WO2007051827A1 - Entraînement de transmission à rapport continuellement variable - Google Patents

Entraînement de transmission à rapport continuellement variable Download PDF

Info

Publication number
WO2007051827A1
WO2007051827A1 PCT/EP2006/068051 EP2006068051W WO2007051827A1 WO 2007051827 A1 WO2007051827 A1 WO 2007051827A1 EP 2006068051 W EP2006068051 W EP 2006068051W WO 2007051827 A1 WO2007051827 A1 WO 2007051827A1
Authority
WO
WIPO (PCT)
Prior art keywords
variator
end load
input
race
races
Prior art date
Application number
PCT/EP2006/068051
Other languages
English (en)
Inventor
Christopher John Greenwood
Original Assignee
Infinitrak, Llc
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 Infinitrak, Llc filed Critical Infinitrak, Llc
Publication of WO2007051827A1 publication Critical patent/WO2007051827A1/fr

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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/664—Friction gearings
    • F16H61/6649—Friction gearings characterised by the means for controlling the torque transmitting capability of the gearing
    • 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
    • F16H15/32—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 curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
    • F16H15/36—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 curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
    • F16H15/38—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 curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces

Definitions

  • the present invention relates to continuously variable ratio transmission devices
  • variable of toroidal-race, rolling-traction type, and in particular to means for applying the "end load” needed to provide traction between rollers and races in such variators.
  • Variators are used in transmissions - particularly but not exclusively in
  • a pair of co-axially mounted circular races have respective semi-toroidally recessed surfaces which together define a generally toroidal cavity, within which is mounted a plurality of rollers.
  • the rollers are sandwiched between the races, running upon their recessed faces, and serve to
  • variable axis which will be referred to as the "variator axis" the relative speeds of the two races - and hence the variator 1 s drive ratio - can be altered in a stepless manner.
  • rollers are caused to steer themselves to suitably vary their inclinations.
  • End load This force will be referred to herein as the "end load".
  • the rollers and races do not actually contact each other, being separated by a thin film of traction fluid which is maintained by continuously jetting the fluid onto these parts. Traction results from shear within the fluid layer, when subject to a suitably high pressure due to the end load. End load is typically provided by applying an axial force to one of
  • reaction pressure A common pressure (the "reaction pressure") is applied to each actuator, and determines a force (the “reaction force”) applied to each
  • reaction torque is proportional to reaction pressure.
  • the end load is provided by means of a hydraulic actuator exerting an axial force on one of the races, and the fluid pressure supplied to this end load actuator is equal to, or at least controlled by, the reaction pressure, so that the end load is
  • the traction coefficient is defined as the ratio of (i) the force parallel to the interface to (ii) the force normal to
  • End load adjustment must in some situations be carried out with little time lag. Externally created events, such as rapid vehicle braking, can abruptly create a requirement for an increase of end load, and failure to respond with sufficient speed could result in catastrophic slip within the variator.
  • the known hydraulic system provides the required speed of response.
  • variableators are not hydraulically controlled.
  • the present invention has been devised in connection with a relatively simple variator in which roller displacement is instead controlled through a direct mechanical coupling.
  • control end load through some form of mechanical coupling which translates the reaction force applied to the roller's mountings into end load, but in reality this is not considered to be practical. Therefore some other way of suitably adjusting end load is required.
  • end load is adjusted in dependence upon reaction torque.
  • end load could instead be adjusted in dependence upon either input torque alone or output torque alone, and in fact it is known to vary end load in proportion to input torque. This is done in variators of the so-called "half toroidal" type but proves less appropriate in full toroidal variators. The difference
  • variator axis 16 and the rollers lie along a diameter of the circle generating the torus.
  • the centres 17 of the rollers 18 lie upon, or close to, the centre of this circle, and the
  • variable continuously variable ratio transmission device
  • variable comprising an input race operatively coupled to a variator input shaft and an output race operatively coupled to a variator output shaft, the input and output races being mounted for rotation about
  • the " races having respective part-toroidally shaped surfaces which together define a substantially toroidal cavity containing at least two rollers, each roller running upon the shaped surfaces of both races to transfer drive from one to the other and being provided with mountings which permit the roller's inclination to the common axis to vary, in order to vary the ratio of input shaft speed to output shaft
  • the variator being characterised in that the end load arrangement comprises (a) a first end load device for applying a first end load component which varies in accordance with torque applied to the input race and (b) a second end load device for applying a second end load component which is
  • the first and second end load devices acting upon the same variator race so that the total end load is the sum of the first and second end load components.
  • variable continuously variable ratio transmission device
  • the input and output races being mounted for rotation about a common axis, the races having respective part-toroidally shaped surfaces which together define a substantially toroidal cavity containing at least two rollers, each ⁇ roller running upon the shaped surfaces of both races to transfer drive from one to the
  • the variator being characterised in that the
  • end load arrangement comprises (a) a mechanical actuator which applies to one of the
  • variator races an axial force which varies according to the torque applied to the input
  • variable continuously variable ratio transmission device
  • part-toroidally shaped surfaces which together define a substantially toroidal cavity
  • each roller running upon the shaped surfaces of both races to transfer drive from one to the other and being provided with mountings
  • the method comprising applying to the same variator race (a) a substantially constant end load component and (b) an end load component which varies with variator input torque.
  • the first end load component is substantially proportional to the absolute value of the torque applied to the input race.
  • Absolute value is used here to refer to the magnitude of the torque, regardless of its sign (direction).
  • the second end load component is preferably substantially constant. It may
  • the first end load device forms a coupling which
  • the coupling serves both to transmit torque from the variator input shaft to the input race and to apply the first end load component, the coupling comprising first and second parts,
  • the ramp surface could in principle be part of a screw thread.
  • the ramp acts upon a force-transmitting part in the form of a ball which
  • the coupling comprises at least two ramp surfaces which are oppositely inclined to said plane perpendicular to the common axis, such that the axial force is applied in the same direction regardless of the direction of action of the torque applied to the input race.
  • the first and second coupling parts have respective ramp surfaces, the force-transmitting part being formed separately from both coupling parts and being retained between their respective ramp surfaces.
  • One of the coupling parts may be formed by the input race itself.
  • first and second end load devices are both anchored to the variator input shaft ,and the variator output race is mounted around and axially restrained relative to the input shaft, so that the end load force is borne in
  • Figures Ia and Ib are highly simplified sections, in an axial plane, through a full toroidal and a half toroidal variator respectively;
  • Figure 2 is a graph of the variation of axial load in a known variator;
  • Figure 3 is a graph of traction coefficient against ratio for variators using different end load control strategies
  • Figure 4a is a section in an axial plane through a variator embodying the present invention.
  • Figure 4b is a section in a radial plane through the same variator
  • Figure 5 is a view along a radial direction of a ball ramp device used in the same variator
  • Figure 6 is a perspective illustration of a thrust disc of the ball ramp device
  • Figure 7 is a perspective view of the rear of a race used in the same variator
  • Figure 8 is a perspective view of the front of the same race
  • Figure 9 is a graph of end load against input torque for a variator embodying the present invention.
  • Figure 10 is a perspective illustration of a registration disc used in the ball ramp device of Figures 4 and 5.
  • the present invention has been devised following an analysis of full-toroidal variator performance, and in this connection reference is directed to Figure 3, which represents variation of variator traction coefficient, on the vertical axis, with ratio, on the horizontal axis, for a full-toroidal type variator.
  • the calculation has been based on the assumption that variator output torque is constant. This assumption is
  • variator input torque can be calculated from the chosen constant output torque and the variator
  • line L 0 represents the case of a constant end load
  • the constant end load would have to be chosen to avoid this even at the high traction coefficient end of the curve (at high negative ratios) and as a result the variator would be inefficient when working elsewhere on the curve, at lower ratios.
  • Line L 1 represents the alternative strategy in which end load is proportional to variator " input torque. Ih this case traction coefficient is greatest at low negative variator ratios and the constant of proportionality of end load to input torque would
  • Line LR represents the strategy where end load is proportional to reaction
  • the range of variation of traction coefficient with ratio is relatively small, and consequently the ratio of end load to reaction torque can be chosen to provide good variator efficiency throughout the ratio range. This is highly desirable and can be achieved, as already explained, in a hydraulically controlled variator.
  • line L INV represents the variation of traction coefficient achieved using a strategy in accordance with the present invention. Note that it approximates to line L R , and shows a similarly small range of traction
  • the variator has an input race 100 with a part toroidal face 102 f and an output race 104
  • the thrust disc 118 rotatably mounted upon a hollow spigot 116 of a thrust disc 118.
  • the thrust disc 118 is rotatably mounted upon a hollow spigot 116 of a thrust disc 118.
  • the variator' s output race 104 is mounted on a collar 111 which in turn is mounted upon the input shaft 112 though a bearing 120 . and rotates freely relative
  • this gear typically couples to an epicyclic gear train through which drive is taken to motor vehicle wheels.
  • gear trains are well known in the art and will not be described herein.
  • This particular variator has two rollers controlled by a simple mechanical
  • the mechanism comprises a lever 130 whose outer end 132 extends outside variator casing 134 to couple to a control mechanism. Variator ratio is determined by the position of this lever.
  • a flexible diaphragm 136 serves as a cover for an opening in the casing through which the lever emerges.
  • the lever is pivoted around a pin 136 mounted in a web 138 formed as part of the casing.
  • the lever is also able to move radially, for reasons which will shortly be explained.
  • the lever has laterally extending arms 142, 144 on either side of the pin 136 which carry respective carriages 146, 148 in
  • variator rollers 150, 152 are journalled through bearings 154, 156.
  • rollers are also able to turn as indicated by curved arrows in Figure 4b to change their inclinations to the variator axis, and thereby change variator drive ratio.
  • the rollers always seek an inclination at which then-
  • rollers 150, 152 are consequently subject to a steering effect by the races 100, 104, changing their inchnations to restore
  • rollers need some freedom to move relative to each other to equalise
  • This freedom is provided in the illustrated mechanism by virtue of the freedom of the lever 130 to move radially through a small distance.
  • the illustrated variator has three different devices for biasing the races 100, 104 toward each other to provide roller/race traction:
  • the ball ramp device 200 is formed by the thrust disc 118 and the input race 100. As Figures 5 and 7 show, the rear face of the input race 100 has a set of
  • the illustrated embodiment has four such
  • each recess can be thought of as being formed by two helical regions or ramps
  • the input shaft 112 is driven from some rotary power source, which is typically an internal combustion engine but could in principle be an electric motor, external combustion engine etc. If zero torque is applied to the input shaft 112, then the rotational position of the input race 100 relative to the thrust disc 118 is such that
  • the force is substantially proportional to the input torque. Note also that by virtue of the "V" section of the recesses, input torque in either rotational direction (clockwise or anti-clockwise) creates a force in the same axial direction (toward the output race 104).
  • a registration disc 211 is positioned between the thrust disc 118 and the input race 100, receiving the balls in respective through-going holes 213.
  • the end load spring 202 acts upon the input race 100 to urge it toward the output race 104. Its contribution to the end load is thus added to that of the ball ramp
  • end load spring 202 is mounted between the thrust disc 118 and the input race 100, serving to urge these two parts away from
  • the end load spring 202 acts upon the thrust disc through a thrust bearing 203.
  • the thrust disc 118 and the race 100 the end load spring 202 acts upon the thrust disc through a thrust bearing 203.
  • the end load spring 202 acts against a bearing 203.
  • the end load spring 202 is formed as a resilient metal disc, known to those skilled in the art as a Belleville washer and widely commercially available.
  • end load spring 202 tends to separate the parts making up the ball ramp device - the input disc 100 and thrust disc 118. In the absence of sufficient
  • the pre-load spring 204 prevents this. It acts upon the output race 104 to urge it toward the input disc 100. Hence the pre-load spring 204 acts in opposition to the ball ramp
  • the end load spring 202 and the pre-load spring 204 are referred to the shaft, which is thus in tension.
  • the force of the pre-load spring 204 is sufficient to overcome that of the end
  • Line L INP represents the end load component contributed by the ball ramp device 200.
  • Dotted line L ELS represents the end load component contributed by the end load spring 202.
  • the solid line L EL represents the actual end load. At low input torque the minimum end load value is determined by the pre-load spring at a value PLS.

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

Abstract

La présente invention concerne la gestion de la charge d’extrémité dans un dispositif de transmission à rapports variables (« variateur ») d’un type doté de chemins d’entrée et de sortie à renfoncements partiellement toroïdaux (100, 104) définissant une cavité toroïdale (108) contenant des rouleaux (150, 152) qui circulent sur lesdits chemins afin de transférer la force motrice de l’un à l’autre, et dont l’inclinaison est variable pour produire une variation continue dans les vitesses relatives des chemins. Une charge d’extrémité est appliquée pour forcer les chemins à entrer en prise avec les rouleaux. Cette charge d’extrémité comprend (a) un premier composant de charge d’extrémité qui varie en fonction du couple appliqué au chemin d’entrée (100) du variateur et (b) un second composant de charge d’extrémité qui est sensiblement constant. Ceci peut être réalisé au moyen d’un agencement qui, malgré une construction simple, offre néanmoins un bon niveau d’efficacité du variateur.
PCT/EP2006/068051 2005-11-02 2006-11-02 Entraînement de transmission à rapport continuellement variable WO2007051827A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0522361.5 2005-11-02
GB0522361A GB0522361D0 (en) 2005-11-02 2005-11-02 Continuously variable ratio transmission drive

Publications (1)

Publication Number Publication Date
WO2007051827A1 true WO2007051827A1 (fr) 2007-05-10

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Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011051702A1 (fr) * 2009-10-29 2011-05-05 Torotrak (Development) Limited Mécanisme d'entraînement pour transmission à variation continue
WO2014039439A1 (fr) * 2012-09-07 2014-03-13 Dana Limited Transmission variable en continu/transmission variable à l'infini du type à bille comprenant des ensembles d'engrenages planétaires
US8771133B2 (en) 2006-08-07 2014-07-08 Torotrak (Development) Limited Drive mechanism for infinitely variable transmission
US8986150B2 (en) 2012-09-07 2015-03-24 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
WO2015130659A1 (fr) * 2014-02-28 2015-09-03 Dana Automotive Systems Group, Llc Système de lubrification à faible perte
US9194472B2 (en) 2013-03-14 2015-11-24 Dana Limited Ball type continuously variable transmission
WO2016067058A1 (fr) * 2014-10-31 2016-05-06 Torotrak (Development) Ltd Variateurs
US9347532B2 (en) 2012-01-19 2016-05-24 Dana Limited Tilting ball variator continuously variable transmission torque vectoring device
US9353842B2 (en) 2012-09-07 2016-05-31 Dana Limited Ball type CVT with powersplit paths
US9404414B2 (en) 2013-02-08 2016-08-02 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9541179B2 (en) 2012-02-15 2017-01-10 Dana Limited Transmission and driveline having a tilting ball variator continuously variable transmission
US9551404B2 (en) 2013-03-14 2017-01-24 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US9556941B2 (en) 2012-09-06 2017-01-31 Dana Limited Transmission having a continuously or infinitely variable variator drive
US9556943B2 (en) 2012-09-07 2017-01-31 Dana Limited IVT based on a ball-type CVP including powersplit paths
US9599204B2 (en) 2012-09-07 2017-03-21 Dana Limited Ball type CVT with output coupled powerpaths
US9638296B2 (en) 2012-09-07 2017-05-02 Dana Limited Ball type CVT including a direct drive mode
US9777815B2 (en) 2013-06-06 2017-10-03 Dana Limited 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission
US10006529B2 (en) 2014-06-17 2018-06-26 Dana Limited Off-highway continuously variable planetary-based multimode transmission including infinite variable transmission and direct continuously variable transmission
US10030748B2 (en) 2012-11-17 2018-07-24 Dana Limited Continuously variable transmission
US10030751B2 (en) 2013-11-18 2018-07-24 Dana Limited Infinite variable transmission with planetary gear set
US10030594B2 (en) 2015-09-18 2018-07-24 Dana Limited Abuse mode torque limiting control method for a ball-type continuously variable transmission
US10088022B2 (en) 2013-11-18 2018-10-02 Dana Limited Torque peak detection and control mechanism for a CVP

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US2164504A (en) * 1935-07-05 1939-07-04 Adiel Y Dodge Variable speed transmission
US2446462A (en) * 1945-07-28 1948-08-03 Adiel Y Dodge Transmission
US3048047A (en) * 1961-03-08 1962-08-07 Curtiss Wright Corp Toroidal transmission damping mechanism
GB1340563A (en) * 1971-01-07 1973-12-12 Titt G Gears
US3822610A (en) * 1972-08-31 1974-07-09 R Erban Traction roller transmission with torque loading means
WO2002079675A1 (fr) 2001-03-29 2002-10-10 Torotrak (Development) Ltd. Circuit de commande hydraulique pour variateur

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2060884A (en) * 1933-09-19 1936-11-17 Erban Operating Corp Power transmission mechanism
US2164504A (en) * 1935-07-05 1939-07-04 Adiel Y Dodge Variable speed transmission
US2446462A (en) * 1945-07-28 1948-08-03 Adiel Y Dodge Transmission
US3048047A (en) * 1961-03-08 1962-08-07 Curtiss Wright Corp Toroidal transmission damping mechanism
GB1340563A (en) * 1971-01-07 1973-12-12 Titt G Gears
US3822610A (en) * 1972-08-31 1974-07-09 R Erban Traction roller transmission with torque loading means
WO2002079675A1 (fr) 2001-03-29 2002-10-10 Torotrak (Development) Ltd. Circuit de commande hydraulique pour variateur

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8771133B2 (en) 2006-08-07 2014-07-08 Torotrak (Development) Limited Drive mechanism for infinitely variable transmission
WO2011051702A1 (fr) * 2009-10-29 2011-05-05 Torotrak (Development) Limited Mécanisme d'entraînement pour transmission à variation continue
US9347532B2 (en) 2012-01-19 2016-05-24 Dana Limited Tilting ball variator continuously variable transmission torque vectoring device
US9541179B2 (en) 2012-02-15 2017-01-10 Dana Limited Transmission and driveline having a tilting ball variator continuously variable transmission
US9556941B2 (en) 2012-09-06 2017-01-31 Dana Limited Transmission having a continuously or infinitely variable variator drive
US9599204B2 (en) 2012-09-07 2017-03-21 Dana Limited Ball type CVT with output coupled powerpaths
US10006527B2 (en) 2012-09-07 2018-06-26 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US10088026B2 (en) 2012-09-07 2018-10-02 Dana Limited Ball type CVT with output coupled powerpaths
US9689477B2 (en) 2012-09-07 2017-06-27 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9353842B2 (en) 2012-09-07 2016-05-31 Dana Limited Ball type CVT with powersplit paths
US9638296B2 (en) 2012-09-07 2017-05-02 Dana Limited Ball type CVT including a direct drive mode
US9416858B2 (en) 2012-09-07 2016-08-16 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9052000B2 (en) 2012-09-07 2015-06-09 Dana Limited Ball type CVT/IVT including planetary gear sets
WO2014039439A1 (fr) * 2012-09-07 2014-03-13 Dana Limited Transmission variable en continu/transmission variable à l'infini du type à bille comprenant des ensembles d'engrenages planétaires
US8986150B2 (en) 2012-09-07 2015-03-24 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9556943B2 (en) 2012-09-07 2017-01-31 Dana Limited IVT based on a ball-type CVP including powersplit paths
US10030748B2 (en) 2012-11-17 2018-07-24 Dana Limited Continuously variable transmission
US9404414B2 (en) 2013-02-08 2016-08-02 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9644530B2 (en) 2013-02-08 2017-05-09 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9638301B2 (en) 2013-03-14 2017-05-02 Dana Limited Ball type continuously variable transmission
US9551404B2 (en) 2013-03-14 2017-01-24 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US9689482B2 (en) 2013-03-14 2017-06-27 Dana Limited Ball type continuously variable transmission
US9933054B2 (en) 2013-03-14 2018-04-03 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US9194472B2 (en) 2013-03-14 2015-11-24 Dana Limited Ball type continuously variable transmission
US9777815B2 (en) 2013-06-06 2017-10-03 Dana Limited 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission
US10030751B2 (en) 2013-11-18 2018-07-24 Dana Limited Infinite variable transmission with planetary gear set
US10088022B2 (en) 2013-11-18 2018-10-02 Dana Limited Torque peak detection and control mechanism for a CVP
WO2015130659A1 (fr) * 2014-02-28 2015-09-03 Dana Automotive Systems Group, Llc Système de lubrification à faible perte
US10006529B2 (en) 2014-06-17 2018-06-26 Dana Limited Off-highway continuously variable planetary-based multimode transmission including infinite variable transmission and direct continuously variable transmission
WO2016067058A1 (fr) * 2014-10-31 2016-05-06 Torotrak (Development) Ltd Variateurs
US11047456B2 (en) 2014-10-31 2021-06-29 Allison Transmission, Inc. Variators
US10030594B2 (en) 2015-09-18 2018-07-24 Dana Limited Abuse mode torque limiting control method for a ball-type continuously variable transmission

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