[go: up one dir, main page]

WO2017151568A1 - Système d'actionneur de changement de vitesse et procédé pour une transmission à engrenages planétaires à billes à variation continue ayant un support rotatif et/ou mis à la terre - Google Patents

Système d'actionneur de changement de vitesse et procédé pour une transmission à engrenages planétaires à billes à variation continue ayant un support rotatif et/ou mis à la terre Download PDF

Info

Publication number
WO2017151568A1
WO2017151568A1 PCT/US2017/019861 US2017019861W WO2017151568A1 WO 2017151568 A1 WO2017151568 A1 WO 2017151568A1 US 2017019861 W US2017019861 W US 2017019861W WO 2017151568 A1 WO2017151568 A1 WO 2017151568A1
Authority
WO
WIPO (PCT)
Prior art keywords
continuously variable
coupled
carrier member
variable transmission
helical gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2017/019861
Other languages
English (en)
Inventor
Krishna Kumar
William F. WALTZ
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dana Ltd
Original Assignee
Dana Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Dana Ltd filed Critical Dana Ltd
Publication of WO2017151568A1 publication Critical patent/WO2017151568A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/26—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution
    • F16H15/28—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution with external friction surface

Definitions

  • a driveline including a continuously variable transmission allows an operator or a control system to vary a drive ratio in a stepless manner, permitting a power source to operate at its most advantageous rotational speed.
  • a continuously variable transmission including: a plurality of tiltable balls arrayed radially about a longitudinal axis of the transmission; a first carrier member having a first plurality of guide slots, the tiltable balls operably coupled to the first plurality of guide slots; a second carrier member having a second plurality of guide slots, the tiltable balls operably coupled to the second plurality of guide slots, wherein the second plurality of guide slots are radially offset from the first plurality of guide slots; a first traction ring assembly in contact with each tiltable ball; a second traction ring assembly in contact with each tiltable ball; and a carrier skew shift actuator mechanism including: a first helical gear coupled to the fust carrier member; a second helical gear coupled to the second carrier member; and a driver shaft coupled to the first helical gear and the second helical gear; a disconnect mechanism operably coupled to the driver shaft, the disconnect mechanism positioned between the first helical gear and the second helical gear.
  • Figure 1 is a side sectional view of a ball-type variator.
  • Figure 2 is a plan view of a carrier member that is used in the variator of Figure 1.
  • Figure 3 is an illustrative view of different tilt positions of the ball-type variator of Figure 1.
  • Figure 4 is a schematic diagram of a continuously variable transmission of the ball-type depicted in Figures 1-3 having a carrier skew shift actuator mechanism utilizing a disconnect mechanism.
  • Figure 5 is a schematic diagram of another continuously variable transmission of the ball- type depicted in Figures 1-3 having a carrier skew shift actuator mechanism utilizing a brake clutch.
  • Figure 6 is a schematic diagram of yet another continuously variable transmission of the ball-type depicted in Figures 1-3 having a carrier skew shift actuator mechanism utilizing a clutch- brake unit.
  • Figure 7 is a schematic diagram of yet another continuously variable transmission of the ball-type depicted in Figures 1-3 having a carrier skew shift actuator mechanism utilizing a force multiplying device.
  • Figure 8 is a schematic diagram of yet another continuously variable transmission of the ball-type depicted in Figures 1-3 having a carrier skew shift actuator mechanism and a torsion spring.
  • Figure 9 is a schematic diagram of yet another continuously variable transmission of the ball-type depicted in Figures 1-3 having a carrier skew shift actuator mechanism.
  • Figure 10 is a schematic diagram of yet another continuously variable transmission of the ball-type depicted in Figures 1-3 having a carrier skew shift actuator mechanism.
  • CVTs based on a ball type variators, also known as CVP, for continuously variable planetary.
  • Basic concepts of a ball type Continuously Variable Transmissions are described in United States Patent No. 8,469,856 and 8,870,711 incorporated herein by reference in their entirety.
  • Such a CVT adapted herein as described throughout this specification, comprises a number of balls (planets, spheres) 1, depending on the application, two ring (disc) assemblies with a conical surface in contact with the balls, an input traction ring 2, an output traction ring 3, and an idler (sun) assembly 4 as shown on FIG. 1.
  • the balls are mounted on tiltable axles 5, themselves held in a carrier (stator, cage) assembly having a first carrier member 6 operably coupled to a second carrier member 7.
  • the first carrier member 6 rotates with respect to the second carrier member 7, and vice versa.
  • the first carrier member 6 is substantially fixed from rotation while the second carrier member 7 is configured to rotate with respect to the first carrier member, and vice versa.
  • the first carrier member 6 is provided with a number of radial guide slots 8.
  • the second carrier member 7 is provided with a number of radially offset guide slots 9, as illustrated in FIG. 2.
  • the radial guide slots 8 and the radially offset guide slots 9 are adapted to guide the tiltable axles 5.
  • the axles 5 are adjusted to achieve a desired ratio of input speed to output speed during operation of the CVT.
  • adjustment of the axles 5 involves control of the position of the first and second carrier members to impart a tilting of the axles 5 and thereby adjusts the speed ratio of the variator.
  • Other types of ball CVTs also exist, but are slightly different.
  • FIG. 3 The working principle of such a CVP of FIG. 1 is shown on FIG. 3.
  • the CVP itself works with a traction fluid.
  • the lubricant between the ball and the conical rings acts as a solid at high pressure, transferring the power from the input ring, through the balls, to the output ring.
  • the ratio is changed between input and output.
  • the ratio is one, illustrated in FIG. 3, when the axis is tilted the distance between the axis and the contact point change, modifying the overall ratio. All the balls' axes are tilted at the same time with a mechanism included in the carrier and/or idler.
  • Embodiments disclosed here are related to the control of a variator and/or a CVT using generally spherical planets each having a tiltable axis of rotation that are adjusted to achieve a desired ratio of input speed to output speed during operation.
  • adjustment of said axis of rotation involves angular misalignment of the planet axis in a first plane in order to achieve an angular adjustment of the planet axis in a second plane that is substantially perpendicular to the first plane, thereby adjusting the speed ratio of the variator.
  • the angular misalignment in the first plane is referred to here as "skew”, “skew angle”, and/or "skew condition”.
  • a control system coordinates the use of a skew angle to generate forces between certain contacting components in the variator that will tilt the planet axis of rotation.
  • the tilting of the planet axis of rotation adjusts the speed ratio of the variator.
  • radial is used here to indicate a direction or position that is perpendicular relative to a longitudinal axis of a transmission or variator.
  • axial refers to a direction or position along an axis that is parallel to a main or longitudinal axis of a transmission or variator.
  • the terms "operationally connected,” “operationally coupled”, “operationally linked”, “operably connected”, “operably coupled”, “operably linked,” “operably coupleable” and like terms refer to a relationship (mechanical, linkage, coupling, etc.) between elements whereby operation of one element results in a corresponding, following, or simultaneous operation or actuation of a second element. It is noted that in using said terms to describe inventive
  • Traction drives usually involve the transfer of power between two elements by shear forces in a thin fluid layer trapped between the elements.
  • the fluids used in these applications usually exhibit traction coefficients greater than conventional mineral oils.
  • the traction coefficient ( ⁇ ) represents the maximum available traction force which would be available at the interfaces of the contacting components and is the ratio of the maximum available drive torque per contact force.
  • friction drives generally relate to transferring power between two elements by frictional forces between the elements.
  • the CVTs described here operate in both tractive and frictional applications.
  • the CVT operates at times as a friction drive and at other times as a traction drive, depending on the torque and speed conditions present during operation.
  • infinitely variable transmission is a type of continuously variable transmission (CVT) that is capable of shifting to a ratio of zero speed at one of the driving elements.
  • An IVT comprises a CVT and all of the claims herein pertain to both CVTs and IVTs that use a continuously variable planetary (CVP).
  • CVP continuously variable planetary
  • the mechanisms described herein operate in multiple modes, for example, an IVT mode, a CVT mode, or some combination thereof such as a planetary differential mode or an operating mode with all nodes or components of the CVP are free to rotate.
  • a continuously variable transmission (CVT) 10 includes a CVP of the type described in FIGS. 1-3.
  • the CVT 10 has a first carrier member 11 and a second carrier member 12 each configured to support a number of balls.
  • the CVT 10 has a first traction ring assembly 13 and a second traction ring assembly 14 coupled to each ball.
  • the CVT 10 has a sun assembly 15 coupled to each ball.
  • the sun assembly 15 is positioned radially inward of each ball.
  • the CVT 10 has a first rotatable shaft 16 coupled to the second carrier member 12.
  • the sun assembly 15 is rotatably supported on the first rotatable shaft 16 with a bearing, for example.
  • the first second carrier member 1 1 is rotatably supported on the first rotatable shaft 16 with a bearing, for example.
  • the CVT 10 has a second rotatable shaft 17 coupled to the first traction ring assembly 13.
  • the CVT 10 has a third rotatable shaft 18 coupled to the second traction ring assembly 14.
  • the second rotatable shaft 17 and the third rotatable shaft 18 are optionally configured to be rotatably supported with bearings (not shown) on the first rotatable shaft 16.
  • the CVT 10 has a first axial thrust bearing 19 coupled to the first traction ring assembly 13 and a grounded member of the transmission, such as a housing (not shown).
  • the CVT 10 has a second axial thrust bearing 20 coupled to the second traction ring assembly 14 and a grounded member of the transmission, such as a housing (not shown).
  • the CVT 10 is optionally configured with a selectable torque transmitting device 21 operably coupled to the first carrier member 11 and the first traction ring assembly 13.
  • the selectable torque transmitting device 21 is a one-way clutch such as a common roller clutch or a sprag clutch, among others.
  • the selectable torque transmitting device 21 is a bi-directional clutch configured to constrain the speed of the first carrier member 11 with respect to the first traction ring assembly 13.
  • the first rotatable shaft 16, the second rotatable shaft 17, and the third rotatable shaft 18 are each configured to transmit or receive rotational power.
  • the tirst rotatable shaft 16 and the second rotatable shaft 17 are optionally configured to couple to a source of rotational power such as an engine, an electric motor, generator, flywheel, auxiliary power devices (fans, air conditioners, pumps), energy storage devices, upstream or downstream gearing, among others.
  • the third rotatable shaft 18 is configured to couple to a driven component.
  • the third rotatable shaft 18 is optionally configured to receive a power input from a source of rotational power.
  • first rotatable shaft 16 or the second rotatable shaft 17 are configured to be selectively grounded from rotation. It should be appreciated, that additional gearing, chain drives, or countershafts are optionally configured to be used in the embodiments disclosed herein.
  • the CVT 10 is provided with a carrier skew shift actuator mechanism 30.
  • the carrier skew shift actuator mechanism 30 includes a driver shaft 31 adapted to rotate and to translate axially.
  • the carrier skew shift actuator mechanism 30 includes a first helical gear 32 and a second helical gear 33 coupled to the driver shaft 31.
  • the first helical gear 32 is coupled to the first carrier member 11.
  • the first helical gear 32 has helical teeth engaged with the first carrier member 11.
  • the second helical gear 33 is coupled to the second carrier member 12.
  • the second helical gear 33 has helical teeth engaged with the second carrier member 12.
  • the first helical gear 32 and the second helical gear 33 have helical teeth with different helix angles.
  • the first helical gear 32 has straight teeth and the second helical gear 33 has angle teeth.
  • the first helical gear 32 and the second helical gear 33 have common pitch diameters.
  • the carrier skew shift actuator mechanism 30 includes an actuator 34 coupled to the driver shaft 31.
  • the actuator 34 is an electrical motor adapted to provide axial translation of the driver shaft 31.
  • the actuator 34 incorporates an electromagnetic, hydraulic, pneumatic, or electromechanical actuation system equipped with or without a mechanical locking mechanism such as a lead screw.
  • the CVT 10 includes a disconnect mechanism 35 coupled to the driver shaft 31.
  • the disconnect mechanism 35 is positioned between the first helical gear 32 and the second helical gear 33.
  • the disconnect mechanism 35 is configured to selectively engage and disengage the first helical gear 32 and the second helical gear 33 to selectively control the feedback torque between the first carrier member 11 and the second carrier member 12.
  • the skew shift actuator mechanism 30 is operably coupled to a motor/generator or other electrical, mechanical, or hydraulic machine (not shown) configured to control speed to a zero speed condition.
  • an adjustment in the ratio of the input speed to output speed corresponds to a relative rotation of the first carrier member 11 with respect to the second carrier member 12.
  • the carrier skew shift actuator mechanism 30 facilitates the relative rotation of the first carrier member 11 with respect to the second carrier member 12.
  • an axial translation of the driver shaft 31 corresponds to an axial translation of the second helical gear 33 to thereby rotate the first carrier member 11 with respect to the second carrier member 12.
  • the selection of the helical angle of the gear teeth on the first helical gear 32 and the second helical gear 33 is within a designer's choice to produce a desired phasing of the first carrier member 11 and the second carrier member 12.
  • an electronic control system (not shown) is configured to control the selective engagement of the disconnect mechanism 35 to engage and disengage the first helical gear 32 with the second helical gear 33.
  • the electronic control system is configured to control the actuator 34.
  • the actuator 34 is a lead screw type actuator having an integral position sensor.
  • the electronic control system is optionally configured to monitor the signal from the position sensor corresponding to a position of the driver shaft 31.
  • the electronic control system is optionally configured to monitor the relative position of the first helical gear 32 with respect to the second helical gear 33 using any position sensing mechanism, a calculation within the control software, or any combination thereof.
  • a continuously variable transmission (CVT) 40 is configured in a substantially similar way to the CVT 10.
  • the CVT 40 includes a braking mechanism 41 coupled to the driver shaft 31.
  • the braking mechanism 41 is configured to be a mechanical brake.
  • the braking mechanism 41 is configured to be an electro-mechanical, electro-magnetic, or hydraulic braking mechanism.
  • a continuously variable transmission (CVT) 50 is configured in a substantially similar way to the CVT 10. For description purposes, only the differences between the CVT 50 and the CVT 10 will be described.
  • the CVT 50 includes a clutch-brake unit 51 coupled to the driver shaft 31 and positioned between the first helical gear 32 and the second gear helical 33.
  • the clutch-brake unit 51 operates as a clutch when engaged in a first position, and operates as a brake when engaged in a second position.
  • the clutch-brake unit 51 is a typical clutch with a band brake surrounding trie clutch.
  • the clutch-brake unit 51 is an electric/electromagnetic device configured to be controlled by an electronic control system (not shown).
  • a continuously variable transmission (CVT) 60 is configured in a substantially similar way to the CVT 50.
  • the CVT 60 includes force multiplying mechanism 61 coupled to the driver shaft 31 and the actuator 34.
  • the force multiplying mechanism 61 is configured to provide a mechanical advantage between the actuator 34 and the driver shaft 31.
  • the force multiplying mechanism 61 is a cam-and-follower mechanism.
  • the force multiplying mechanism 61 is a ball- ramp cam mechanism.
  • the force multiplying mechanism 61 is configured with a lead screw mechanism.
  • a continuously variable transmission (CVT) 70 is configured in a substantially similar way to the CVT 60.
  • the CVT 70 includes a torsion spring 71 operably coupled to the first carrier member 11 and the second carrier member 12.
  • the torsion spring 71 applies a spring torque to the first carrier member 11 and the second carrier member 12 to bias the first carrier member 11 to a position relative to the second carrier member 12.
  • a continuously variable transmission (CVT) is a continuously variable transmission (CVT)
  • the CVT 80 is configured in a substantially similar way to the CVT 60. For description purposes, only the differences between the CVT 80 and the CVT 60 will be described.
  • the CVT 80 includes a torsion spring 81 operably coupled to the first carrier member 11 and the second carrier member 12. During operation of the CVT 80, the torsion spring 81 applies a spring torque to the first carrier member 11 and the second carrier member 12 to bias the first carrier member 11 to a position relative to the second carrier member 12.
  • the CVT 80 includes an actuator gear 82 coupled to an actuator shaft 83. The actuator shaft 83 is coupled to the actuator 34. During operation of the CVT 80, the actuator gear 82 provides a mechanical advantage for driving the second helical gear 33.
  • the CVT 90 is configured in substantially similar way as the CVT 50. For description purposes, only the differences between the CVT 90 and the CVT 50 will be described.
  • the CVT 90 includes a second disconnect mechanism 91 coupled to the driver shaft 31.
  • the (JVT 90 includes a first transfer gear 92 coupled to the driver shaft 31.
  • the second disconnect mechanism 91 is position between the first helical gear 32 and the first transfer gear 92.
  • the first transfer gear 92 engages a second transfer gear 93.
  • the second transfer gear 93 is coupled to the second rotatable shaft 17 and thereby the first traction ring assembly.
  • the second disconnect mechanism 91 is selectively engaged to control the transmission of rotatable power from the driver shaft 31 to and from the second rotatable shaft 17.
  • the disconnect mechanism 91 is disengaged when the clutch-brake unit 51 is engaged as a brake.
  • the disconnect mechanism 91 is a clutch.
  • the first transfer gear 92 and the second transfer gear 93 are optionally configured to be a planetary gear set having a ring gear, planet carrier, and sun gear such that a defined speed differential is introduced between the first traction ring and the first carrier member of the CVT. It should be appreciated that any type of clutching, gearing, hydrodynamic, hydro-mechanical or electrodynamic mechanism that introduces a speed differential between the first traction ring and the first carrier member of the CVT is an optional configuration.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

L'invention concerne des dispositifs et des procédés se rapportant à la transmission de puissance dans des véhicules à moteur. La puissance peut être transmise d'une manière plus régulière et plus efficace par la répartition du couple entre deux trajectoires de couple ou plus. Une transmission à variation continue comporte un ensemble variateur à billes ayant une pluralité de billes inclinables supportées dans un ensemble de support. Dans certains modes de réalisation, l'ensemble de support est configuré pour être rotatif et mis à la terre de manière sélective. Un mécanisme d'actionneur de décalage d'inclinaison de support est configuré pour fournir un moyen servant à ajuster la position relative d'un premier élément de support par rapport à un deuxième élément de support de l'ensemble de support pour ainsi ajuster le fonctionnement de la transmission à variation continue.
PCT/US2017/019861 2016-03-01 2017-02-28 Système d'actionneur de changement de vitesse et procédé pour une transmission à engrenages planétaires à billes à variation continue ayant un support rotatif et/ou mis à la terre Ceased WO2017151568A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201662301992P 2016-03-01 2016-03-01
US62/301,992 2016-03-01

Publications (1)

Publication Number Publication Date
WO2017151568A1 true WO2017151568A1 (fr) 2017-09-08

Family

ID=58266214

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2017/019861 Ceased WO2017151568A1 (fr) 2016-03-01 2017-02-28 Système d'actionneur de changement de vitesse et procédé pour une transmission à engrenages planétaires à billes à variation continue ayant un support rotatif et/ou mis à la terre

Country Status (1)

Country Link
WO (1) WO2017151568A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110131409A (zh) * 2019-05-29 2019-08-16 杭州神驹科技有限公司 一种机械式自动变速箱换档执行机构
WO2023192166A1 (fr) * 2022-03-29 2023-10-05 Gates Corporation Systèmes de transmission à variation continue commandée par came

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010044778A1 (fr) * 2008-10-14 2010-04-22 Fallbrook Technologies Inc. Transmission à variation continue
US20100267510A1 (en) * 2009-04-16 2010-10-21 Fallbrook Technologies Inc. Continuously variable transmission
US8469856B2 (en) 2008-08-26 2013-06-25 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US20140274551A1 (en) * 2013-03-14 2014-09-18 Team Industries, Inc. Continuously variable transmission with input/output planetary ratio assembly
US8870711B2 (en) 2008-10-14 2014-10-28 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US20150345599A1 (en) * 2014-05-30 2015-12-03 Toyota Jidosha Kabushiki Kaisha Continuously variable transmission

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8469856B2 (en) 2008-08-26 2013-06-25 Fallbrook Intellectual Property Company Llc Continuously variable transmission
WO2010044778A1 (fr) * 2008-10-14 2010-04-22 Fallbrook Technologies Inc. Transmission à variation continue
US8870711B2 (en) 2008-10-14 2014-10-28 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US20100267510A1 (en) * 2009-04-16 2010-10-21 Fallbrook Technologies Inc. Continuously variable transmission
US20140274551A1 (en) * 2013-03-14 2014-09-18 Team Industries, Inc. Continuously variable transmission with input/output planetary ratio assembly
US20150345599A1 (en) * 2014-05-30 2015-12-03 Toyota Jidosha Kabushiki Kaisha Continuously variable transmission

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110131409A (zh) * 2019-05-29 2019-08-16 杭州神驹科技有限公司 一种机械式自动变速箱换档执行机构
WO2023192166A1 (fr) * 2022-03-29 2023-10-05 Gates Corporation Systèmes de transmission à variation continue commandée par came

Similar Documents

Publication Publication Date Title
US20170284508A1 (en) Planetary Powertrain Configuration with a Ball Variator Continuously Variable Transmission Used as a Powersplit
US10066712B2 (en) Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US20180119786A1 (en) Continuously Variable Transmission Having A Ball-Type Continuously Variable Transmission
WO2016094254A1 (fr) Transmission planétaire à variation continue pour l'entraînement des roues avant et des roues arrière en 3 modes
US20190323582A1 (en) Idler assembly for a ball variator continuously variable transmission
WO2017151568A1 (fr) Système d'actionneur de changement de vitesse et procédé pour une transmission à engrenages planétaires à billes à variation continue ayant un support rotatif et/ou mis à la terre
US20180119811A1 (en) Ball Variator Continuously Variable Transmission
US20180119810A1 (en) Symmetric Infinitely Variable Transmission Having A Ball-Type Continuously Variable Transmission
US20170248213A1 (en) Planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit
US20180252303A1 (en) Continuously Variable Drive Having A Ball-Type Continuously Variable Transmission
US20190154147A1 (en) Non-synchronous shift control method and assemblies for continuously variable transmissions
US20180372199A1 (en) Multi-mode cvp transmission with geared launch and reverse modes
US20180119785A1 (en) Power Converter Having A Ball-Type Continuously Variable Transmission
US20180135734A1 (en) Electromagnetic Device For Ball-Type Continuously Variable Transmission
US20190078668A1 (en) Powersplit Powertrains Having Dual Ball-Type Continuously Variable Transmission
US9964203B2 (en) Passive method of preventing ball axle movement during a rollback event in a ball-planetary type continuously variable transmission
US20180135742A1 (en) Ball Variator Continuously Variable Transmission
US20170248214A1 (en) Planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit
US20190154125A1 (en) Planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit
US20190186602A1 (en) Ball variator continuously variable transmission
US20190032756A1 (en) Ball Variator Continuously Variable Transmission
US20190017583A1 (en) Four mode dual planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit
WO2018187296A1 (fr) Configurations de groupe motopropulseur planétaire dotées d'une transmission à variation continue munie d'un variateur à billes, utilisées comme répartition du couple
WO2018022741A1 (fr) Configuration de groupe motopropulseur planétaire pourvue d'une transmission à variation continue à variateur à billes ayant une interface de prise de force
WO2018209061A1 (fr) Ensemble à force de serrage axiale pour transmission à variation continue de variateur à bille

Legal Events

Date Code Title Description
NENP Non-entry into the national phase

Ref country code: DE

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17710103

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 17710103

Country of ref document: EP

Kind code of ref document: A1