WO2018085317A1 - Composants et ensembles pour une transmission planétaire à variation continue de type à billes - Google Patents

Composants et ensembles pour une transmission planétaire à variation continue de type à billes Download PDF

Info

Publication number
WO2018085317A1
WO2018085317A1 PCT/US2017/059430 US2017059430W WO2018085317A1 WO 2018085317 A1 WO2018085317 A1 WO 2018085317A1 US 2017059430 W US2017059430 W US 2017059430W WO 2018085317 A1 WO2018085317 A1 WO 2018085317A1
Authority
WO
WIPO (PCT)
Prior art keywords
carrier member
cvt
thrust bearing
shaft
carrier
Prior art date
Application number
PCT/US2017/059430
Other languages
English (en)
Inventor
Ryan D. Nelms
Brad P. Pohl
Benjamin POWELL
Matthew Simister
Gregory G. Stevenson
Original Assignee
Dana Limited
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 Limited filed Critical Dana Limited
Publication of WO2018085317A1 publication Critical patent/WO2018085317A1/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
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/10—Means for influencing the pressure between the members
    • F16H13/14—Means for influencing the pressure between the members for automatically varying the pressure mechanically
    • 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
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts

Definitions

  • a vehicle having a driveline including a tilting ball variator allows an operator of the vehicle or a control system of the vehicle to vary a drive ratio in a stepless manner.
  • a variator is an element of a
  • CVT Continuously Variable Transmission
  • Transmissions that use a variator can decrease the transmission's gear ratio as engine speed increases. This keeps the engine within its optimal efficiency while gaining ground speed, or trading speed for torque during hill climbing, for example. Efficiency in this case can be fuel efficiency, decreasing fuel consumption and emissions output, or power efficiency, allowing the engine to produce its maximum power over a wide range of speeds. That is, the variator keeps the engine turning at constant RPMs over a wide range of vehicle speeds.
  • a continuously variable transmission having a plurality of balls, each ball having a tiltable axis of rotation, each ball in contact with a first traction ring and a second traction ring.
  • the CVT includes a rotatable shaft aligned along a longitudinal axis of the CVT, the shaft positioned radially inward of the balls, the first traction ring and the second traction ring; a carrier assembly operably coupled to each ball, the carrier assembly including a first carrier member arranged coaxial to the shaft and a second carrier member operably coupled to the first carrier member, the second carrier member configured to rotate relative to the first carrier member and arranged coaxial to the shaft; a first cam driver operably coupled to the first traction ring and the first carrier member, the first cam driver adapted to receive a rotational power; and a thrust bearing assembly coupled to the cam driver and to the shaft.
  • 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 plan view of a ball-type continuously variable transmission depicting a number of section views with respect to a longitudinal axis.
  • Figure 5 is a cross-sectional view "A-A" of the ball-type continuously variable transmission of Figure 4.
  • Figure 6 is a detail view "G" of a thrust bearing assembly used in the ball-type continuously variable transmission of Figure 4.
  • Figure 7 is a detail view "H" of an anti-rotation washer used in the ball- type continuously variable transmission of Figure 4.
  • Figure 8 is an exploded isometric detail view "L" of the thrust bearing assembly and anit-rotation washer of Figures 6 and 7, respectively.
  • Figure 9 is a cross-section view "C-C" of certain components of the ball- type continuously variable transmission of Figure 4.
  • Figure 10 is an isometric cross-section view of the ball-type continuously variable transmission of Figure 4.
  • Figure 1 1 is an isometric view of a cam driver used in the ball-type continuously variable transmission of Figure 4.
  • Figure 12 is another isometric view of the cam driver of Figure 1 1.
  • Figure 13 is an isometric, cross-sectional view "F-F" of the cam driver of
  • Figure 14 is a plan view of another embodiment of a ball-type
  • continuously variable transmission depicting a section view with respect to a longitudinal axis.
  • Figure 15 is a cross-sectional view "T-T" of certain components of the ball-type continuously variable transmission of Figure 14.
  • Figure 16 is a cross-section detail view "Y" of a bearing hub used in the ball-type continuously variable transmission of Figure 14.
  • Figure 17 is a cross-section view "J-J" of the ball-type continuously variable transmission of Figure 4.
  • Figure 18 is a cross-sectional detail view "K” of a shift-stop assembly used in the ball-type continuously variable transmission of Figure 4.
  • Figure 19 is a cross-sectional view "V-V" of certain components of the ball-type continuously variable transmission of Figure 4, depicting a shift-stop assembly.
  • Figure 20 is a detail view "W" of the shift-stop of Figure 19.
  • Figure 21 is a detail view "Z" of ramped surfaces of the cam driver of
  • CVTs based on 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 United States Patent No. 8,870,71 1 incorporated herein by reference in their entirety.
  • Such a CVT adapted herein as described throughout this specification, includes a number of balls (planets, spheres) 1 , depending on the application, two ring (disc) assemblies with a conical surface contact with the balls 1 , as a first (input) traction ring 2 and a second (output) traction ring 3, and an idler (sun) assembly 4 as shown on FIG. 1 .
  • the balls 1 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
  • 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.
  • the radial guide slots 8 and the radially offset guide slots 9 are adapted to guide the tiltable axles 5.
  • the axles 5 is 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 carrier member and the second carrier member to impart a tilting of the axles 5 and thereby adjusts the speed ratio of the variator.
  • the conical surfaces of the first traction ring 2 and the second traction ring 3 have angled contact surfaces with respect to the balls 1 in the range of 30 to 45 degrees.
  • the traction surface profile is typically described as a radius, R, of concave or convex nature between 100% conformal and 100% convex, including a straight (0% convex).
  • the traction surface profile R is generally less than the planet (ball) diameter.
  • the idler assembly 4 includes rings in contact with each balls 1 having angled contact surfaces with respect to the balls 1 in the range of 7 to 13 degrees.
  • the traction surface shape is between 200% conformal and 200% convex including straight (0% convex).
  • the traction surface profile of the idler assembly rings is less than or equal to two times the planet diameter.
  • FIG. 2 The working principle of such a CVP of FIG. 1 is shown on FIG. 2.
  • 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 is capable of being 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.
  • the terms “operationally connected,” “operationally coupled”, “operationally linked”, “operably connected”, “operably coupled”, “operably linked,” and like terms refer to a relationship (mechanical, linkage, coupling, etc.) between elements whereby operation of one element results in a corresponding, following, or simultaneous operation or actuation of a second element. It is noted that in using said terms to describe inventive
  • 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.
  • 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 forces which would be available at the interfaces of the contacting components and is a measure of the maximum available drive torque.
  • the traction coefficient is a design parameter in the range of 0.3 to 0.6.
  • friction drives generally relate to transferring power between two elements by frictional forces between the elements.
  • the CVTs described here may operate in both tractive and frictional
  • the traction coefficient ⁇ is a function of the traction fluid properties, the normal force at the contact area, and the velocity of the traction fluid in the contact area, among other things.
  • the traction coefficient ⁇ increases with increasing relative velocities of components, until the traction coefficient ⁇ reaches a maximum capacity after which the traction coefficient ⁇ decays.
  • the condition of exceeding the maximum capacity of the traction fluid is often referred to as "gross slip condition".
  • creep As used herein, "creep”, “ratio droop”, or “slip” is the discrete local motion of a body relative to another and is exemplified by the relative velocities of rolling contact components such as the mechanism described herein.
  • traction drives the transfer of power from a driving element to a driven element via a traction interface requires creep.
  • creep in the direction of power transfer is referred to as “creep in the rolling direction.”
  • the driving and driven elements experience creep in a direction orthogonal to the power transfer direction, in such a case this component of creep is referred to as "transverse creep.”
  • the terms "prime mover”, “engine,” and like terms, are used herein to indicate a power source.
  • Said power source may be fueled by energy sources including hydrocarbon, electrical, biomass, solar, geothermal, hydraulic, and/or pneumatic to name but a few.
  • energy sources including hydrocarbon, electrical, biomass, solar, geothermal, hydraulic, and/or pneumatic to name but a few.
  • a continuously variable transmission (CVT) 10 is configured in a similar manner as the variator depicted in FIGS. 1-3.
  • CVT continuously variable transmission
  • orientation of cross-sectional views are provided with respect to the longitudinal axis in FIGS. 4 and 14.
  • the longitudinal axis is arranged perpendicular to the plane of the page when viewed in FIGS. 4 and 14.
  • the CVT 10 is provided with a shaft 1 that is arranged along the longitudinal axis.
  • a thrust bearing assembly 12 is operably coupled to the shaft 1 1 .
  • the CVT 10 is adapted to receive a rotational input power on a first cam driver 13.
  • the first cam driver 13 is coupled to a first array of ball cam bearings 14.
  • the first array of ball cam bearings 14 are configured to cooperate with a number ramped surfaces provided on the first cam driver 13 and/or a first traction ring 15 to provide torque dependent axial force, sometimes referred to as "clamping force”, “clamping”, or "axial clamp force”.
  • the first traction ring 15 is in contact with a number of balls 1 .
  • the CVT 10 is provided with a second traction ring 16 in contact with the balls 1.
  • the second traction ring 16 is coupled to a second array of ball cam bearings 17.
  • the ball cam bearings 17 are configured to cooperate with a number of ramped surfaces provided on the second traction ring 16 and/or a second cam driver 18.
  • the second cam driver 18 is coupled to the shaft 1 1.
  • the second cam driver 18 is coupled to the shaft 1 1 with a set of splines.
  • the shaft 1 1 is adapted to transmit a power output from the CVT 10.
  • the balls 1 are operably coupled to a carrier assembly 19.
  • the carrier assembly 19 is provided with a first carrier member 20 and a second carrier member 21.
  • the carrier assembly 19 is coaxial with the shaft 1 1.
  • the carrier assembly 19 is operably coupled to the shaft 1 1 with a bearing, a bushing, or some other means of rotatable coupling.
  • the thrust bearing assembly 12 is provided with a thrust bearing nut 25.
  • the thrust bearing nut 25 is coupled to the shaft 1 1 with a threaded portion 26.
  • the threaded portion 26 is on the radially inner surface of the thrust bearing nut 25.
  • the threaded portion 26 provides a piloting surface for alignment of the thrust bearing assembly 12 with respect to the shaft 1 1.
  • the thrust bearing nut 25 is coupled to an array of thrust bearing balls 27.
  • the thrust bearing balls 27 are configured to couple to an outer bearing race 28.
  • the outer bearing race 28 is integral to the thrust bearing nut 25.
  • the outer bearing race 28 is located radially outward with respect to the threaded portion 26.
  • the thrust bearing assembly 12 includes an inner thrust bearing race member 29.
  • the inner thrust bearing race member 29 is operably coupled to the first cam driver 13.
  • a preload spring 30 is coupled to the first cam driver 13 and the inner thrust bearing race member 29.
  • the inner thrust bearing race member 29 includes an inner bearing race 31 adapted to couple to the thrust bearing balls 27.
  • the inner thrust bearing race member 29 is located on an opposite side of the thrust bearing nut 25 with respect to the thrust bearing balls 27. For example, the inner bearing race 31 and the outer bearing race 28 contact opposite surfaces of the thrust bearing balls 27.
  • the inner thrust bearing race member 29 is provided with an extension portion 32 configured to surround the thrust bearing nut 25.
  • the extension portion 32 is an annular ring located radially outward of the inner bearing race 31 on the inner thrust bearing member 29.
  • the extension portion 32 extends axially toward the thrust bearing nut 25.
  • the extension portion 32 is sized to substantially surround the radial periphery of the thrust bearing nut 25.
  • extension portion 32 is provided to limit lube flow out of thrust bearing assembly 12, thus resulting in a flooded bearing space.
  • a shallow angle angular contact ball bearing is used to allow for standard raceway processing, therefore, lowering cost. Improvements in axial packaging are possible when the raceways 28, 31 are integrated into the thrust bearing nut 25 and the first cam driver 3.
  • an anti-rotation washer 33 is coupled to the thrust bearing nut 25.
  • the anti-rotation washer 33 includes a protrusion 34 that couples to a set of holes 35 formed in the thrust bearing nut 25.
  • the protrusion 34 is optionally a cylinder-like body configured to fit within one of the holes 35.
  • the protrusion 34 is sized to be approximately the diameter of one of the holes 35.
  • the anti-rotation washer 33 is radially located on the shaft 1 1.
  • the anti-rotation washer 33 has an inner bore that the shaft 11 fits through and the inner bore of the anti-rotation washer 33 is provided with a set of splines configured to couple to mating splines formed on the shaft 11. In some embodiments, the anti-rotation washer 33 is coupled to the shaft 1 1 with a c-clip 36.
  • the shaft 1 1 and the carrier assembly 19 are configured to facilitate flow of fluid, such as traction fluid, through the CVT 10 to provide lubrication and cooling, among other purposes.
  • the shaft 11 is provided with a hollow central passage 37.
  • the hollow central passage 37 is in fluid communication with a source of pressurized fluid from a pump, for example.
  • the shaft 11 is provided with a thrust bearing lube port 38 aligned axially to the thrust bearing assembly 12.
  • the thrust bearing lube port 38 is a drilled radial hole arranged between the hollow central passage 37 and an outer periphery of the shaft 1 1.
  • the shaft 11 is provided with a first carrier member lube port 39 arranged in proximity to the first carrier member 20.
  • the first carrier member lube port 39 is a drilled hole arranged between the hollow central passage 37 and the outer periphery of the shaft 1 1.
  • the shaft 1 1 is provided with an idler assembly lube port 40 arranged in proximity to the idler assembly 4, for example.
  • the idler assembly lube port 40 is a radial hole arranged between the hollow central passage 37 and the outer periphery of the shaft 1 1.
  • the shaft 11 is provided with a second carrier member lube port 41 arranged in proximity to the second carrier member 21.
  • the second carrier member lube port 41 is a radial hole drilled between the hollow central passage 37 and the outer periphery of the shaft 11.
  • the first carrier member 20 is provided with a first array of radial lubricant passages 42.
  • the first array of radial lubricant passages 42 are arranged so that one of the radial lubricant passages 42 is between each ball 1.
  • a CVT having six balls is provided with six radial lubricant passages.
  • the second carrier member 21 is provided with a second array of radial lubricant passages 43.
  • the second array of radial lubricant passages 42 are arranged between each ball 1 in a similar manner as the first array of radial lubricant passages 42.
  • the first array of radial lubricant passages 42 and the second array of radial lubricant passages 43 are arranged to be in fluid communication with the first carrier member lube port 39 and the second carrier member lube port 41 , respectively.
  • the first carrier member 20 is provided with a first array of orifice lube passages 44.
  • the first array of orifice lube passages 44 are in fluid communication with the first array of radial lubricant passages 42.
  • Each of the first array of orifice lube passages 44 is located between each ball 1.
  • Each of the first array of orifice lube passages 44 are located radially outward of each of the first array of radial lubricant passages 42.
  • the second carrier member 21 is provided with a second array of orifice lube passages 45. The second array of orifice lube passages
  • first array of orifice lube passages 43 and the second array of orifice lube passages 45 are configured to supply a metered flow of fluid to an array of input traction ring orifice plugs 46 and an array of output traction ring orifice plugs 47.
  • the first cam driver 13 is a substantially disc shaped body having an inner bore 50.
  • the first cam driver 13 is provided with a splined ring 51 positioned between the inner bore 50 and an outer periphery of the disc shaped body.
  • the splined ring 51 is configured to couple to a source of rotational power.
  • the splined ring 51 is provided with a number of raised piloting surfaces 49 located radially inward of the splined ring 51 .
  • the raised piloting surfaces 49 provide an alignment feature to the thrust bearing assembly 12.
  • the raised piloting surfaces 49 are adapted to receive the inner thrust bearing race member 29.
  • the first cam driver 13 is provided with an array of ramped surfaces 52 located radially about an outer periphery of the disc shaped body.
  • the ramped surfaces 52 are coupled to the first array of ball cam bearings 14, for example, and provide a means to produce an axial force during operation of the CVT 10.
  • each of the ramped surfaces 52 are formed adjacent to each other so that the ramped surfaces 52 connect at the crest of each ramp. By connecting ramp crests, the cam ball bearings 14 are able to roll on the ramped surface to the crest and down into the next adjacent ramped surface 52, all the while ensuring radial location of the cam ball bearings 14. This operating condition is sometimes referred to as "cam-hop".
  • the first cam driver 13 is provided with a ridge 53 coaxially aligned with the splined ring 51 .
  • the ridge 53 is formed on a common side with the ramped surfaces 52.
  • the splined ring 51 is formed on an opposite side of the disc shaped body from the ridge 53.
  • the first cam driver 13 is provided with a number of radial legs 54 positioned between the inner bore 50 and the ridge 53.
  • the radial legs 54 and the ridge 53 guide the strain in the first cam driver 13 during operation of the CVT 10.
  • the strain or deflection, in the first cam driver 13 is controlled by the positioning of the ridge 53 with respect to the splined ring 51 and the inner bore 50.
  • a continuously variable transmission (CVT) 55 is provided with a shaft 56, a first carrier member 57, and a second carrier member 58.
  • the CVT 55 is provided with a first cam driver 59 adapted to receive a first power.
  • the CVT 55 is provided with a carrier bearing hub 60.
  • the carrier bearing hub 60 is coupled to the shaft 56 with a bearing 61 , for example.
  • the carrier bearing hub 60 is coupled to the first cam driver 59 with a need bearing 62, for example.
  • the carrier bearing hub 60 is coupled to an inner bore of the first carrier member 57.
  • the carrier bearing hub 60 is a different material than the first carrier member 57.
  • the CVT 10 is provided with a shift stop pin 65 fixedly coupled to the first carrier member 20.
  • the shift stop pin 65 is a common dowel pin having a cylindrical shape.
  • the second carrier member 21 has a pocket 66 recessed into the second carrier member 21 and adapted to receive the shift stop pin 65.
  • the pocket 66 has a first stop face 67 at one end of the pocket 66, and a second stop face 68 at an opposite end of the pocket 66.
  • a relative rotation of the first carrier member 20 with respect to the second carrier member 21 corresponds to a change in the operating condition of the CVT 10.
  • the first stop face 67 and the second stop face 68 provide a physical limitation to the relative rotation of the first carrier member 20 to the second carrier member 21 to thereby limit the operating speed ratio range of the CVT 10.
  • a crest 70 is formed between two adjacent ramped surfaces 52 (labeled as "52A” and "52B" in FIG. 21).
  • the ball cam bearing 14 contacts the ramped surface 52.
  • the contacting location between the ball cam bearing 14 and the ramped surface 52 is an elliptical shape, referred to herein as the "contact ellipse”.
  • the contact ellipse of the ball cam bearing 14 to the ramped surface 52 is smaller than the width of the crest to thereby lower contact pressure or stress at the crest 52.
  • the contact stress on the ball cam bearing 14 at the crest 70 is less than the contact stress on the ball cam bearing 14 when on either the ramped surface 52A or the ramped surface 52B.
  • the crest 70 facilitates a transition from the ramped surface 52A to the ramped surface 52B within the stress limits of the materials selected for the ball cam bearing 14 and the ramped surface 52.

Landscapes

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

Abstract

Transmission à variation continue (CVT) comportant une pluralité de billes, chaque bille ayant un axe de rotation inclinable et étant en contact avec un premier anneau de traction et un second anneau de traction. La CVT comprend un arbre rotatif aligné le long d'un axe longitudinal de la CVT et positionné radialement vers l'intérieur des billes, du premier anneau de traction et du second anneau de traction ; un ensemble de support fonctionnellement accouplé à chaque bille comprenant un premier élément de support coaxial à l'arbre et un second élément de support fonctionnellement accouplé au premier élément de support ; un premier dispositif d'entraînement de came fonctionnellement accouplé au premier anneau de traction et au premier élément de support et conçu pour recevoir une puissance de rotation ; et un ensemble palier de butée accouplé au dispositif d'entraînement de came et à l'arbre. Selon un mode de réalisation, l'ensemble de support comprend des canaux de passage de lubrification.
PCT/US2017/059430 2016-11-02 2017-11-01 Composants et ensembles pour une transmission planétaire à variation continue de type à billes WO2018085317A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201662416358P 2016-11-02 2016-11-02
US62/416,358 2016-11-02

Publications (1)

Publication Number Publication Date
WO2018085317A1 true WO2018085317A1 (fr) 2018-05-11

Family

ID=60321021

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2017/059430 WO2018085317A1 (fr) 2016-11-02 2017-11-01 Composants et ensembles pour une transmission planétaire à variation continue de type à billes

Country Status (1)

Country Link
WO (1) WO2018085317A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007067249A1 (fr) * 2005-12-09 2007-06-14 Fallbrook Technologies Inc. Transmission a variation continue
EP1811202A1 (fr) * 2005-12-30 2007-07-25 Fallbrook Technologies, Inc. Transmission à variation continue
US20100093480A1 (en) * 2008-10-14 2010-04-15 Fallbrook Technologies Inc. Continuously variable transmission
US20100119184A1 (en) * 2008-11-12 2010-05-13 Hitachi Construction Machinery Co., Ltd. Travel Assembly
EP2304272A1 (fr) * 2008-06-23 2011-04-06 Fallbrook Technologies Inc. Transmission à variation continue
US8469856B2 (en) 2008-08-26 2013-06-25 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US20160290451A1 (en) * 2015-03-31 2016-10-06 Fallbrook Intellectual Property Company Llc Balanced split sun assemblies with integrated differential mechanisms, and variators and drive trains including balanced split sun assemblies

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007067249A1 (fr) * 2005-12-09 2007-06-14 Fallbrook Technologies Inc. Transmission a variation continue
EP1811202A1 (fr) * 2005-12-30 2007-07-25 Fallbrook Technologies, Inc. Transmission à variation continue
EP2304272A1 (fr) * 2008-06-23 2011-04-06 Fallbrook Technologies Inc. Transmission à variation continue
US8469856B2 (en) 2008-08-26 2013-06-25 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US20100093480A1 (en) * 2008-10-14 2010-04-15 Fallbrook Technologies Inc. Continuously variable transmission
US8870711B2 (en) 2008-10-14 2014-10-28 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US20100119184A1 (en) * 2008-11-12 2010-05-13 Hitachi Construction Machinery Co., Ltd. Travel Assembly
US20160290451A1 (en) * 2015-03-31 2016-10-06 Fallbrook Intellectual Property Company Llc Balanced split sun assemblies with integrated differential mechanisms, and variators and drive trains including balanced split sun assemblies

Similar Documents

Publication Publication Date Title
US10066712B2 (en) Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US20190323582A1 (en) Idler assembly for a ball variator continuously variable transmission
US20180119786A1 (en) Continuously Variable Transmission Having A Ball-Type Continuously Variable Transmission
WO2016168439A1 (fr) Serrage hydraulique centrifuge passif pour fonctionnement planétaire à variation continue à grande vitesse
US20170089433A1 (en) Carrier for ball-type continuously variable transmission
US20180119811A1 (en) Ball Variator Continuously Variable Transmission
WO2018222660A1 (fr) Composants et ensembles pour transmission planétaire à variation continue de type à billes
WO2018085317A1 (fr) Composants et ensembles pour une transmission planétaire à variation continue de type à billes
US20180135734A1 (en) Electromagnetic Device For Ball-Type Continuously Variable Transmission
US20190271379A1 (en) Passive preload control for a ball-type continuously variable planetary transmission
US20190264784A1 (en) Ball assembly for a ball-type continuously variable planetary transmission
US20180119810A1 (en) Symmetric Infinitely Variable Transmission Having A 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
US20180128357A1 (en) Articulating Sub-Housing For A Ball-Type Continuously Variable Planetary Transmission
US20180135742A1 (en) Ball Variator Continuously Variable Transmission
US20180119785A1 (en) Power Converter Having A Ball-Type Continuously Variable Transmission
US20190032756A1 (en) Ball Variator Continuously Variable Transmission
US20180119812A1 (en) Traction Path Oil Control For A Ball Variator Continuosly Variable Transmission
US20190186602A1 (en) Ball variator continuously variable transmission
WO2018209061A1 (fr) Ensemble à force de serrage axiale pour transmission à variation continue de variateur à bille
US20190078668A1 (en) Powersplit Powertrains Having Dual Ball-Type Continuously Variable Transmission
US20190017583A1 (en) Four mode dual planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit
US20170122418A1 (en) Four mode powertrain configurations with a ball variator continuously variable transmission used as a powersplit
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
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

Legal Events

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

Ref document number: 17797833

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17797833

Country of ref document: EP

Kind code of ref document: A1