 44. The variator subassembly 40 may have a traction sun assembly 56 that is coaxially disposed about the main shaft 44. A traction sun assembly 56 may be configured to be operably coupled to each of the traction planet assemblies 54. A traction sun assembly 56 may be disposed radially inward of each of the traction planet assemblies 54. In some embodiments, the traction sun assembly 56 is adapted to move axially along the main shaft 44. In one embodiment, the variator subassembly 30 can have a first carrier member 58 that is operably coupled to the second carrier member 60. The first carrier member 58 and the second carrier member 60 are adapted to support each of the traction planet assemblies 54. In one embodiment, the first carrier member 58 can be coupled to the first carrier member cap 62. The second carrier member 60 can be coupled to the second carrier member cap 64. Carrier member caps 62 and 64 can be configured to operably couple to traction planet assembly 54. The carrier member caps 62, 64 can be configured to counteract the forces generated during the CVT 12 shift.

  In some embodiments, the carrier member caps 62, 64 are integrated with the carrier members 58, 60, respectively. In other embodiments, the carrier member caps 62, 64 are rigidly and permanently attached to the carrier members 58, 60. In one embodiment, the carrier member caps 62, 64 are separate components from the carrier members 58, 60, thereby allowing different materials to be used for those components. For example, the carrier member 58 can be made from aluminum and the carrier member cap 62 can be made from steel. The carrier member cap 62 may also facilitate assembly of the traction planet assembly 54 with the carrier member 58 as a separate component. In some embodiments, the carrier member cap 62 can be configured as a separate component to simplify the manufacture of the first carrier member 58 and the second carrier member 60.

  Referring to FIG. 5, in one embodiment, the variator subassembly 30 has a carrier retaining ring 66 that is adapted to couple to a first carrier member 58 and a second carrier member 60. The carrier retaining ring 66 can be coupled to the housing 26 and configured to be substantially non-rotatable with respect to the longitudinal axis of the CVT 12. In one embodiment, each of the traction planet assemblies 54 has at least one leg 68 operably coupled to the planet shaft 70. Each of the legs 68 is adapted to operably couple to the traction sun assembly 56. In one embodiment, the traction sun assembly 56 has a plurality of anti-rotation inserts 72. The anti-rotation insert 72 can be configured to be located substantially on each side of the leg 68. An anti-rotation insert 72 can be coupled to the first shift cam 74. In some embodiments, the anti-rotation insert 72 can be coupled to the second shift cam 76. In still other embodiments, the anti-rotation insert 72 can be coupled to both the first shift cam 74 and the second shift cam 76. Anti-rotation insert 72 can substantially prevent shift cams 74 and 76 from rotating during operation of CVT 12.

  During operation of the CVT 12, a power input can be coupled to the drive pulley 24, for example, by a belt or chain (not shown). The drive pulley 24 transmits power input to the input cam driver 40, and the input cam driver 40 transmits power to the first traction ring 32 via the first load cam roller assembly 36. The first traction ring 32 transmits power to each of the traction planet assemblies 54. Each of the traction planet assemblies 54 supplies power to the second traction ring 34, and the second traction ring 34 transmits power to the output cam driver 42 via the second load cam roller assembly 38. In one embodiment, the output driver 42 provides power to the main shaft 44. The main shaft 44 can be coupled to the alternator / generator 14 via, for example, a keyed hole 45. The shift in the ratio of input speed to output speed, and thus the ratio of input torque to output torque, is achieved by tilting the rotational axis of the traction planet assembly 54 to a tilt angle, sometimes referred to herein as gamma (γ). Achieved. The inclination of the rotation axis of the traction planet assembly 54 substantially occurs, for example, in the page plane of FIG. Tilt of the rotational axis of the traction planet assembly 54 can be achieved by rotating the second carrier member 60 relative to the first carrier member 58 about the longitudinal axis. This relative angular rotational displacement is sometimes referred to herein as β. The rotation of the second carrier member 60 relative to the first carrier member 58 provides each of the traction planet assemblies 54 with a skew angle, or state that may be referred to herein as a “skew state”. The skew angle can be applied in a plane that is substantially parallel to the longitudinal axis of the CVT 12 (eg, a plane that is perpendicular to the page plane of FIG. 4). In one embodiment, the skew angle may range from 0 degrees to 15 degrees. Usually, the skew angle is in the range of 0 to 8 degrees.

  Referring now to FIG. 6, in one embodiment, the input cam driver 40 is coupled to the drive pulley 24. The input cam driver 40 can be provided with a plurality of roller reaction surfaces 78 that can be adapted to operably couple to the first load cam roller assembly 36. The main shaft 44 may be provided with a central lubricating oil passage 80, which supplies lubricating oil to the plurality of lubricating oil distribution passages 82A, 82B, 82C. The lubricating oil distribution passages 82A, 82B, and 82C intersect the central lubricating oil passage 80 and extend radially outward from the center of the main shaft 44. In one embodiment, the main shaft 44 can be provided with a spline portion 84 that is configured to couple to the output cam driver 42. A shoulder 86 may be provided proximate one end of the spline portion 84 of the main shaft 44. A groove 88 can be provided at the opposite end of the spline portion 84 of the main shaft 44. In some embodiments, a screw hole 90 is provided at one end of the main shaft. During assembly of the CVT 12, the variator subassembly 30 is disposed coaxially with the main shaft 44. An assembly tool (not shown) is coupled to the screw hole 90. The assembly tool is screwed into the bore 90 and applies force to the output ring 42 to facilitate tightening the output ring 42 and input ring 40 to a predetermined axial force. By placing at least one clip 92 (FIGS. 3 and 4) in the groove 88, the axial preload setting can be maintained when the assembly tool is removed. In some embodiments, a shim (not shown) can be placed in the groove 88 along with the clip 92 to maintain the axial preload setting.

  Turning now to FIG. 7, in one embodiment, the first carrier member 58 is adapted to couple to the second carrier member 60 via a stepped bolt 94. A stepped bolt 94 can be configured to couple to the carrier retaining ring 66. In one embodiment, a shim 96 can be placed under the head of the stepped bolt 94. The thickness of the shim 96 can be selected to adjust the axial force and / or axial clearance between the first carrier member 58 and the second carrier member 60 when the stepped bolt 94 is tightened. . In one embodiment, it is desirable for the axial force between the first carrier member 58 and the second carrier member 60 to be minimal, so that the second carrier member 60 is connected to the first carrier member 58 and the second carrier. It can rotate relative to the first carrier member 58 about the longitudinal axis with minimal axial displacement or play with the member 60. In some embodiments, the carrier retaining ring 66 is coupled to the housing 26 and is substantially non-rotatable about the longitudinal axis. In other embodiments, a thrust bearing (not shown) may be provided between the first carrier member 58 and the second carrier member 60.

  Referring now to FIG. 8, in one embodiment, the carrier retaining ring 66 is a substantially annular ring with a reaction surface 98 formed on the inner periphery. A flange 100 can be provided on the outer periphery of the substantially annular ring of the carrier retaining ring 66. The flange 100 can be configured to couple to the housing 26, for example. In one embodiment, the opening 102 is disposed substantially between the reaction surface 98 of the carrier retaining ring 66 and the flange 100. In some embodiments, the reaction surface 98 is formed with a plurality of fastening holes 104 that are adapted to receive stepped bolts 94. The flange 100 can be provided with a fastening hole 106 that can be configured to secure the carrier retaining ring 66 to the housing 24.

  Turning now to FIG. 9, in one embodiment, the U-shaped member 43 can be provided with at least one fork 110. The fork 110 extends from the base 112. A set screw land 114 can be provided on the base 112. The U-shaped member 43 can be coupled to the carrier member 58 or the second carrier member 60. In one embodiment, the base 112 is attached to one of the first carrier member 58 or the second carrier member 60 by, for example, a set screw (not shown). The fork 110 can be arranged to extend through the opening 110. By coupling the actuator 16 to the fork 110 during operation of the CVT 12, changing the ratio of the CVT 12 can be facilitated. In one embodiment, changing the ratio of CVT 12 is accomplished by rotating second carrier member 60 relative to first carrier member 58. In some embodiments, changing the ratio of CVT 12 is accomplished by rotating first carrier member 58 relative to second carrier member 60.

  Referring now to FIG. 10, in one embodiment, the carrier member 58 can be a substantially bowl-like body having a flange 120. The plurality of support fingers 122 extend radially inward from the flange 120, whereby a bowl-shaped space can be formed. The reaction surface 124 is located on the side of each finger 122 on both sides thereof. It is also possible to provide a fastening hole 126 in each finger part. The fastening holes 126 can facilitate the coupling of the first carrier member cap 62 to the carrier member 58. In one embodiment, the flange 120 has a plurality of holes 128 and grooves 130. In some embodiments, the holes 128 and grooves 130 can be positioned around the flange 120 such that the grooves 130 are located on the sides of each hole 128 and vice versa. In one embodiment, carrier member 58 and carrier member 60 are substantially similar. When assembled, the holes 128 in the carrier member 58 can be aligned with the grooves 130 in the carrier member 60, and vice versa. A notch 132 can be provided in the flange 120. The notch 132 can be adapted to couple to the U-shaped member 43. A set screw hole 134 can be provided in the flange 120, which is arranged to intersect the notch 132 and the outer periphery of the flange 120. The set screw hole 134 can facilitate coupling of the U-shaped member 43 to the carrier member 58 by, for example, a set screw (not shown). The carrier member 58 can have a plurality of gap openings 140. In one embodiment, the gap opening 140 is configured to cooperate with each of the traction planet assemblies 54.

  Referring now to FIGS. 11-12B, in one embodiment, the traction planet assembly 54 has a substantially spherical traction planet 150 having a central hole. Traction planet 150 can be operably coupled to planet shaft 70 by bearing 152. In some embodiments, the spacer 154 can be operably coupled to the planet shaft 70 and disposed between the bearings 152. Each end of the planetary shaft 70 can be coupled to the leg 68. A skew reaction roller 156 can be operatively coupled to each of the planet shafts 70. A shift reaction ball 158 can be pushed into a hole 160 formed at each end of the planetary shaft 70. A shift cam roller 162 can be operatively coupled to each leg 68. A shift cam roller 162 can be coupled to the shift cam roller shaft 164. The shift cam roller shaft 164 can be coupled to a shift cam roller shaft hole 166 formed in the leg portion 68. The shift cam roller 162 can be disposed in a groove 168 formed at one end of the leg portion 68. In one embodiment, the groove 168 is substantially perpendicular to the shift cam roller shaft hole 166. A planetary shaft hole 170 can be provided in the leg portion 68. A planetary shaft hole 170 can be formed at the end of the leg 68 opposite the end of the groove 166. A skew reaction roller gap shoulder 172 can be provided on the leg 68. The leg 68 can have a side 174 with an angular taper when viewed in the page plane of FIG. 12B. In one embodiment, side 174 has an angle 176 in the range of about 5 degrees to 10 degrees with respect to the vertical plane.

  Referring now to FIGS. 13 and 14, in one embodiment, the traction sun assembly 56 has a traction sun 180 operably coupled to the first shift cam 74 and the second shift cam 76. Shift cams 74 and 76 can be positioned to be substantially located on the sides of traction sun 180. In one embodiment, shift cams 74 and 76 are substantially similar. The traction sun assembly 56 can have a set of bearings 184. Each bearing 184 can be coupled to a bearing race 186. The bearing race 186 is configured to couple to a shoulder 188 formed on the inner diameter of the traction sun 180. In one embodiment, the bearing race 186 is coupled to the spring 190. Spring 190 can facilitate axial preloading of bearing race 186, thereby applying an axial preloading force to bearing 184 and shift cams 74 and 76. A bearing 192 may be provided on the traction sun assembly 56. The bearing 192 can be adapted to facilitate coupling of the traction sun assembly 56 to the main shaft 44. In one embodiment, the traction sun assembly has a plurality of anti-rotation spacers 194. Each anti-rotation spacer 194 can be coupled to the shift cam 182. In one embodiment, shift cams 74 and 76 are provided with a plurality of seats 196 that are configured to couple to anti-rotation spacers 194. Each rotation prevention spacer 194 is provided with a hole 198. Each seat 196 is provided with a hole 200. Holes 198 and 200 are adapted to facilitate coupling of anti-rotation insert 194 to shift cam 74. In one embodiment, the shift cam 74 can be a generally disk-like body with a shoulder 202 extending from one end. A bearing race 204 can be formed on the shoulder 202. The bearing race 204 can be adapted to couple to the bearing 184. In some embodiments, the cam surface 206 can be provided on the shift cam 74. The cam surface 206 can have a substantially curved profile when viewed in cross section in the plane of FIG.

  Turning now to FIG. 15, in one embodiment, the CVT 1000 can have a housing 1002 coupled to a housing cap 1004. Housing 1002 and housing cap 1004 can be configured to operably couple to and substantially surround variator subassembly 1006. A variator subassembly 1006 can be coupled to the first traction ring 1008 and the second traction ring 1010. A first traction ring 1008 can be coupled to the first load cam roller assembly 1012. A second traction ring 1010 can be coupled to the second load cam roller assembly 1014. In one embodiment, the first load cam roller assembly 1012 is coupled to the input cam driver 1016. A second load cam roller assembly 1014 can be coupled to the output driver 1018. In one embodiment, the input cam driver 1016 can be coupled to the drive pulley 24. Each of the load cam roller assemblies 1012 and 1014 can be provided with a toothed and / or notched perimeter that can be configured proximate to the speed sensor 18. The variator subassembly 1006 can be operably coupled to the skew actuator 16 by a U-shaped member 43 (FIG. 3). In one embodiment, the CVT 1000 can be provided with a main shaft 1020 that is substantially aligned with the longitudinal axis 1022 of the CVT 1000. The main shaft 1020 can be provided with a keyed hole 1025, which can be adapted to receive, for example, the shaft of the alternator / generator 14 or any other accessory. A drive pulley 24 can be operably coupled to the main shaft 1020. In one embodiment, the coupling of drive pulley 24 to main shaft 1020 is substantially similar to the coupling of drive pulley 24 to main shaft 44.

  Referring to FIGS. 15-18, in one embodiment, the variator subassembly 1006 can have a plurality of traction planet assemblies 1024 arranged at an angle about the longitudinal axis 1022. The variator subassembly 1006 can include a traction sun assembly 1026 that is coaxially disposed about the main shaft 1020. A traction sun assembly 1026 may be positioned radially inward of each of the traction planet assemblies 1024. In one embodiment, the traction sun assembly 1026 can be adapted to be substantially axially fixed along the main shaft 1020. In one embodiment, the variator subassembly 1006 can have a first carrier member 1028 operably coupled to a second carrier member 1030. First carrier member 1028 and second carrier member 1030 are configured to support each of traction planet assemblies 1024.

  In one embodiment, the first carrier member 1028 is coupled to the first carrier member cap 1032. The second carrier member 1030 can be coupled to the second carrier member cap 1034. Carrier member caps 1032, 1034 are adapted to operably couple to traction planet assembly 1024. In one embodiment, the variator subassembly 1006 can have a carrier retaining ring 1036. The carrier retaining ring 1036 can be configured to couple to the first carrier member 1028 and the second carrier member 1030. A flange 1038 can be provided on the carrier retaining ring 1036. Flange 1038 can be coupled to housing 1002 and can be configured to be substantially non-rotatable with respect to longitudinal axis 1022. An opening 1040 can be provided in the carrier retaining ring 1036 through which the U-shaped member 43 can be arranged to couple, for example, to the second carrier member 1030. A plurality of stepped bolts 1042 can be provided to operably couple the first carrier member 1028 and the second carrier member 1030 to the carrier retaining ring 1036. The coupling of the first carrier member 1028 and the second carrier member 1030 to the carrier retaining ring 1036 is substantially similar to the coupling of the first carrier member 58 and the second carrier member 60 to the carrier retaining ring 66 (FIG. 7). Can be configured.

  During operation of the CVT 100, the power input can be coupled to the drive pulley 24, for example, by a belt or chain (not shown). The drive pulley 24 can transmit power input to the input cam driver 1016. The input cam driver 1016 can transmit power to the first traction ring 1008 via the first load cam roller assembly 1012. The first traction ring 1008 transmits power to each of the traction planet assemblies 1024. Each of the traction planet assemblies 1024 powers the second traction ring 1010. The second traction ring 1010 supplies power to the output driver 1018. The output driver 1018 is configured to supply power to the main shaft 1020 so that power can be transmitted out of the CVT 100. A shift in the ratio of input speed to output speed, and thus the ratio of input torque to output torque, can be achieved by tilting the rotational axis of the traction planet assembly 1024 to a tilt angle (γ). Inclination of the rotational axis of the traction planet assembly 1024 can be facilitated by rotating the first carrier member 1028 relative to the second carrier member 130. US patent application Ser. No. 12 / 198,402 filed Aug. 26, 2008, the disclosure of which is incorporated herein by reference in its entirety by rotation of the first carrier member 1028 relative to the second carrier member 1030. A skew condition of the type generally described in 1) occurs. Skew conditions can be applied to the traction planet assembly 1024 by two events that occur separately or in combination. One event is a change in each degree of rotation (β) of the carrier member 1028 and the other event is a change in the tilt angle (γ) of the traction planet assembly 1024. As the rotational axis of the traction planet assembly 1024 tilts for a constant angular rotation (β) of the carrier member 1028, the skew state can approach a zero skew angle state. The axis of rotation of the traction planet assembly 1024 can stop tilting when a zero skew condition is reached. The zero skew state is an equilibrium state with respect to the tilt angle (γ).

  With further reference to FIGS. 15-18, in one embodiment, the traction sun assembly 1026 can have a traction sun 1044 operably coupled to the first and second traction sun supports 1046, eg, by bearings. . The traction sun support 1046 can be adapted to contact the first carrier member 1028 and the second carrier member 1030. First carrier member 1028 and second carrier member 1030 may constrain and / or limit axial movement of traction sun assembly 1044. In one embodiment, the traction sun support 1046 can be coupled to a wave spring (not shown) disposed between the traction sun support 1046 and the first carrier member 1028 and the second carrier member 1030. The wave spring can be energized during operation of the CVT 1000 to provide minimal axial movement to the traction solar assembly 1026. In some embodiments, the traction sun support 1046 is coupled to the first carrier member 1028 and the second carrier member 1030 via screw leads (not shown), whereby the first carrier member 1029 or the second carrier member. Any rotation of 1030 tends to displace the traction sun assembly 1026 in the axial direction. In other embodiments, an actuator (not shown) is coupled to the traction sun assembly 1026 to at least partially based on the tilt angle (γ) of the traction planet assembly 1024 of the CVT 1000 in the axial direction of the traction sun assembly 1026. It is possible to facilitate the change of the position. In yet another embodiment, an actuator (not shown) is coupled to the traction sun assembly 1026 so that the axial direction of the traction sun assembly 1026 is substantially random with respect to the tilt angle (γ) of the traction planet assembly 1024. The position can be easily changed. The above-described method of axially arranging the traction sun assembly 1026 can increase the expected life of the traction sun 1044, for example, by distributing the operating load over a larger area of the surface of the traction sun 1044 that is inherently achievable. Can be long.

  Referring now to FIGS. 19-21C, in one embodiment, the first carrier member 1028 can be provided with a plurality of radial offset grooves 1050. The second carrier member 1030 can be provided with a plurality of radial grooves 1052. The radial grooves 1052 are indicated by broken lines in FIG. The radial offset groove 1050 and the radial groove 1052 are sized to accommodate several components of the traction planet assembly 1024, such as the skew reaction roller 1100 (FIG. 22). For illustrative purposes, the arrangement of the radial offset groove 1050 relative to the radial groove 1052 can be shown as a protrusion in a plane perpendicular to the longitudinal axis 1022. Longitudinal axis 1022 is perpendicular to the page plane of FIG. A radial construction line 1054 can be shown perpendicular to the longitudinal axis 1022. The structural line 1054 passes through the center 1056 of the first carrier member 1028 and the second carrier member 1030 in the radial direction. Similarly, the second structure line 1058 can pass through the center 1056. The structural line 1058 substantially bisects the radial groove 1052. A radial offset structure line 1060 is parallel to the structure line 1054. The radial offset structure line 1060 is perpendicular to the longitudinal axis 1022. The offset distance 1062 separates the radial offset structure line 1060 from the structure line 1054. In one embodiment, the offset distance 1062 ranges from about 5 mm to 20 mm. In some embodiments, the offset distance 1062 is 16-18 mm. In some embodiments, the offset distance 1062 is proportional to the width of the radial offset groove 1050. For example, the offset distance 1062 can be approximately equal to the width of the radial offset groove 1050. The radial male set structure line 1060 substantially bisects the radial offset groove 1050. The radial offset structure line 1060 intersects the second structure line 1058 to form an angle 1064 (sometimes referred to herein as ψ). In one embodiment, the angle (Ψ) 1064 can range from 5 degrees to 45 degrees when the traction planet subassembly 1024 is at a tilt angle (γ) that is substantially equal to zero. Preferably, the angle (Ψ) 1064 is in the range of 10 degrees to 20 degrees when the traction planet subassembly 1024 is at a tilt angle (γ) that is substantially equal to zero.

  Still referring to FIG. 19, in one embodiment, the first carrier member 1028 can be provided with a plurality of gap openings 1066. The second carrier member 1030 can be provided with a plurality of gap openings 1068. The gap openings 1066, 1068 can be adapted to provide a gap for each of the traction planet assemblies 1024. In one embodiment, the clearance opening 1066 is larger than the clearance opening 1068 to provide additional clearance to the traction planet assembly 1024 during operation of the CVT 1000.

  Referring now to FIGS. 20A-20C, in one embodiment, the first carrier member 1028 can be substantially bowl-shaped, which includes a central hole 1027 and a flange 1072 on the outer periphery of the bowl-shaped body. Have. The flange 1072 can be provided with a plurality of holes 1074 and a plurality of grooves 1076. Hole 1074 and groove 1076 allow relative rotational displacement between carrier member 1028 and carrier member 1030 while providing axial constraints to first carrier member 1028 and second carrier member 1030. For example, it can be adapted to facilitate coupling by stepped bolts 1042. The first carrier member 1028 can be provided with a reaction shoulder 1078 disposed about the center hole 1070. In one embodiment, the reaction shoulder 1078 can be configured to contact the traction sun support 1046. A notch 1080 can be provided in the flange 1072. The notch 1080 can be adapted to facilitate the coupling of the first carrier member 1028 to the U-shaped member 43. A plurality of holes 1082 can be disposed on the bottom surface of the bowl-shaped body of the first carrier member 1028. The hole 1082 can be arranged to facilitate coupling of the first carrier member cap 1032 to the first carrier member 1028. In one embodiment, each radial groove 1050 is provided with a reaction surface 1084. Reaction surface 1084 is configured to facilitate coupling of first carrier member 1028 to traction planet assembly 1024.

  With reference to FIGS. 21A-21D, the structure line 1058 may form an angle (Ψ) 1064 with the offset structure line 1060. During operation of the CVT 1000, the carrier members 1028, 1030 can rotate about the longitudinal axis 1022. The offset structure line 1060 follows the first carrier member 1028 and the structure line 1058 follows the second carrier member 1030. For clarity, structural lines 1058 and 1060 are shown in FIGS. 21B-21D for three angular rotational positions, for example about the longitudinal axis of the second carrier member 1030 relative to the first carrier member 1028 (this The relative angular rotational position may be referred to herein as β). As the carrier members 1028, 1030 rotate relative to each other, the angle (Ψ) 1064 can change and the intersection location 1063 can move radially relative to the structural line 1058. For example, the angle 10640 shown in FIG. 21B is smaller than the angle 10661 shown in FIG. 21D. When the tilt angle (γ) is less than zero, an angle 10640 is formed between the structural line 1058 and the structural line 1060. When the tilt angle (γ) is greater than zero, an angle 10642 is formed between the structure line 1058 and the structure line 1060. Depending on the embodiment, the positions of the carrier members 1028 and 1030 in the CVT 1000 may be reversed. Such a reversal can change the relationship embodied in FIG. An intersection location 1063 can be shown at the intersection between the offset structure line 1060 and the structure line 1058. The intersection location 1063 generally corresponds to a skew angle equal to zero, or “zero skew condition”, for a traction planet subassembly 1024 at a constant tilt angle (γ). The magnitude of the change in angle (Ψ) 1064 may indicate the stability of the tilt angle (γ) of the traction planet assembly 1024 during operation. A high value for angle (Ψ) 1064 tends to be more stable, indicating a slower shift than a lower angle, which tends to be less stable and indicates a faster shift.

  Referring now specifically to FIGS. 21E-21H, in one embodiment, the radial offset groove 1051 can have a curved profile that generally follows the structural line 1059. In some embodiments, the carrier member 1028 can be provided with a radial offset groove 1051. The curvature of the structural line 1059, and thus the curvature of the radial offset groove 1051, can be configured to provide the desired control stability and response of the CVT 1000. For illustrative purposes, the structure line 1061 can be shown as touching the structure line 1059 at the intersection location 1065. The intersection location 1065 is generally at the intersection of the structure line 1058 and the structure line 1059. In FIG. 21E, the angle (Ψ) 1064 is shown between the structural line 1058 and the structural line 1061. In some embodiments, the bending of the structural line 1059 causes a constant angle (Ψ) between the structural line 1058 and the structural line 1061 when the carrier member 1028 rotates an angle β relative to the carrier member 1030 about the longitudinal axis. 1064 can be arranged. For clarity, in FIGS. 21F-21H, structural lines 1058, 1059, and 1061 are shown for three angular rotational positions (β). As the carrier members 1028, 1030 rotate relative to each other, the angle (Ψ) 1064 remains constant and the intersection location 1065 can move radially relative to the structural line 1058. In some embodiments, the angle (Ψ) 1064 can arbitrarily vary between the tilt angle (γ) states shown in FIGS. 21F-21H. The change in structure angle 1064 can be selected to optimize the control state of CVT 1000. The resulting path of the structural line 1059 can be formulated using techniques available to those skilled in the relevant art.

  Referring now to FIG. 22, in one embodiment, the traction planet assembly 1024 has a substantially spherical planet 1090 having a central hole. The planet 1090 can be operably coupled to the planet shaft 1092 by, for example, a bearing 1094. In one embodiment, a spacer 1096 can be disposed between the bearings 1094. In some embodiments, the spacer 1096 is integral with the bearing 1094. The bearing 1094 can be held on the planet shaft 1092 by a ring 1098. In some embodiments, the ring 1098 can be integral with the bearing 1094. In one embodiment, the traction planet assembly 1024 can have a skew reaction roller 1100 coupled to each end of the planet shaft 1092. The skew reaction roller 1100 can be held on the planetary shaft 1092 by the collar 1101. In one embodiment, the collar 1101 can be attached to the planet shaft 1092 by press fit or other suitable attachment means. In other embodiments, the collar 1101 can be constrained by carrier caps 1032 and 1034 (FIG. 15). Each end of the planetary shaft 1092 can be adapted to receive a shift reaction ball 1102. In one embodiment, the shift reaction ball 1102 is pushed into a hole 1103 formed at each end of the planetary shaft 1092. In some embodiments, the shift reaction ball 1102 can contact the first carrier member cap 1032 or the second carrier member cap 1034 during operation of the CVT 1000.

  Turning now to FIGS. 23 and 24, in one embodiment, the housing 1002 can be a substantially bowl-like body 1109 that is formed with a flange 1110 at the first end and lubricated at the second end. An oil supply hub 1112 is formed. Flange 1100 can be configured to couple to a support structure, such as pulley cover 23. A lubricating oil passage 1113 may be provided in the lubricating oil supply hub 1112. The lubricant passage 1113 can be adapted to couple to an external pump (not shown). The housing 1002 can be provided with a sensor mounting hub 1114, which is disposed on the outer periphery of the bowl-like body 1009. The sensor mounting hub 1114 can facilitate mounting of the speed sensor 18, for example. Inserting the speed sensor 18 into the access hole 1115 can facilitate positioning the speed sensor 18 in proximity to the load cam roller assembly 1012. In one embodiment, the housing 1002 can have a lubricant reservoir 1116 attached to the outer periphery of the bowl 1009 at the attachment intermediate surface 1117. The lubricating oil reservoir 1116 can be provided with a plurality of fins 1118. The fins 1118 can facilitate the transfer of heat from the lubricant to the ambient air, for example during operation of the CVT 12. The lubricating oil reservoir 1116 can also be provided with a lubricating oil passage 1119. In some embodiments, the lubricant passage 1119 is adapted to couple to an external pump (not shown). In one embodiment, the housing 1002 can be provided with an actuator mounting hub 1120 that is disposed on the outer periphery of the bowl 1009. Actuator mounting hub 1120 can be configured to mount to actuator 16, for example. The actuator mounting hub can be adapted to facilitate coupling of the actuator 16 to, for example, a U-shaped member 43.

  Referring now to FIG. 25, in one embodiment, the skew-based control process 2000 may be implemented with a microprocessor that communicates with the power control circuit hardware of the CVT 1000, for example. In some embodiments, the skew-based control control process 2000 can be implemented with a microprocessor that communicates with the CVT 12 or other CVT embodiments described herein. The skew-based control process 2000 begins at block 2002. The skew-based control process 2000 then proceeds to block 2004 and receives the desired speed ratio (SR) setting for the CVT 1000. In one embodiment, the desired SR setting is received from the user. In some embodiments, the desired SR settings are received from a predetermined map that resides in the memory of the controller (see, eg, FIG. 28A). The skew-based control process 2000 proceeds to block 2006 and determines an angular rotation (β) about the longitudinal axis of the second carrier member 1030 relative to the first carrier member 1028, for example. Next, the skew-based control process 2000 proceeds to the actuator sub-process 2008 and applies angular rotation (β) to the carrier member 1028, for example. When the actuator sub-process 2008 is complete, the skew-based control process 200 proceeds to block 2009 and measures the actual SR of the CVT 1000. In one embodiment, the actual SR of the CVT 1000 can be determined, for example, by measuring the speed of the load cam roller assemblies 1012 and 1014, or any other component that indicates the input and output speeds of the CVT 1000. . In some embodiments, the actual SR can be calculated based at least in part on the target output speed condition, or at least in part on the target input speed condition. In other embodiments, the actual SR of the CVT 1000 can be determined by measuring the tilt angle (γ) of the planetary axis 1092. In yet another embodiment, the actual SR of the CVT 1000 can be determined by measuring the actual torque ratio of the CVT 1000. The actual torque ratio of the CVT 1000 can be determined, for example, by measuring the torque of the traction rings 1008 and 1010, or any other component that indicates input torque and output torque for the CVT 1000. In some embodiments, the torque indicating the input torque and the output torque can be determined by measuring the torques that react against each of the first carrier member 1028 and the second carrier member 1030. Next, the skew-based control process 2000 proceeds to decision block 2010 and forms a comparison value by comparing the measured speed ratio with a desired speed ratio setting. If the measured speed ratio is not equal to the desired speed ratio setting, the skew-based control process 2000 returns to block 2006. If the measured speed ratio is equal to the desired speed ratio setting, the skew-based control process 2000 proceeds to end block 2012. The skew-based control process 2000 remains at the end block 2012 until a new speed ratio setting is received. In some embodiments, the skew-based control process 2000 is configured to operate in an open loop manner, in which case blocks 2009 and 2010 are not included in the skew-based control process 2000.

Referring to FIG. 26, in one embodiment, block 2006 can use a lookup table that can be represented by curve 2007. Curve 2007 shows an exemplary relationship between angular rotation (β) and a desired speed ratio of, for example, CVT1000. Block 2006 may use curve 2007 during the open loop operation of skew-based control process 2000. Curve 2007 can be represented by the equation y = Ax ² −Bx + C where y is the angular rotation (β) and x is the speed ratio. In one embodiment, the values of A, B and C are 0.5962, 4.1645 and 3.536, respectively. In some embodiments, the values of A, B, and C are 0.5304, 4.0838, and 3.507, respectively. In other embodiments, the values of A, B, and C may be the dimensions and shape of CVT 1000, in particular, for example, the location of grooves 1050 and 1052 on carrier members 1028 and 1030, the length of planetary shaft 1092, and traction ring 1008 and Related to 1010 dimensions. In one embodiment, block 2006 may be configured to include a known PID control process suitable for closed-loop operation of skew-based control system 2000. In a closed loop configuration, block 2006 determines the angular rotation (β) based at least in part on a comparison of the actual SR and the SR setpoint (sometimes referred to herein as an error).

  Referring to FIG. 27, in one embodiment, the actuator sub-process 2008 begins at block 2014 and proceeds to block 2015 where a setpoint for angular rotation (β) is received. The actuator sub-process 2008 proceeds to block 2016 and determines an actuator command signal based at least in part on the angular rotation (β). In one embodiment, a look-up table can be used to convert angular rotation (β) setpoints into actuator command signals. In some embodiments, the actuator command signal can be a voltage or a current. In other embodiments, the actuator command signal may be a change in the position of the cable or linkage. In some embodiments, an algorithm can be used to derive an actuator command signal from an angular rotation (β) setpoint. The actuator sub-process 2008 then proceeds to block 2017 and sends an actuator command signal to the actuator and associated hardware. In one embodiment, a standard serial communication protocol can be used to send command signals to the actuator hardware. In some embodiments, a cable or link mechanism can be used to send command signals to the actuator hardware. Actuator subprocess 2008 then proceeds to block 2018 and rotates the carrier member, eg, carrier member 1028. Next, the actuator sub-process 2008 proceeds to block 2019 and measures the angular rotation (β). The actuator sub-process 2008 then proceeds to decision block 2020 and compares the measured angular rotation (β) with a set value for the angular rotation (β). If the measured angular rotation (β) is not equal to the angular rotation (β) setpoint, the actuator sub-process 1008 returns to block 2016. If the measured angular rotation (β) is equal to the angular rotation (β) setting, the actuator sub-process 2008 ends at block 2022, and the skew-based control process 2000 continues at block 2009 as described above with respect to FIG. be able to. In some embodiments, the actuator sub-process 2008 is configured to operate in an open loop manner, and in such cases, blocks 2019 and 2020 are not included in the sub-process 2008.

  Turning now to FIG. 28A, in one embodiment, the control system 2050 can be configured to control the CVT 2051 coupled to the prime mover 2052 and the load 2053. The CVT 2051 can be configured to accommodate a skew-based control system. In some embodiments, CVT 2051 is substantially similar to CVT 12 and / or CVT 1000. CVT 2051 can be coupled to skew actuator 2054. In one embodiment, the skew actuator 2054 may be substantially similar to the skew actuator 16, for example. In some embodiments, the skew actuator 2054 is a servo actuator. In other embodiments, the skew actuator 2054 can be a mechanical lever (not shown). In still other embodiments, the skew actuator 2054 can be a hydraulic actuator or an electrohydraulic actuator (not shown). The control system 2050 can include a plurality of sensors 2055 that are in electrical and / or mechanical communication with the CVT 2051, the control module 2056, and the skew control module 2057. In some embodiments, sensor 2055 can communicate with prime mover 2052, load 2053, and / or actuator 2054. Sensor 2055 communicates with control module 2056. In one embodiment, control module 2056 communicates with skew actuator 2054. The control module 2056 can be configured to communicate with the skew control module 2057. In one embodiment, the skew control module 2057 is configured to perform a skew-based control process 2000. In some embodiments, the control module 2056 communicates with a data display module 2058 that is configured to provide a user control interface using one or more displays and / or input devices (not shown).

  Those skilled in the art will understand the various exemplary logic blocks, modules, circuits and algorithm steps described in connection with the embodiments disclosed herein, including references to control system 2050, electronic hardware, computer It will be understood that the software can be implemented as software stored on a readable medium and executable by a processor, or a combination of both. To clearly illustrate this hardware and software interchangeability, various illustrative components, blocks, modules, circuits, and steps have been described above generally in terms of their functionality. Whether such functionality is implemented as hardware or software depends upon the particular application and design constraints imposed on the overall system. Those skilled in the art can implement the described functionality in different ways for each particular application, but such implementation decisions should not be construed as causing a departure from the scope of the invention. For example, the various exemplary logic blocks, modules and circuits described in connection with the embodiments disclosed herein can be general purpose processors, digital signal processors (DSPs), application specific integrated circuits (ASICs), field programmable. Implement or execute a gate array (FPGA) or other programmable logic device, discrete gate or transistor logic, discrete hardware components, or any combination thereof designed to perform the functions described herein. be able to. A general purpose processor may be a microprocessor, but in the alternative, it may be any conventional processor, controller, microcontroller, or state machine. The processor may also be implemented as a combination of computing devices, such as a combination of DSP and microprocessor, multiple microprocessors, one or more microprocessors with a DSP core, or any other such configuration. The software associated with such modules may be RAM memory, flash memory, ROM memory, EPROM memory, EEPROM memory, registers, hard disk, removable disk, CD-ROM, or any other suitable form known in the art. It can exist on a storage medium. An exemplary storage medium is coupled to the processor such that the processor can read information from, and write information to, the storage medium. In the alternative, the storage medium may be integral to the processor. The processor and the storage medium can reside in an ASIC. For example, in one embodiment, the control module 2056 includes a processor (not shown). The processor of the control module 2056 may be configured to perform the functions described herein with respect to one or both of the skew control module 2057 and the data display module 2058.

  Referring to FIG. 28B, in one embodiment, the skew actuator 2054 can have a hydraulic piston 2060 in communication with the hydraulic control valve 2061. The hydraulic piston 2060 can be coupled to the U-shaped member 43, for example. The hydraulic control valve 2061 can provide pressure to the ports 2062 and 2063, which can facilitate movement of the hydraulic piston 2060, thereby moving the U-shaped member 43. The skew actuator 2054 can have a pump 2064 in fluid communication with the reservoir 2065. Pump 2064 can supply pressurized control fluid to pressure relief valve 2066 and accumulator 2067, which are adapted to supply pressure control fluid to hydraulic control valve 2061. In some embodiments, the hydraulic control valve 2061 is a four-way control valve that can communicate with the spool actuator 2068. The spool actuator 2068 can be configured to adjust the hydraulic control valve 2061 based at least in part on, for example, a desired skew state of the CVT 1000. In one embodiment, the spool actuator 2068 can be an electronic servo actuator (not shown). In some embodiments, the spool actuator 2068 can be a manual lever (not shown). In other embodiments, the hydraulic control valve 2061 can be provided with a movable housing that facilitates adjustment of the port 2069 relative to an internal spool (not shown). The movable housing may be configured to compensate for steady state errors that may occur during operation of the skew actuator 2054 or during operation of the CVT 1000.

  Referring now to FIG. 29A, in one embodiment, the control module 2056 includes a control device 2070, a communication device 2072, and a microprocessor 2074. In some embodiments, the controller 2070 can be configured to perform a control process, such as a well-known proportional / integral gain control process based on the setpoint signal 2076 and the feedback signal 2078. In one embodiment, the setpoint signal 2076 can be configured to represent a desired input speed. In some embodiments, the setpoint signal 2076 can be configured to represent a desired speed ratio of the CVT 2051, for example. In other embodiments, the setpoint signal 2076 may be configured to represent a desired output speed, desired input torque and / or desired output torque of the CVT 2051, or any other desired operating characteristic. The feedback signal 2078 can be configured to provide an indication of the current operating state of the CVT 2051. In one embodiment, feedback signal 2078 is configured to represent the actual speed of CVT 2051. In some embodiments, feedback signal 2078 is configured to represent the actual speed ratio of CVT 2051. In other embodiments, the feedback signal 2078 is configured to provide an indication of the actual output speed, actual output torque, and / or actual input torque of the CVT 2051. The controller 2070 can be configured to cooperate with the communication device 2072. The communication device 2072 may include communication hardware such as a serial device, eg, an RS232 device, a USB device, or other known communication hardware. Communication device 2072 can be adapted to cooperate with microprocessor 2074. Microprocessor 2074 can generate actuator command signal 2080 based at least in part on setpoint signal 2076 and / or feedback signal 2078. In one embodiment, the microprocessor 2074 includes hardware configured to operate a power control circuit that communicates with any one or more of the skew actuator 2054, CVT 2051, prime mover 2052, and / or load 2053. .

  Referring now to FIG. 29B, in one embodiment, the skew control process 2100 may be implemented, for example, by a microprocessor that communicates with the power control circuit hardware of the CVT 1000. In some embodiments, the skew-based control process 2100 can be implemented with a microprocessor that communicates with the CVT 12 or other CVT embodiments described herein. The skew based control process 2100 begins at block 2101. The skew-based control process 2100 then proceeds to block 2102 and receives a desired tilt angle (γ) setting for the traction planet assembly 1024 of the CVT 1000, for example. The skew-based control process 2100 proceeds to block 2103 and determines a command signal for the skew actuator. In one embodiment, the command signal is established by a known gain (sometimes referred to as “PI” or “PID”) control process. Next, the skew-based control process 2100 moves to the actuator sub-process 2104 and applies the command signal to the skew actuator 2054, for example. When the actuator sub-process 2104 is complete, the skew-based control process 2100 proceeds to block 2105 and measures the tilt angle (γ) of the traction planet assembly 1024. In one embodiment, the actual tilt angle (γ) of the traction planet assembly 1024 is used as a proximity sensor or other device adapted to provide an indication of the actual tilt angle (γ) of the traction planet assembly 1024. Can be confirmed. Next, the skew-based control process 2100 proceeds to decision block 2106 and forms a comparison value by comparing the measured tilt angle (γ) with a desired tilt angle (γ) setpoint. If the measured tilt angle (γ) is not equal to the desired tilt angle (γ) setting, the skew-based control process 2100 returns to block 2103. If the measured tilt angle (γ) is equal to the desired tilt angle (γ) setting, the skew-based control process 2100 proceeds to end block 2107. The skew-based control process 2100 remains at the end block 2107 until a new tilt angle (γ) setting is received. In some embodiments, the skew-based control process 2100 is configured to operate in an open loop manner, and in such cases, blocks 2105 and 2106 are not included in the skew-based control process 2100.

  Referring now to FIG. 29C, in one embodiment, the skew control process 2110 may be implemented, for example, by a microprocessor that communicates with the power control circuit hardware of the CVT 1000. In some embodiments, the skew-based control process 2110 can be implemented with a microprocessor that communicates with the CVT 12 or other CVT embodiments described herein. The skew-based control process 2110 begins at block 2111. The skew-based control process 2110 then proceeds to block 2112 and receives the desired output speed setpoint setpoint for the CVT 1000. The skew-based control process 2110 proceeds to block 2113 and determines a command signal for the skew actuator. In one embodiment, the command signal is determined by a known PI control process. Next, the skew-based control process 2110 moves to the actuator sub-process 2114 and applies the command signal to, for example, the skew actuator 2054. When the actuator sub-process 2114 is complete, the skew-based control process 2110 proceeds to block 2115 and measures the output speed of the CVT 1000. In one embodiment, the output speed of the CVT 1000 can be determined by using a speed sensor configured to measure a speed indicative of the output speed of the CVT 1000. Next, the skew-based control process 2110 proceeds to decision block 2116 and forms a comparison value by comparing the measured output speed with a desired output speed setpoint. If the measured output speed is not equal to the desired output speed setting, the skew-based control process 2110 returns to block 2113. If the measured output speed is equal to the desired output speed setting, the skew-based control process 2110 proceeds to end block 2117. The skew-based control process 2110 remains at the end block 2117 until a new output speed setting is received. In some embodiments, the skew-based control process 2110 is configured to operate in an open loop manner, and in such cases, blocks 2115 and 2116 are not included in the skew-based control process 2110.

  Referring now to FIG. 29D, in one embodiment, the skew control process 2120 may be implemented, for example, by a microprocessor that communicates with the power control circuit hardware of the CVT 1000. In some embodiments, the skew-based control process 2120 can be implemented with a microprocessor that communicates with the CVT 12 or other CVT embodiments described herein. The skew-based control process 2120 begins at block 2121. The skew-based control process 2120 then proceeds to block 2122 and receives the desired input speed setting for the CVT 1000. The skew-based control process 2120 proceeds to block 2123 and determines a command signal for the skew actuator. In one embodiment, the command signal is determined by a known PI control process. Next, the skew-based control process 2120 moves to the actuator sub-process 2124 and applies the command signal to, for example, the skew actuator 2054. Once the actuator sub-process 2124 is complete, the skew-based control process 2120 proceeds to block 2125 and measures the input speed of the CVT 1000. In one embodiment, the input speed of the CVT 1000 can be determined by using a speed sensor configured to measure a speed indicative of the input speed of the CVT 1000. Next, the skew-based control process 2120 proceeds to decision block 2126 and forms a comparison value by comparing the measured input speed with a desired input speed setpoint. If the measured input speed is not equal to the desired input speed setting, the skew-based control process 2120 returns to block 2123. If the measured input speed is equal to the desired input speed setting, the skew-based control process 2120 proceeds to end block 2127. The skew-based control process 2120 remains at the end block 2127 until a new input speed setting is received. In some embodiments, the skew-based control process 2120 is configured to operate in an open loop manner, and in such cases, blocks 2125 and 2126 are not included in the skew-based control process 2120.

  Turning now to FIGS. 30-33, in one embodiment, the CVT 3000 can include a first housing member 3002 coupled to a second housing member 3004. A flange 3006 may be provided at the first end of the first housing member 3002. Flange 3006 can facilitate coupling of CVT 3000 to, for example, an electric drive motor (not shown). In some embodiments, the CVT 3000 can be coupled to a crankshaft of an internal combustion engine (not shown). The CVT 3000 can have a skew actuator 3005 coupled to a skew driver 3007. Skew actuator 3005 and skew driver 3007 can be adapted to facilitate adjustment of the skew state and thus the operating state of CVT 3000. In some embodiments, the skew actuator 3005 can communicate with a skew control system (not shown).

  In one embodiment, the CVT 3000 is provided with a main shaft 3008 that can be configured to be substantially aligned with the longitudinal axis 3010 of the CVT 3000. Main shaft 3008 may be coupled to input driver 3012 and to planetary driver 3014. In one embodiment, the main shaft 3008 can be adapted to couple to several components of the pump 3015. In one embodiment, pump 3015 is a well-known gear rotor type pump. In one example, the pump 3015 has an internal gear configured to be driven by the main shaft 3008. The pump 3015 can also have a housing configured to be substantially non-rotatable about the longitudinal axis 3010. The pump 3015 can be configured to provide lubricating oil to the CVT. In some embodiments, the pump 3015 can be configured to supply pressurized hydraulic fluid to, for example, an aircraft control system. Planetary driver 3014 can be configured to couple to planetary gear assembly 3016. In one embodiment, the planetary gear assembly 3016 may be a set of dual pinion planetary gears having a sun gear, a set of planetary gears, a carrier and a ring gear. In some embodiments, the planetary driver 3014 can be coupled to the carrier of the planetary gear assembly 3016.

  Still referring to FIGS. 30-33, in one embodiment, the CVT 3000 is provided with a first traction ring 3018 coupled to the input driver 3012. First traction ring 3018 is in contact with variator assembly 3020. The CVT 3000 can be provided with a second traction ring 3022 in contact with the variator assembly 3020. A second traction ring 3022 can be coupled to the axial force generator assembly 3024. In one embodiment, the axial force generator assembly 3024 includes a plurality of rollers configured to cooperate with a plurality of tilts to generate an axial force during operation of the CVT 3000. An axial force generator assembly 3024 can be coupled to the planetary sun driver 3026. A planetary sun driver 3026 can be coupled to the sun gear of the planetary gear assembly 3016. In one embodiment, the planetary gear assembly 3016 can be coupled to the output shaft 3028. In some embodiments, output shaft 3028 is coupled to a ring gear of planetary gear assembly 3016.

  During operation of the CVT 3000, input power can be supplied to the CVT 3000 via a coupling on the main shaft 3008. The main shaft 3008 can transmit power to the input driver 3012 and to the planetary driver 3014. The input driver 3012 can be configured to power the variator assembly 3020 by transmitting power to the first traction ring 3018. The variator assembly 3020 transmits power to the second traction ring 3022. The second traction ring 3022 transmits power to the planetary sun driver 4026. In one embodiment, power supplied to planetary gear assembly 3016 via planetary driver 3014 and planetary sun driver 3026 is transmitted out of CVT 3000 via output shaft 3028.

  Referring now to FIGS. 34 and 35, in one embodiment, the variator assembly 3020 includes a plurality of traction planet assemblies 3030 that are angled about the longitudinal axis 3010. Each traction planet assembly 3030 is adapted to contact the traction sun 3032 at a radially inner position. Traction sun 3032 is operably coupled to a set of shift cams 3034. In one embodiment, traction sun 3020 and shift cam 3034 are adapted to move axially along longitudinal axis 3010 during CVT 3000 operation. A shift cam 3034 can be configured to couple to each of the traction planet assemblies 3030. In one embodiment, the variator assembly 3020 is provided with a first carrier member 3036 and a second carrier member 3038. First carrier member 3036 and second carrier member 3038 are configured to support each of traction planet assemblies 3030. In one embodiment, the second carrier member 3038 is configured to rotate relative to the first carrier member 3036. First carrier member 3036 and second carrier member 3038 can be coupled to skew driver 3007. First carrier member 3036 and second carrier member 3038 can be coupled to first carrier cap 3040 and second carrier cap 3042, respectively. First carrier cap 3040 and second carrier cap 3042 are configured to couple to each of traction planet assemblies 3030. First carrier cap 3040 and second carrier cap 3042 can be attached to first carrier member 3036 and second carrier member 3038 by clip 3044.

  Referring now specifically to FIG. 35, in one embodiment, the variator assembly 3020 is provided with a plurality of carrier inserts 3046. The carrier insert 3046 can be adapted to attach to the first carrier member 3036 and the second carrier member 3038. When assembled, the carrier insert 3046 can contact several components of the traction planet assembly 3030. In one embodiment, the carrier insert 3046 is made from steel and the first carrier member 3036 and the second carrier member 3038 are made from aluminum. In some embodiments, the carrier insert 3046 is integrated with the first carrier member 3036 and the second carrier member 3038.

  Referring now to FIGS. 36 and 37, in one embodiment, the traction planet assembly 3030 has a substantially spherical traction planet 3048 having a central hole adapted to receive the planet shaft 3050. Traction planet 3048 can be coupled to planet shaft 3050 by bearing 3052. The traction planet assembly 3030 can have a first leg 3054 coupled to a first end of the planet shaft 3050. The traction planet assembly 3030 can have a second leg 3056 coupled to the second end of the planetary shaft 3050, the second end of the planetary shaft being remote from the first end. First leg 3054 and second leg 3056 can each be adapted to receive reaction roller 3058. In one embodiment, the reaction roller 3058 is received in a groove 3060 provided in each leg 3054, 3056. In one embodiment, the first leg 3054 can be attached to the planet shaft 3050 by press fit or by other suitable rigid coupling methods. The roller 3058A can be configured to rotate about the planet shaft 3050. In some embodiments, the second leg 3056 can be configured to rotate relative to the planet shaft 3050. The second leg 3056 can be held axially on the planetary shaft 3050 by attaching the roller 3058B to the planetary shaft 3050 by press fitting or by other suitable rigid coupling methods. Roller 3058 is configured to couple to carrier members 3036 and 3038. In one embodiment, a shift reaction roller 3062 is provided on each of the first leg 3054 and the second leg 3056. The shift reaction roller 3062 can be received in a groove 3064 formed in each of the first leg 3054 and the second leg 3056. In one embodiment, groove 3064 is substantially perpendicular to groove 3060. The shift reaction roller 3062 can be adapted to receive the shift roller shaft 3066. Shift roller shaft 3066 can be received in hole 3068. During operation of CVT 3000, shift reaction roller 3062 is coupled to shift cam 3034.

  Still referring to FIGS. 36 and 37, in one embodiment, the first leg 3054 and the second leg 3056 are provided with holes 3070 adapted to receive the planetary shaft 3050. The hole 3070 can be substantially perpendicular to the groove 3060. A shoulder 3072 can be provided on the first leg 3054 and the second leg 3056. Shoulder 3072 can be substantially aligned with hole 3070 and shoulder 3072 can extend from hole 3070. In one embodiment, shoulder 3072 is configured to cooperate with bearing 3052. Reaction surfaces 3074 can be provided on the first leg 3054 and the second leg 3056. The reaction surface 3074 can have a curved profile when viewed in the page plane of FIG. The reaction surface 3074 can be adapted to slidingly engage the carrier caps 3040, 3042.

  Turning now to FIG. 38, in one embodiment, the carrier insert 3046 can have a substantially U-shaped 3076. The carrier insert 3046 can have a reaction surface 3078 formed within the U-shaped body 3076. The reaction surface 3078 is configured to contact the roller 3058 during operation of the CVT 3000. The carrier insert 3046 can have an outer surface 3080. The outer surface 3080 is adapted to be attached to the first carrier member 3036 or the second carrier member 3038.

  Referring now to FIGS. 39 and 40, in one embodiment, the second carrier member 3038 can be a substantially bowl 3082 having a central hole 3084. The bowl 3082 can be provided with a plurality of radial grooves 3086 arranged at an angle around the central hole 3084. Each of the radial grooves 3086 can have a skew reaction surface 3088 configured to contact the roller 3058. The second carrier member 3038 can be provided with a shoulder 3090 that extends axially from the central hole 3084. The shoulder 3090 can be provided with a groove 3092 adapted to receive the clip 3044. A substantially flat surface 3094 can be formed on the outer periphery of the bowl-shaped body 3082. The surface 3094 can be configured to provide a sliding intermediate surface between the first carrier member 3036 and the second carrier member 3038. The second carrier member 3038 can be provided with tabs 3094 that extend radially from the outer periphery of the bowl-shaped body 3082. The tab 3094 can be provided with an elongated hole 3095. The speed ratio can be adjusted during operation of the CVT 3000 by rotating the elongated carrier 3095 with the skew driver 3007 to rotate the second carrier member 3038 relative to the first carrier member 3036. In one embodiment, the first housing member 3002 surrounds the tab 3094 and is configured to facilitate coupling of the first carrier member 3036 and the second carrier member 3038 to the skew driver 3007 (see FIG. 30 and FIG. 31). In some embodiments, the first carrier member 3036 is substantially similar to the second carrier member 3038. The first carrier member 3036 can be provided with holes 3098 (FIG. 34). When the CVT 3000 is assembled, the hole 3098 can be positioned to substantially align with the elongated hole 3095 and can be adapted to cooperate with the skew driver 3007.

  Referring now to FIGS. 41 and 42, in one embodiment, the skew driver 3007 can be a substantially cylindrical rod 3100 having a first end 3102 and a second end 3104. The first end 3101 can be configured to facilitate coupling of the skew driver 3007 to the skew actuator 3005 (FIG. 30). In some embodiments, the first end 3120 is provided with a set of threads adapted to couple to the skew actuator 3005. In other embodiments, the first end 3102 is provided with a spline configured to couple to the skew actuator 3005. The second end 3104 can be adapted to couple to the first carrier member 3036. In some embodiments, the second end 3104 is configured to rotate within the hole 3098 of the first carrier member 3036. The skew driver 3007 can be provided with an eccentric skew cam 3106 formed close to the second end 3104. The eccentric skew cam 3106 can be arranged to have a center 3108 that is radially offset from the center 3110 of the cylindrical rod 3100. The eccentric skew cam 3106 can be configured to couple to the elongated hole 3095 of the second carrier member 3038 (FIG. 39). The eccentric skew cam 3106 is configured to be in sliding engagement with the elongated hole 3095.

  During operation of the CVT 3000, the skew driver 3007 can be rotated by the skew actuator 3007. The rotation of the skew driver 3007 tends to rotate the second carrier member 3038 relative to the first carrier member 3036. The rotation of the second carrier member 3038 relative to the first carrier member 3036 causes a skew condition for each of the traction planet assemblies 3030. The skew condition tends to tilt the planet axis 3050 of the traction planet assembly 3030. The speed ratio of the CVT 3000 is adjusted by the inclination of the planetary shaft 3050.

  Turning now to FIG. 43, in one embodiment, the CVT 4000 can have a plurality of traction planets 4002 arranged at an angle about the longitudinal axis. The CVT 4000 may be provided with a traction sun 4003 configured to contact each traction planet 4002 at a radially inner position. Each of the traction planets 4002 can be provided with a tiltable axis of rotation 4004 configured to be supported by a first carrier member 4006 and a second carrier member 4008. In some embodiments, the first carrier member 3006 and the second carrier member 4008 are adapted to facilitate skewing for each of the traction planets 4002. In one embodiment, the first carrier member 4006 is substantially non-rotatable about the longitudinal axis of the CVT 4000. The CVT 4000 can have a first traction ring 4010 and a second traction ring 4012 that are in contact with each of the traction planets 4002. The first traction ring 4010 and the second traction ring 4012 can be coupled to a first axial force generator 4014 and a second axial force generator 4016, respectively. A first axial force generator 4014 can be coupled to the input driver 4018. A second axial force generator 4016 can be coupled to the output shaft 4020. In one embodiment, the input driver 4018 is coupled to the clutch 4022. The clutch 4022 can be adapted to receive input power from, for example, an electric motor or other suitable prime mover.

  During operation of the CVT 4000, input power can be transmitted from the clutch 4022 to the input driver 4018. The input driver 4018 supplies power to the first traction ring 4010 via the first axial force generator 4014. First traction ring 4010 transmits power to each of traction planets 4002. The traction planet 4002 transmits power to the second traction ring 4012. Power is supplied from the second traction ring 4012 to the output shaft 4020 via the second axial force generator 4016. In some embodiments, the output shaft 4020 is configured to power the load 4024.

  Referring now to FIG. 44, in one embodiment, the CVT 4100 can have a plurality of traction planets 4102 arranged at an angle about the longitudinal axis. The CVT 4100 can be provided with a traction sun 4103 configured to contact each traction planet 4102 at a radially inner position. Each of the traction planets 4102 can be provided with a tiltable rotation shaft 4104. The traction planet 4102 can be adapted to couple to the first carrier member 4106 and the second carrier member 4108, respectively. In one embodiment, the first carrier member 4106 and the second carrier member 4108 are configured to facilitate skewing for each of the traction planets 4102. In one embodiment, the first carrier member 4106 and the second carrier member 4108 are configured to rotate about the longitudinal axis of the CVT 4100. The CVT 4100 may include a first traction ring 4110 and a second traction ring 4112. A first traction ring 4110 and a second traction ring 4112 may be coupled to the first axial force generator 4114 and the second axial force generator 4116, respectively. In one embodiment, the first axial force generator 4114 is configured to be substantially non-rotatable with respect to the longitudinal axis of the CVT 4100. A second axial force generator 4116 can be coupled to the output shaft 4118.

  During operation of CVT 4100, first carrier member 4106 can be adapted to receive power from input shaft 4120. The first carrier member 4106 supplies power to each of the traction planets 4120. The traction planet 4102 rotates around the traction sun 4103 and transmits power to the second traction ring 4112. Power is transmitted from the second traction 4112 to the output shaft via the second axial force generator 4116. Output shaft 4118 is adapted to power load 4122.

  Turning now to FIGS. 45-48, in one embodiment, the variator 4200 may have a traction sun assembly 4202 coupled to a plurality of traction planetary subassemblies 4202. The variator 4200 may be configured for use with, for example, a CVT 12, CVT 1000, or CVT 3000. Each of the traction planetary subassemblies 4204 is operably coupled to a first carrier member 4206 and a second carrier member 4208. In some embodiments, the carrier retaining ring 4210 can be attached to the first carrier member 4206 and the second carrier member 4208. The traction sun subassembly 4204 can have a traction sun 4212. The traction sun 4212 can have a central hole 4214 adapted to receive a bearing 4216. By providing the shoulder 4218 and the c-clip groove 4220 in the center hole 4214, the bearing 4216 can be easily coupled to the center hole 4214. The traction sun 4214 can be provided with a plurality of lubricating oil passages 4222 extending radially outward from the central hole 4214. In one embodiment, a first contact surface 4224 </ b> A and a second contact surface 4224 </ b> B extending from the valley 4226 are provided on the outer periphery of the traction sun 4214. The first contact surface 4224A and the second contact surface 4224B can contact each of the traction planetary subassemblies 4204. First contact surface 4224A and second contact surface 4224B can extend from valley 4226 at an angle 4228 when viewed in cross-section in the plane of FIG. In one embodiment, angle 4228 ranges from about 2 degrees to 45 degrees. In a preferred embodiment, angle 4228 is between about 5 degrees and 10 degrees. During operation of the variator 4200, the traction sun assembly 4204 is adapted to remain axially coupled to the traction planet subassembly 4204 as the traction planet subassembly 4204 tilts. In some embodiments, the sun assembly 4002 is no longer coupled to the central hole 4214, but remains radially coupled to the CVT 1000, for example, by contacting the traction planet assembly 4204 via the contact surface 4224. The bearing 4216 can be removed.

  Referring now to FIGS. 49-51, in one embodiment, the gear 5000 can be coupled to the first carrier member 5002 and to the second carrier member 5004. The gear 5000 can facilitate rotation about the longitudinal axis between the first carrier member 5002 and the second carrier member 5004. The gear 5000 can be provided with a shaft 5006. The shaft 5006 can extend radially outward from the first carrier member 5002 and the second carrier member 5004. Shaft 5006 can be configured to couple to a skew actuator (not shown). In some embodiments, the gear 5000 can be a conical gear and the first carrier member 5002 and the second carrier member 5004 can be adapted to properly accommodate the conical gear. In operation, the skew actuator can rotate gear 5000 by transmitting rotation to shaft 5006. The rotation of the gear 5000 tends to rotate the first carrier member 5002 in the first rotation direction and tends to rotate the second carrier member 5004 in the second rotation direction substantially opposite to the first rotation direction. There is.

  With particular reference now to FIGS. 50 and 51, in one embodiment, the skew driver 5010 can be coupled to the first carrier member 5012 and to the second carrier member 5014. The first carrier member 5012 and the second carrier member 5014 can be substantially similar to the first carrier member 5002 and the second carrier member 5004. The first carrier member 5012 can be threaded to engage the skew driver 5010 at the first thread intermediate surface 5016. The second carrier member 5014 can be threaded to engage the skew driver 5010 at the second thread intermediate surface 5018. The first thread intermediate surface 5018 is generally a right-hand thread, while the second thread intermediate surface 5018 is a left-hand thread. In one embodiment, the skew driver 5010 can be coupled to a skew actuator (not shown). In some embodiments, the skew driver 5010 is disposed so as to contact the first carrier member 5012 and the second carrier member 5014. During operation, the skew driver 5010 can be rotated to cause relative rotation between the first carrier member 5012 and the second carrier member 5014. Screw intermediate surfaces 5016 and 5018 can be adapted to accommodate slight radial displacement to facilitate rotation of first carrier member 5012 and second carrier member 5014 relative to each other.

  With particular reference now to FIG. 52, in one embodiment, gear 5020 can be coupled to first carrier member 5022 and to second carrier member 5024. For clarity, FIG. 52 shows gear 5020 without any known teeth. The gear 5020 can facilitate rotation about the longitudinal axis between the first carrier member 5022 and the second carrier member 5024. The gear 5020 can be provided with a shaft 5026. The shaft 5026 can be configured to couple to a skew actuator (not shown). In one embodiment, shaft 5026 extends axially from gear 5020. The first carrier member 5022 can be provided with an engagement extension 5028 adapted to contact the gear 5020. In operation, the skew actuator can rotate gear 5020 by transmitting rotation to shaft 5026. The rotation of the gear 5020 tends to rotate the first carrier member 5022 in the first rotation direction and tends to rotate the second carrier member 5024 in the second rotation direction that is substantially opposite to the first rotation direction. There is.

  It should be noted that the above description provided dimensions for several components or subassemblies. The dimensions or dimension ranges described above are provided to comply as much as possible with some legal requirements, such as best mode. However, the scope of the invention described herein should be determined only by the language of the claims, and thus any claim is characterized by a particular dimension or range of dimensions. Except as far as possible, none of the dimensions mentioned should be construed as limiting to the embodiments of the present invention.

  The above description details several embodiments of the invention. It will be understood, however, that no matter how detailed the foregoing appears in text, the invention can be implemented in many ways. As previously mentioned, the use of a particular term when describing some feature or aspect of the invention means that the term is any given feature of the feature or aspect of the invention to which the term relates. It should be noted that it should not be construed to imply that it has been redefined herein as being limited to including.

Claims (3)

A power source capable of generating power in a first operating range, and a variator coupled to a power load configured to operate in a second operating range, disposed between the first carrier member and the second carrier member And a plurality of tiltable traction planet assemblies operatively coupled to the first carrier member and the second carrier member, each traction planet assembly having a traction planet and a planet shaft, wherein the first carrier member is A plurality of radial offset grooves, the second carrier member having a plurality of radial grooves, and the first carrier member rotating relative to the second carrier member about a longitudinal axis; A configured variator;
A controller configured to receive at least one signal related to the speed of the power source or the speed of the power load and adjust a transmission ratio of the variator based on the at least one signal, the adjustment of the transmission ratio being In order to maintain a constant angle (Ψ) of the planetary axis while changing the tilt angle (γ), the relative angular position (β) of the first carrier member with respect to the second carrier member is Changing the first carrier member to a non-zero angle relative to two carrier members;
Comprising
Continuously variable transmission. The power source includes an electric motor or an internal combustion engine,
The continuously variable transmission according to claim 1 . The output shaft of the variator is coaxial with the power load;
The continuously variable transmission according to claim 1 .

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